1、 Reference numberISO 1940-1:2003(E)ISO 2003INTERNATIONAL STANDARD ISO1940-1Second edition2003-08-15Mechanical vibration Balance quality requirements for rotors in a constant (rigid) state Part 1: Specification and verification of balance tolerances Vibrations mcaniques Exigences en matire de qualit
2、dans lquilibrage pour les rotors en tat rigide (constant) Partie 1: Spcifications et vrification des tolrances dquilibrage ISO 1940-1:2003(E) PDF disclaimer This PDF file may contain embedded typefaces. In accordance with Adobes licensing policy, this file may be printed or viewed but shall not be e
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7、.org Published in Switzerland ii ISO 2003 All rights reservedISO 1940-1:2003(E) ISO 2003 All rights reserved iiiContents Page Foreword. v Introduction . vi 1 Scope 1 2 Normative references . 1 3 Terms and definitions. 2 4 Pertinent aspects of balancing 4 4.1 General. 4 4.2 Representation of the unba
8、lance 4 4.3 Unbalance effects . 6 4.4 Reference planes for balance tolerances. 6 4.5 Correction planes 6 4.6 Permissible residual unbalance 7 5 Similarity considerations . 8 5.1 General. 8 5.2 Permissible residual unbalance and rotor mass . 8 5.3 Permissible residual specific unbalance and service s
9、peed . 8 6 Specification of balance tolerances 9 6.1 General. 9 6.2 Balance quality grades G . 9 6.3 Experimental evaluation. 10 6.4 Methods based on special aims 13 6.5 Methods based on established experience 13 7 Allocation of permissible residual unbalance to tolerance planes . 13 7.1 Single plan
10、e . 13 7.2 Two planes. 13 8 Allocation of balance tolerances to correction planes . 15 8.1 General. 15 8.2 Single plane . 15 8.3 Two planes. 16 9 Assembled rotors 16 9.1 General. 16 9.2 Balanced as a unit. 16 9.3 Balanced on component level . 16 10 Verification of residual unbalance 16 10.1 General.
11、 16 10.2 Acceptance criteria . 17 10.3 Verification on a balancing machine. 17 10.4 Verification outside a balancing machine 17 Annex A (informative) Example of the specification of permissible residual unbalance based on balance quality grade G and allocation to the tolerance planes 19 Annex B (inf
12、ormative) Specification of balance tolerances based on bearing force limits 22 Annex C (informative) Specification of balance tolerances based on vibration limits . 23 Annex D (informative) Specification of balance tolerances based on established experience . 24 ISO 1940-1:2003(E) iv ISO 2003 All ri
13、ghts reservedAnnex E (informative) Rules for allocating balance tolerances from tolerance planes to correction planes .26 Bibliography28 ISO 1940-1:2003(E) ISO 2003 All rights reserved vForeword ISO (the International Organization for Standardization) is a worldwide federation of national standards
14、bodies (ISO member bodies). The work of preparing International Standards is normally carried out through ISO technical committees. Each member body interested in a subject for which a technical committee has been established has the right to be represented on that committee. International organizat
15、ions, governmental and non-governmental, in liaison with ISO, also take part in the work. ISO collaborates closely with the International Electrotechnical Commission (IEC) on all matters of electrotechnical standardization. International Standards are drafted in accordance with the rules given in th
16、e ISO/IEC Directives, Part 2. The main task of technical committees is to prepare International Standards. Draft International Standards 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
17、the member bodies casting a vote. Attention is drawn to the possibility that some of the elements of this document may be the subject of patent rights. ISO shall not be held responsible for identifying any or all such patent rights. ISO 1940-1 was prepared by Technical Committee ISO/TC 108, Mechanic
18、al vibration and shock, Subcommittee SC 1, Balancing, including balancing machines. This second edition cancels and replaces the first edition (ISO 1940-1:1986), which has been technically revised. The most important change is the introduction of reference planes for balance tolerances instead of us
19、ing the correction planes as tolerance planes. ISO 1940 consists of the following parts, under the general title Mechanical vibration Balance quality requirements for rotors in a constant (rigid) state: Part 1: Specification and verification of balance tolerances Part 2: Balance errors ISO 1940-1:20
20、03(E) vi ISO 2003 All rights reservedIntroduction A general introduction to balancing standards will be given in ISO 19499 (under preparation). For rotors in a constant (rigid) state, only the resultant unbalance and the resultant moment unbalance (resultant couple unbalance) are of interest, both t
21、ogether often expressed as dynamic unbalance. The balancing machines available today enable unbalance to be reduced to low limits. However, it would be uneconomical to reduce the unbalances to these limits. On the contrary, it is necessary to specify the balance quality requirement for any balancing
