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Basic data
| Standard ID | GB/T 22437.1-2018 (GB/T22437.1-2018) |
| Description (Translated English) | Cranes -- Design principles for loads and load combinations -- Part 1: General |
| Sector / Industry | National Standard (Recommended) |
| Classification of Chinese Standard | J80 |
| Classification of International Standard | 53.020.20 |
| Word Count Estimation | 46,480 |
| Date of Issue | 2018-05-14 |
| Date of Implementation | 2018-12-01 |
| Older Standard (superseded by this standard) | GB/T 22437.1-2008 |
| Regulation (derived from) | National Standards Announcement No. 6 of 2018 |
| Issuing agency(ies) | State Administration for Market Regulation, China National Standardization Administration |
GB/T 22437.1-2018: Cranes -- Design principles for loads and load combinations -- Part 1: General
---This is a DRAFT version for illustration, not a final translation. Full copy of true-PDF in English version (including equations, symbols, images, flow-chart, tables, and figures etc.) will be manually/carefully translated upon your order.
Cranes--Design principles for loads and load combinations--Part 1. General
ICS 53.020.20
J80
National Standards of People's Republic of China
Replace GB/T 22437.1-2008
Design principle for crane load and load combination
Part 1. General
Part 1.General
(ISO 8686-1.2012, IDT)
Published on.2018-05-14
2018-12-01 implementation
State market supervision and administration
China National Standardization Administration issued
Content
Foreword I
1 Scope 1
2 Normative references 1
3 Terms and Definitions 1
4 symbol 1
5 General 2
5.1 General Principles 2
5.2 Two common methods of structural design or capability checking 3
5.3 Load estimation 3
5.4 Load category 3
6 Load and applicability factor 4
6.1 Conventional load 4
6.2 Accidental load 8
6.3 Special load 8
6.4 Other loads 11
7 Selection principle of load combination 12
7.1 Basic considerations 12
7.2 Load combinations during installation, disassembly and transport 15
7.3 Application of Table 3 15
7.4 Verification of the safety factor of rigid body stability 17
Appendix A (Normative Appendix) Application of Allowable Stress Design and Limit State Design Method 19
Appendix B (informative) General notes on the application of the dynamic coefficient φi 21
Appendix C (informative) Example of a model for estimating the coefficient φ4 of a hoisting machine operating on a track 22
Appendix D (informative) Determining the load generated by acceleration Example 26
Appendix E (informative) Example of analysis method for load (horizontal lateral force) caused by skewness 34
Appendix F (informative) Lifting drive type icon 39
Reference 42
Foreword
GB/T 22437 "Design Principles for Crane Load and Load Combination" is divided into five parts.
--- Part 1. General;
--- Part 2. Mobile cranes;
--- Part 3. Tower cranes;
--- Part 4. Boom cranes;
--- Part 5. Bridge and gantry cranes.
This part is the first part of GB/T 22437.
This part is drafted in accordance with the rules given in GB/T 1.1-2009.
This part replaces GB/T 22437.1-2008 "Design Principles for Crane Load and Load Combination", and GB/T 22437.1-
The main technical changes in.2008 are as follows.
--- Modify the "item load factor" to "item safety factor" (see Table 1 in Chapter 4, Table 4 of Chapter 4 of the.2008 edition);
--- Increased the dynamic effect coefficient φ9 caused by accidental loss of payload (see Table 1 in Chapter 4);
--- "When applying this part to different types of cranes operating under the same operating and environmental conditions, the equivalent equivalent resistance should be sought
The provisions of "force" are adjusted from Chapter 1 to Chapter 5 (see Chapter 5.1, Chapter 1 of the.2008 edition);
--- Added in the limit state method "If this part is used in combination with ISO 20332, the limit state method is the first necessary second order
The provisions of the method (see 5.2);
--- Adjust the load type from Chapter 6 to Chapter 5 (see Chapter 5, Chapter 6 of the.2008 edition);
--- Amend the "when the lifting load is off the ground" to "when the lifting payload leaves the ground" (see 6.1.1, 6.1.1 of the.2008 edition);
--- Modified the calculation formula of φ2 and the corresponding number table (see 6.1.2.1.1, 6.1.2.1 and 6.1.2.2 of the.2008 edition);
--- Added the expression "accuracy of axle parallelism" (see 6.2.2);
--- Added the expression "for the verification calculation of the test load, the minimum wind speed should be considered 5.42m/s" (see 6.3.2);
--- Increased the "load caused by accidental loss of payload" (see 6.3.5);
--- Increased the "quality of crane or crane parts" (see 7.3.7);
--- Added "quality that is advantageous or unfavorable for structural calculations" (see 7.3.7.1);
--- Added "sub-safety factor for crane quality" (see 7.3.7.2);
--- Increased the "safety factor for crane quality" (see 7.3.7.3);
--- Added "sub-safety factor applicable to loads caused by displacement" (see 7.3.8);
--- Added "sub-item safety factor for verifying the stability of rigid body" and the corresponding number table (see 7.4);
This section uses the translation method equivalent to ISO 8686-1.2012 "Design Principles for Crane Load and Load Combinations Part 1.
