1、BRITISH STANDARD BS ISO 16881-1:2005 Cranes Design calculation for rail wheels and associated trolley track supporting structure Part 1: General ICS 53.020.20 BS ISO 16881-1:2005 This British Standard was published under the authority of the Standards Policy and Strategy Committee National foreword
2、This British Standard reproduces verbatim ISO 16881-1:2005 and implements it as the UK national standard. The UK participation in its preparation was entrusted by Technical Committee MHE/3, Cranes and derricks to Subcommittee MHE/3/3 Bridge, gantry and slewing jib cranes, which has the responsibilit
3、y to: A list of organizations represented on this committee can be obtained on request to its secretary. Cross-references The British Standards which implement international publications referred to in this document may be found in the BSI Catalogue under the section entitled “International Standard
4、s Correspondence Index”, or by using the “Search” facility of the BSI Electronic Catalogue or of British Standards Online. This publication does not purport to include all the necessary provisions of a contract. Users are responsible for its correct application. Compliance with a British Standard do
5、es not of itself confer immunity from legal obligations. aid enquirers to understand the text; present to the responsible international/European committee any enquiries on the interpretation, or proposals for change, and keep UK interests informed; monitor related international and European developm
6、ents and promulgate them in the UK. Summary of pages This document comprises a front cover, an inside front cover, the ISO title page, pages ii to v, a blank page, pages 1 to 13 and a back cover. The BSI copyright notice displayed in this document indicates when the document was last issued. Amendme
7、nts issued since publication Amd. No. Date Comments on 30 August 2005 BSI 30 August 2005 ISBN 0 580 46470 9 Reference number ISO 16881-1:2005(E)INTERNATIONAL STANDARD ISO 16881-1 First edition 2005-05-15 Cranes Design calculation for rail wheels and associated trolley track supporting structure Part
8、 1: General Appareils de levage charge suspendue Calcul de conception des galets et de la structure de support du chariot de roulement Partie 1: Gnralits BS ISO 16881-1:2005 ii BS ISO 16881-1:2005 iiiContents Page Foreword iv Introduction v 1 Scope 1 2 Normative references . 1 3 Terms and definition
9、s. 1 4 Requirements 1 4.1 Selection of rail wheels 1 4.2 Determination of the class of mechanism of the travel wheel . 5 4.3 Determination of local stresses due to wheel loads . 5 Annex A (informative) Distribution of wheel load under rail 6 Annex B (informative) Local stresses in wheel-supporting f
10、langes . 8 Bibliography . 13 BS ISO 16881-1:2005 iv Foreword ISO (the International Organization for Standardization) is a worldwide federation of national standards bodies (ISO member bodies). The work of preparing International Standards is normally carried out through ISO technical committees. Ea
11、ch member body interested in a subject for which a technical committee has been established has the right to be represented on that committee. International organizations, governmental and non-governmental, in liaison with ISO, also take part in the work. ISO collaborates closely with the Internatio
12、nal Electrotechnical Commission (IEC) on all matters of electrotechnical standardization. International Standards are drafted in accordance with the rules given in the ISO/IEC Directives, Part 2. The main task of technical committees is to prepare International Standards. Draft International Standar
13、ds adopted by the technical committees are circulated to the member bodies for voting. Publication as an International Standard requires approval by at least 75 % of the member bodies casting a vote. Attention is drawn to the possibility that some of the elements of this document may be the subject
14、of patent rights. ISO shall not be held responsible for identifying any or all such patent rights. ISO 16881-1 was prepared by Technical Committee ISO/TC 96, Cranes, Subcommittee SC 9, Bridge and gantry cranes. ISO 16881 consists of the following parts, under the general title Cranes Design calculat
15、ion for rail wheels and associated trolley track supporting structure: Part 1: General The following parts are under preparation: Part 2: Mobile cranes Part 3: Tower cranes Part 4: Jib cranes Part 5: Bridge and gantry cranes vIntroduction This part of ISO 16881 establishes requirements and gives gui
16、dance and design rules that reflect the present state of the art in the field of crane machine design. The rules given represent good design practice that will ensure fulfilment of essential safety requirements and adequate service life of components. Deviation from these rules normally could lead t