22、 task. Of similar importance is the verification of residual unbalances. For this verification, different balance errors have to be taken into account. An improved procedure to handle errors of the balancing machine is described in connection with ISO 1940-2. INTERNATIONAL STANDARD ISO 1940-1:2003(E
23、) ISO 2003 All rights reserved 1Mechanical vibration Balance quality requirements for rotors in a constant (rigid) state Part 1: Specification and verification of balance tolerances 1 Scope This part of ISO 1940 gives specifications for rotors in a constant (rigid) state. It specifies a) balance tol
24、erances, b) the necessary number of correction planes, and c) methods for verifying the residual unbalance. Recommendations are also given concerning the balance quality requirements for rotors in a constant (rigid) state, according to their machinery type and maximum service speed. These recommenda
25、tions are based on worldwide experience. This part of ISO 1940 is also intended to facilitate the relationship between the manufacturer and user of rotating machines, by stating acceptance criteria for the verification of residual unbalances. Detailed consideration of errors associated with balancin
26、g and verification of residual unbalance are given in ISO 1940-2. This part of ISO 1940 does not cover rotors in a flexible state. The balance quality requirements for rotors in a flexible state are covered by ISO 11342. 2 Normative references The following referenced documents are indispensable for
27、 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 1925:2001, Mechanical vibration Balancing Vocabulary ISO 1940-2, Mechanical vibration Balance quality
28、 requirements of rigid rotors Part 2: Balance errors ISO 1940-1:2003(E) 2 ISO 2003 All rights reserved3 Terms and definitions For the purposes of this document, the terms and definitions given in ISO 1925 apply. For the convenience of users, some of these definitions are cited below. NOTE Some of th
29、ese definitions are at present under review. 3.1 balancing procedure by which the mass distribution of a rotor is checked and, if necessary, adjusted to ensure that the residual unbalance or the vibration of the journals and/or forces on the bearings at a frequency corresponding to service speed are
30、 within specified limits ISO 1925:2001, definition 4.1 3.2 unbalance condition which exists in a rotor when vibration force or motion is imparted to its bearings as a result of centrifugal forces ISO 1925:2001, definition 3.1 3.3 initial unbalance unbalance of any kind that exists in the rotor befor
31、e balancing ISO 1925:2001, definition 3.11 3.4 residual unbalance final unbalance unbalance of any kind that remains after balancing ISO 1925:2001, definition 3.10 3.5 resultant unbalance vector sum of all unbalance vectors distributed along the rotor NOTE 1 See notes to definition 3.6. ISO 1925:200
32、1, definition 3.12 NOTE 2 This can be expressed as r1KkkUU=JJ GJJGwhere rUJJ Gis the resultant unbalance vector (gmm); kUJJ Gare the individual unbalance vectors, numbered 1 to K. 3.6 resultant moment unbalance vector sum of the moments of all the unbalance vectors distributed along the rotor about
33、the plane of the resultant unbalance ISO 1940-1:2003(E) ISO 2003 All rights reserved 3NOTE 1 The resultant unbalance together with the resultant moment unbalance describe completely the unbalance of a rotor in a constant (rigid) state. NOTE 2 The resultant unbalance vector is not related to a partic
34、ular radial plane, but the amount and angular direction of the resultant moment unbalance depend on the axial location chosen for the resultant unbalance. NOTE 3 The resultant unbalance vector is the vector sum of the complementary unbalance vectors of the dynamic unbalance. NOTE 4 The resultant mom
35、ent unbalance is often expressed as a pair of unbalance vectors of equal magnitude, but opposite directions, in any two different radial planes. NOTE 5 This can be expressed as ()rr1KUk kkP zzU=JG G G JJ Gwhere rPJGis the resultant moment unbalance (gmm2); kUJJ Gare the individual unbalance vectors,
36、 numbered 1 to K; rUzGis the axial position vector from a datum mark to the plane of the resultant unbalance rUJJ G; kzGis the axial position vector from the same datum mark to the plane of kUJJG. NOTE 6 Adapted from ISO 1925:2001, definition 3.13. 3.7 couple unbalance pair of unbalance vectors of e
37、qual amount but opposite angles, in two radial planes, forming a moment unbalance with the plane distance 3.8 dynamic unbalance condition in which the central principal axis has any position relative to the shaft axis NOTE 1 In special cases it may be parallel to or may intersect the shaft axis. NOT
38、E 2 The quantitative measure of dynamic unbalance can be given by two complementary unbalance vectors in two specified planes (perpendicular to the shaft axis) which completely represent the total unbalance of the rotor in a constant (rigid) state. NOTE 3 Adapted from ISO 1925:2001, definition 3.9.