General.
The documents of our country that have a consistent correspondence with the international documents referenced in this part are as follows.
---GB/T 5905-2011 Crane test specifications and procedures (ISO 4310.2009, IDT)
---GB/T 6974 (all parts) Crane terminology [ISO 4306 (all parts)]
---GB/T 30024-2013 Crane metal structure capability verification (ISO 20332.2008, IDT)
This section has made the following editorial changes.
--- The text and the formula in the appendix are uniformly numbered;
--- Modify the absolute value of the relationship between the C.2.4 coefficient ξ and the coefficient α in Appendix C.
This part was proposed by the China Machinery Industry Federation.
This part is under the jurisdiction of the National Machinery Standardization Technical Committee for Lifting Machinery (SAC/TC227).
This section is responsible for drafting units. Taiyuan University of Science and Technology, Beijing Crane Transportation Machinery Design and Research Institute Co., Ltd.
Participated in the drafting of this section. Zoomlion Heavy Industry Co., Ltd., Jiangxi Gongyi Machinery Co., Ltd., and the Franck Heavy Industry Co., Ltd.
Limited company, Henan Mining Crane Co., Ltd., Shanghai Machinery Construction Group Co., Ltd.
The main drafters of this section. Xu Gening, Dong Qing, Zhang Pei, Qi Qisong, Ren Huili, Yu Lin, Jin Hongping, Ren Haitao, Chen Xiaoming.
The previous versions of the standards replaced by this section are.
---GB/T 22437.1-2008.
Design principle for crane load and load combination
Part 1. General
1 Scope
This part of GB/T 22437 specifies the general methods for various load calculations and the general principles for selecting load combinations. The purpose is to
Verification of the load carrying capacity of various crane metal structures and mechanical components as defined in ISO 4306-1.
The method is based on rigid body dynamic analysis and elastic static analysis, but also allows the use of theoretically and practically proven
A more advanced (calculation or test) method estimates the effect of the load and load combination and the value of the dynamic load factor.
This section has two different uses.
a) Develop more specific standards for different types of hoisting machinery, providing a common form, content and scope of parameter values.
b) agreement between the designer, the manufacturer and the purchaser on the combination of load and load for hoisting machinery without dedicated standards
a framework.
2 Normative references
The following documents are indispensable for the application of this document. For dated references, only dated versions apply to this article.
Pieces. For undated references, the latest edition (including all amendments) applies to this document.
ISO 4302 crane wind load estimation (Cranes-Windloadassessment)
ISO 4306 (all parts) Crane terminology (Liftingappliances-Vocabulary)
ISO 4310 Crane Test Specifications and Procedures (Cranes-Testcodeandprocedures)
ISO 20332 crane metal structure capability verification (Cranes-Proofofcompetenceofsteelstructures)
3 Terms and definitions
The following terms and definitions defined by ISO 4306 apply to this document.
3.1
Load loadloads
Acting externally or internally in the form of force, displacement or temperature, causing stress on the metal structure or mechanical components of the crane.
3.2
Dynamic analysis
< rigid body> studies the motion and internal forces of a system model assumed to be a non-elastic component.
3.3
Dynamic analysis
< Elastomer> A study of the elastic displacement, motion, and internal forces of a system model assumed to be an elastic component.
4 symbol
The main symbols used in this section are shown in Table 1.