17、o increased risks or reduction of service life, but it is acknowledged that new technical innovations, materials, etc. may enable new solutions that result in equal or improved safety and durability. BS ISO 16881-1:2005blank1Cranes Design calculation for rail wheels and associated trolley track supp
18、orting structure Part 1: General 1 Scope This part of ISO 16881 gives the requirements for the selection of the size for iron or steel wheels and presents the formulae for the local stresses in crane structures due to the effects of the wheel loads. 2 Normative references The following referenced do
19、cuments are indispensable for the application of this document. For dated references, only the edition cited applies. For undated references, the latest edition of the referenced document (including any amendments) applies. ISO 4301-1, Cranes and lifting appliances Classification Part 1: General ISO
20、 4306-1, Cranes Vocabulary Part 1: General ISO 8686-1, Cranes Design principles for loads and load combinations Part 1: General ISO 8686-2, Cranes Design principles for loads and load combinations Part 2: Mobile cranes ISO 8686-3, Cranes Design principles for loads and load combinations Part 3: Towe
21、r cranes ISO 8686-4, Cranes Design principles for loads and load combinations Part 4: Jib cranes ISO 8686-5, Cranes Design principles for loads and load combinations Part 5: Overhead travelling and portal bridge cranes 3 Terms and definitions For the purposes of this document, the terms and definiti
22、ons given in ISO 4306-1 apply. 4 Requirements 4.1 Selection of rail wheels 4.1.1 Rail wheel size To determine the size of a rail wheel, the following checks shall be made: a) verify that the wheel is capable of withstanding the maximum load to which it will be subjected; b) verify that the wheel wil
23、l allow the appliance to perform its normal duty without abnormal wear. BS ISO 16881-1:20052 These verifications are made by means of the following two equations: max L 1, 9 P P bD u (1) mean L12 P Pcc bD u (2) where D is the wheel diameter, in millimetres; b is the useful width of the rail, in mill
24、imetres; P L is a limiting pressure dependent upon the metal used for the wheel, in newtons per square millimetre (N/mm 2 ), see Table 1; c 1is a coefficient depending on the speed of rotation of the wheel, see Table 2; c 2is a coefficient depending on the group of the mechanism, see Table 3; P maxi
25、s the maximum load on the wheel resulting from load combinations A, B or C, including consideration of both dynamic and static test loadings (load combinations are defined in ISO 8686-1 to ISO 8686-5); P mean is the higher mean load value resulting from Equation (3) when considering both load combin
26、ations A and B. The mean wheel load takes into account variations of the wheel loading, including, where applicable, positional changes of the handled load in relation to the supporting wheels during a working cycle. Equation (3) gives an approximate value of the resultant cubic mean loading. When t
27、he work process is well known, the cubic mean load can be calculated more accurately using the wheel loads resulting from the actual positions of the handled load. In this calculation, the maximum lifted load shall be used, coefficient c 2taking into account the variation of the load. 4.1.2 Determin
28、ing the mean load In order to determine the mean loads, the procedure is to consider the maximum and minimum loads withstood by the wheel in the loading cases considered, i.e. with the appliance in normal duty but omitting the dynamic coefficients when determining P mean . The values of P meanare de
29、termined by the Equation (3) in the load combinations A and B. min,A,B max,A,B mean 2 3 PP P + = (3) 4.1.3 Determining the useful rail width b For rails having a flat or slightly convex bearing surface, of total width, l, with rounded corners of radius, r, at each side (see Figure 1), the useful wid
30、th, b, shall be calculated using Equation (4): 2 blr = (4) For rails or wheels with a slightly convex bearing surface, the limiting pressure P Lmay be increased by 10 %. This allows for the improved contact of a rail to the rolling motion of the wheel. BS ISO 16881-1:20053In the case of a flat, tape
31、red or convex wheel running on the bottom flange of a beam, the useful width is calculated by Equation (5): bwr = (5) where the wheel tread of width, w, and the corner radius r are to be taken according to Figure 2. The wheel diameter, D, shall be taken as the mean diameter on the projected width (w
32、 r). Figure 1 Rail dimensions Figure 2 Dimensions of flange running wheel 4.1.4 Determining limiting pressure P LThe value of P Lis given in Table 1 as a function of the ultimate strength of the metal of which the rail wheel is made. BS ISO 16881-1:20054 Table 1 Values of P LUltimate strength of met
33、al used for rail wheelMinimum ultimate strength for rail f uP LN/mm 2N/mm 2N/mm 2 500 5,00 350 600 5,60 350 700 6,50 510 800 7,20 510 900 7,80 600 1 000 8,50 700 The qualities of metal correspond to cast, forged or rolled steels, and spheroidal graphite cast iron. The hardening of the wheel tread at