39、3.9 amount of unbalance product of the unbalance mass and the distance (radius) of its centre of mass from the shaft axis NOTE Units of amount of unbalance are gram millimetres (gmm). ISO 1925:2001, definition 3.3 3.10 angle of unbalance polar angle at which the unbalance mass is located with refere
40、nce to the given rotating coordinate system, fixed in a plane perpendicular to the shaft axis and rotating with the rotor ISO 1925:2001, definition 3.4 ISO 1940-1:2003(E) 4 ISO 2003 All rights reserved3.11 unbalance vector vector whose magnitude is the amount of unbalance and whose direction is the
41、angle of unbalance ISO 1925:2001, definition 3.5 3.12 state of a rotor state determined by the unbalance behaviour with speed, the types of unbalance to be corrected, and the ability of the rotor to maintain or to change the position of its mass elements and their centres of mass relative to each ot
42、her within the speed range NOTE 1 Unbalances in most cases to not change considerably with speed. Contrary to the definitions used up to now (ISO 1925) even modal unbalances are not speed dependent. Only a special cases do unbalances change considerably with speed. NOTE 2 Mass elements are useful me
43、ans to describe the mass distribution of a rotor and possible changes with speed. Mass elements can be finite elements, or parts or components. NOTE 3 The rotor state is also influenced by its design, construction and assembly. NOTE 4 The response of the rotor to unbalance can change with the speed
44、range and its bearing support conditions. The acceptability of the response is determined by the relevant balance tolerances. NOTE 5 The speed range covers all speeds from standstill to the maximum service speed, but can also include an overspeed as a margin for service loads (e.g. temperature, pres
45、sure, flow). NOTE 6 With regard to balancing, only changes in the position of rotor mass elements not symmetric to the shaft axis need to be considered. 3.13 constant (rigid) rotor state state of a rotor where the unbalances are not changing considerably with speed, only the resultant unbalance and/
46、or the resultant moment unbalance are out of specified limits, and the position of all mass elements of the rotor relative to each other remains sufficiently constant within the speed range NOTE The unbalance of a rotor in its constant state can be corrected in any two (arbitrarily selected) planes.
47、 4 Pertinent aspects of balancing 4.1 General Balancing is a procedure by which the mass distribution of a rotor is checked and, if necessary, adjusted to ensure that the residual unbalance or the vibration of the journals and/or forces at the bearings at a frequency corresponding to service speed a
48、re within specified limits. Rotor unbalance can be caused by design, material, manufacturing and assembly. Every rotor has an individual unbalance distribution along its length, even in a series production. 4.2 Representation of the unbalance One and the same unbalance of a rotor in a constant (rigi
49、d) state can be represented by vectorial quantities in various ways, as shown in Figures 1a) to 1f). Figures 1a) to 1c) show different representations in terms of resultant unbalance and resultant couple unbalance, whereas Figures 1d) to 1f) are in terms of a dynamic unbalance in two planes. NOTE 1 The resultant unbalance vector may be located in any radial plane (without changing amount and angle); but the associated resultant couple unbalance is dependent