Table 1 main symbols
Symbol description refer to the relevant content of this section
Φi reflects multiple dynamic load coefficients of dynamic effects
The φ1 action on the quality of the hoisting machinery reflects the lifting impact coefficient of the lifting gravity effect 6.1.1, Table 3
Lifting dynamic load factor of φ2 lifting ground load 6.1.2.1, Table 3
Φ3 reflects the sudden unloading impact coefficient of the dynamic effect of sudden unloading of partial loads. 6.1.2.2, Table 3
Φ4 reflects the operational impact coefficient of the dynamic effect of operation on uneven roads 6.1.3.2, Table 3
Φ5 Addition (decrease) speed dynamic load factor due to acceleration of crane drive mechanism 6.1.4, 6.3.6, Table 3
Φ6 reflects the lifting load coefficient of the dynamic load test load 6.3.2, Table 3
Φ7 reflects the elastic effect of the buffer collision elastic effect caused by the collision with the damper 6.3.3
The dynamic effect coefficient caused by the accidental loss of φ9 payload is 6.3.5, Table 3
α Dedicated symbol for determining the value of φ1 6.1.1
Lifting status of hoisting machinery specified in HC1~HC4 6.1.2.1.2~6.1.2.1.4
Lifting state level coefficient specified in β2 6.1.2.1.1~6.1.2.1.2, 6.12.1.5
Β3 is used to determine the φ3 value of the special symbol 6.1.2.2
Vh Stable lifting speed in m/s 6.1.2.1.3 (Table 2b)
Fx, Fx2, Fx4 buffering force 6.3.3
Γf is used to calculate the safety factor of allowable stress 7.3.2
Γp sub-item safety factor 7.3.3, Table 3, 7.3.7.2, 7.3.8, A.3
Γm resistance coefficient table 3, Appendix A
Γn high risk factor 7.3.6, Appendix A
m payload quality 6.1.2.2
mH total load quality 6.1.2.1.1, 6.3.1
Ηm=mH-ΔmH The remaining part (suspension) suspended on the hoisting machine 6.3.1
Note. More symbols used in the appendix will be defined in the appendix.
5 General
5.1 General principles
The purpose of the capability calculation verification in accordance with this section is to use mathematical methods to confirm that the crane is operating in accordance with the manufacturer's instructions.
The actual carrying capacity of the time.
The basis for verification of failure prevention (such as yielding, elastic instability or fatigue) is the accounting load caused by the crane structural parts and mechanical components.
Calculate whether the stress is less than the corresponding calculated strength.
Failure verification is also necessary to combat overturning stability. The overturning stability is calculated by the load and the overturning is calculated by the hoisting machinery.
The ratio of the anti-overturn calculation torque is determined. In addition, to ensure the stability of the hoist and/or to avoid lifting machinery and its parts
Unexpected movement, such as boom sling ropes, accidental unloading of fixed cables, or accidental sliding of lifting machinery, should also be made for certain forces
limit.
Consideration should be given to the effects of differences between the actual and theoretical geometries of mechanical and structural systems (eg tolerances and foundation sinking)
influences). Since this effect may cause the stress to exceed the specified limit value, it should be given when carrying out the crane load capacity check.
consider.
When applying this section to different types of cranes operating under the same operating and environmental conditions, the equivalent resistance to failure should be sought.
5.2 Two common methods of structural design or capability checking
a) permissible stress method which is the design stress generated by the combined load and the allowable stress determined by the type of the component or the test condition.
Line comparison. The allowable stress is determined based on experience and is considered to prevent loss due to yield, elastic instability or fatigue.
The margin of effectiveness.
b) limit state method which uses a partial safety factor to amplify the loads before combination and is specified by yield or elastic instability
The limit state is compared. The sub-item safety factor of each load is based on the probability of occurrence and the basis of the accuracy of the load that can be determined.
Up. The limit state value is composed of the strength value after the standard strength of the component is reduced to reflect the strength of the component and the geometric parameters.
Deviation.
If this part is used in conjunction with ISO 20332, the limit state method is the first necessary second order method.
A more detailed description of the application of the two methods is given in Appendix A.
5.3 Load estimation
In order to calculate the stress caused by the load, an appropriate crane model should be used. Causes time-varying loads according to the provisions of this section
The various loads of the effect (internal force) shall be estimated according to experience, test or calculation according to the equivalent static load. Rigid body dynamic analysis
The method uses some dynamic coefficients to estimate the forces required to simulate the response of the elastic system. Elastic dynamics analysis or on-site measurement
Try, but in order to reflect the smoothness of the operation, you need to consider the actual operation of the crane driver.
Regardless of the allowable stress method or the limit state method, when considering stability and displacement, the load, load combination, and dynamic load factor should be
Based on experience, consider setting other relevant standards, or set it based on test or statistical data. Used in this section
The parameters are considered to be determinable.
If a certain load is unlikely to occur (for example, a wind load acting on an indoor working crane), it should be omitted in the carrying capacity check.
meter. For the same reason, the load caused by the following conditions should also be omitted.
a) conditions prohibited in the crane machinery manual;
b) characteristics not provided in the design of the hoisting machinery;
c) Conditions that are prevented or prohibited in the design of the hoisting machinery.
If the probability of carrying capacity is checked, the corresponding conditions, in particular the acceptable probability of failure, should be indicated.