34、 the depth of 0,01D may be taken into account when selecting the value of P L . In the case of rail wheels with tyres, consideration must obviously be given to the quality of the tyre, which shall be sufficiently thick not to roll itself out. 4.1.5 Determining coefficient c 1The values of c 1depend
35、on the speed of rotation of the wheel and are given in Table 2. Table 2 Values of c 1Wheel rotation speed c 1Wheel rotation speed c 1Wheel rotation speed c 1r/min r/min r/min 200 0,66 50 0,94 16 1,09 160 0,72 45 0,96 14 1,10 125 0,77 40 0,97 12,5 1,11 112 0,79 35,5 0,99 11,2 1,12 100 0,82 31,5 1 10
36、1,13 90 0,84 28 1,02 8 1,14 80 0,87 25 1,03 6,3 1,15 71 0,89 22,4 1,04 5 1,16 63 0,91 20 1,06 56 0,92 18 1,07 4.1.6 Determining coefficient c 2Coefficient c 2depends on the group classification of the mechanism and is given in Table 3. BS ISO 16881-1:20055Table 3 Values of c 2Group classification of
37、 mechanism c 2M1 et M2 1,25 M3 et M4 1,12 M5 1,00 M6 0,90 M7 et M8 0,80 The formulae apply only to wheels whose diameters do not exceed 1,25 m. For larger diameters, experience shows that the permissible pressures between the rail and the wheel must be lowered. The use of wheels of greater diameter
38、is not recommended. NOTE The wheel selection method presented here is based on FEM 1.001-1988, Booklet 4, as revised in Booklet 9 in 1998. This method is based on the group classification of mechanisms (classes M1 to M8) that is equal to the classification of ISO 4301-1. 4.2 Determination of the cla
39、ss of mechanism of the travel wheel The determination of the mechanism class (according to ISO 4301-1) of the rail wheel is made in general terms as follows. a) The number of working cycles, C, is taken as the specified value or the upper limit of the given U-class. b) The average displacement of th
40、e travel motion, x m , is specified according to intended use. c) The wheel load spectrum class number, L i , shall be taken as specified or to be calculated from a given spectrum or description of work cycles. d) Total travel distance is L = 2Cx m . e) Running time T = L/v t , where v tis the norma
41、l travel speed of the motion (usually, the maximum speed). f) Operation time class number is calculated as T j= 1 + Int log (T/200,01 h)/log (2). EXAMPLE 1 T = 3 200, T j= 1 + Int log (3 200/200,01)/0,693 147 = 1 + Int (3,999 9) = 4; classe T 4 . EXAMPLE 2 T = 3 201, T j = 1 + Int log (3 201/200,01)
42、/0,693 147 = 1 + Int (4,000 4) = 5; classe T 5 . g) The mechanism class number is calculated as m m= L i+ T j 2. T j , L i , and m mshall be understood as integer numbers, e.g. 5, or as the corresponding symbol, T 5. 4.3 Determination of local stresses due to wheel loads The local stresses due to th
43、e wheel forces of a crab or a crane may be determined according to Annexes A and B. When the permissible stress method is used, the local stresses according to Annexes A and B, combined with the global stresses due to the rated loads, shall not exceed the permissible stresses. When the limit state m
44、ethod is used, the local stresses shall be calculated with the loads multiplied by the relevant partial load factors, p . These stresses, combined with the global stresses, shall not exceed the yield stress divided by the material factor, m . Factors pand mshall be taken according to the relevant pa
45、rt(s) of ISO 8686. BS ISO 16881-1:20056 Annex A (informative) Distribution of wheel load under rail The local stresses in the welds or web rivets and webs of rail bearing beams which arise from wheel loads acting normally and transversely to the rail shall be determined in accordance with the rail a
46、nd flange system. The method presented in this annex is valid when the web and rail alignment meets the tolerances of ISO 12488-1. When the tolerances are exceeded, the resulting bending moments shall be taken into account. Unless a more accurate calculation is made, the local vertical stress in a w
47、eb or in the upper welds of girders due to a wheel load shall be calculated with the following Equation when the rail is supported immediately by the upper flange: max w 3 Z cc 0,32 F t tJ = (A.1) where F maxis the maximum wheel load including the amplification factors, it wis the web thickness (see
48、 Figure A.1); t cis the web thickness see Figure A.1 a), or the reduced weld throat thickness 1,4a see Figure A.1 b), or the reduced weld throat thickness 0,7a see Figure A.1 c). J cis the moment of inertia of the section made up of cross travel rail and a part of flange plate (hatched surface, see
49、Figure A.2) J cshall normally be calculated using 90 % of the available section of the crane rail. This value may be adjusted as the function of the expected number of cycles, load spectrum, alignment tolerances, and material of the rail and wheel. The wear limit used in the calculations shall be stated in the operating instructions. In the case of a clamped