5.4 Load category
Chapter 6 gives the range of the dynamic load factor φi used to determine the load effect in the load and bearing capacity check.
Note. The specific values of a particular type of hoisting machinery (see the Preface) that meet the dynamic load factor range can be found in other parts of this standard.
The loads acting on the crane are divided into normal loads, accidental loads, special loads and other loads. When various types of loads are considered
It is considered when the machine is related or related to its use.
a) Conventional loads occur during normal operation and should be considered in the ability to check for yield, elastic instability, and fatigue failure. they
Is the acceleration or deceleration of the weight of the crane and the lifting load caused by gravity and drive mechanism, brake and various bits
The load caused by the shift.
b) Accidental loads and effects are less likely to occur and are not considered in fatigue estimation. They include wind, snow, ice, and temperature from working conditions.
And the load caused by the skewing operation.
c) Special loads and their effects are rare and are not considered in fatigue estimation. They include winds from trials and non-working conditions.
Impulse and tipping, unplanned downtime, transmission failure, and loads caused by external excitation of the hoisting machinery foundation.
d) Other loads include installation and disassembly loads as well as loads on platforms and channels.
The category to which the load belongs is not a sign of the importance or criticality of the load. For example, the mounting and dismounting loads are in the last type,
However, special attention should be given because a considerable number of accidents occur during the loading and unloading phase.
Appendix B gives general comments on the application of the coefficient φi.
6 Load and applicable coefficient
6.1 Conventional load
6.1.1 Lifting gravity effect on the mass of the lifting machinery
The quality of the hoisting machinery shall include certain components that are always in the fixed position of the hoisting machinery during operation, except for the payload (see
6.1.2). For certain lifting appliances or certain applications, it may be necessary to superimpose the quality of the material crust, such as coal or similar powder.
Bonded to the hoist and its parts.
The gravity generated by the mass of the hoisting machinery should be multiplied by the hoisting impact coefficient φ1, where φ1=1±α, 0≤α≤0.1, using this method
The vibration excitation of the lifting machine metal structure is considered when the lifting payload leaves the ground. In order to reflect the range of the vibration pulse effect
The lower limit, which usually takes the upper and lower limits.
The hoisting impact coefficient φ1 can be applied to the design of the hoisting machinery structure and its support. In some cases, in order to find components and components
For the most dangerous load, the upper and lower limits of the coefficient should be used.
Appendix B gives general comments on the application of the coefficient φi.
6.1.2 Inertia and Gravity Effects of Vertical Action on Total Load
6.1.2.1 Lifting unconstrained ground load
6.1.2.1.1 General
When lifting an unconstrained ground load, the dynamic effect of transferring the load from the ground to the hoist is multiplied by the lifting dynamic load factor φ2
The gravity caused by the total load mass is considered (see Figure 1).
The mass of the total load includes the payload, the spreader, and the quality of the wire rope overhang.
The lifting dynamic load coefficient φ2 is determined by the formula (1).
Φ2=φ2min β2·vh (1)
In the formula.
22 --- the coefficient obtained according to the crane lifting state level (see Table 2a);
Vh --- Typical lifting speed of the drive system in m/s (see Table 2b);
The minimum value of φ2min---φ2 (see Table 2c).
Figure 1 Dynamic effect of lifting ground load
6.1.2.1.2 Lifting status level
According to the elastic characteristics of the crane and its support, the lifting state is divided into four levels HC1~HC4, which should be based on typical vertical load.
The displacement δ selects the lift state level (see Table 2a).
Table 2a Lifting status level
Displacement state level typical vertical load displacement δ β2/(s/m)
HC1 0.8m≤δ 0.17
HC2 0.3m≤δ< 0.8m 0.34
HC3 0.15m≤δ< 0.3m 0.51
HC4 δ< 0.15m 0.68
The displacement δ of a typical vertical load can be based on the maximum total load of the crane and its supporting structure and the wire rope system without regard to the increase factor.
Elastic static calculations are obtained.
Since the displacement δ of a typical vertical load varies with the structure of the crane, the maximum value of δ can be used to select the lifting state.
level.
6.1.2.1.3 Lifting drive level
According to the control characteristics of the hoisting drive mechanism when the weight of the load is transmitted from the ground to the crane, the hoisting drive is divided into 5
Level HD1~HD5. The lifting drive level is as follows.
HD1. no low speed available or the drive may not start at low speed;
HD2. The hoist drive can only be started at a low speed within a preset time;
HD3. The hoist drive control remains at a low speed until the hoisting load leaves the ground;
HD4. stepless speed regulation lifting drive control achieves continuous speed increase;
HD5. Stepless speed regulation hoist drive control automatically ensures that the dynamic load factor φ2 does not exceed φ2min.
Appendix F gives detailed information and examples of typical lift controls and their characteristics at each level.
Typical lifting speeds vh for combinations A1, B1 and C1 are shown in Table 2b.
The load combination C1 is used to reflect the special case where the hoisting mechanism starts operating at a higher speed than the load combinations A1, A2.
Table 2b is used to calculate the typical lifting speed of φ2 vh
Load combination
(see Chapter 7)
Lift drive level
HD1 HD2 HD3 HD4 HD5
A1, B1 vh, max vh, CS vh, CS 0.5vh, max vh=0
C1 vh,max vh,max 0.5vh,max vh,max 0.5vh,max
Vh,max---the maximum stable lifting speed of the main hoisting mechanism when the load combination is A1 and B1;
Vh,max---the maximum lifting speed caused by all drive mechanisms (for example, variable amplitude and hoisting motion) when the load combination is C1;
Vh, CS --- stable lifting creep speed
6.1.2.1.4 Minimum value of lifting dynamic load coefficient φ2
The minimum value of φ2 is determined according to the lift state level and the lift drive level (see Table 2c).
Table 2c φ2min value
Lifting status level
Lift drive level
HD1 HD2 HD3 HD4 HD5
HC1 1.05 1.05 1.05 1.05 1.05
HC2 1.10 1.10 1.05 1.10 1.05
HC3 1.15 1.15 1.05 1.15 1.05
HC4 1.20 1.20 1.05 1.20 1.05
6.1.2.1.5 Other methods
The size of φ2min can be determined by experiment or dynamic analysis. When using alternative methods, the actual drive system should be simulated
Characteristics and elastic properties under the total load of the crane support system. According to the simulation results, it is determined that it is equivalent to φ2min and β2.
Up state level.
6.1.2.2 Effect of sudden unloading of partial payload
For lifting machinery that is removed or dropped to a normal working condition with a partial payload, such as when using a grab or an electric disk, lifting
The maximum dynamic effect of the machine can be simulated by multiplying the payload by the sudden unloading impact factor φ3 (see Figure 2).
Figure 2 Sudden unloading impact coefficient φ3
The sudden unloading impact coefficient φ3 is given by equation (2).
Φ3=1-
Δm
(1 β3) (2)
In the formula.
m --- the quality of the payload;
Δm --- part of the mass removed or dropped from the payload mass;
33=0.5 for lifting appliances with grabs or similar slow unloading devices;
33=1.0 for lifting appliances with electric disks or similar quick unloading devices.
Appendix B gives general comments on the application of the coefficient φi.
6.1.3 Loads caused by running on uneven road surfaces
6.1.3.1 Cranes operating inside or outside the road
The dynamic effect of a loaded or empty hoisting machine operating inside or outside the road depends on the structural form of the crane (mass distribution),
The elasticity and/or load suspension mode of the crane, the speed of operation and the nature and condition of the running road surface. The dynamic effect should be based on
Tests, tests to estimate or use appropriate lifting machinery and models of running pavements for calculations.
6.1.3.2 Cranes operating in orbit
For a loaded or unloaded crane operating on a track with geometric or elastic properties, the dynamic effect due to wheel acceleration depends on
The structural form of the crane (mass distribution), the elasticity and/or suspension of the crane, the operating speed and the wheel diameter. And should be based on
Tests, tests to estimate or use appropriate crane and orbital models for calculations.
The vertical acceleration caused by the crane running on the track can be multiplied by the gravity of the crane and the total load mass by the operating impact coefficient φ4
consider. The relevant standards specify the orbital tolerances for several specific types of cranes and propose conditions in which the φ4 value can be taken as 1.
Appendix B gives general comments on the application of the coefficient φi.
Appendix C gives an example of a model for estimating the value of the operational impact coefficient φ4, which is used to consider the crane's high and low error in the absence of welding.
The vertical acceleration generated on the wheel when running on the track of the bit or gap joint.
6.1.4 Loads caused by acceleration of all crane drive mechanisms including hoisting drive mechanisms
The load caused by the drive mechanism to accelerate or decelerate in the crane can be calculated using a rigid body dynamic model. Lifting should be considered in the calculation
The geometric characteristics and mass distribution of the machine drive mechanism, as appropriate, should also take into account the resulting internal friction losses. For this purpose, the total load is considered fixed
At the top of the boom or directly below the trolley.
Rigid body analysis cannot directly reflect the elastic effect. In order to reflect the actual elastic effect, the mechanism is driven to increase (decrease) the dynamic load factor.
Φ5 is multiplied by the driving force change value ΔF which causes the addition ...
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