Some standard content:
National Standard of the People's Republic of China
Design rules for cranes
UDC621.87
GB3811—83
1.1 This rule applies to electric-driven bridge cranes, gantry cranes, loading and unloading bridges, portal cranes, tower cranes, floating cranes, cranes with electric energy as the lifting mechanism, as well as deck cranes, belt hoists, tire hoists, steam hoists and cable cranes.
Note: floating cranes. Medium-sized cranes do not meet the requirements of relevant user specifications. 1.2 This rule is the necessary criterion and common technical basis for crane design, but does not include special issues of the above crane design. Any other calculation method that has been proved to be correct by theory and practice may also be adopted in the design after consultation and agreement between the design department and the user. Various and professional crane design rules and standards should not conflict with this rule. 1.3 This specification was formulated with reference to the standards of the International Organization for Standardization (ISO) 1S(4301-1980 "Hoisting Equipment", 1S(4302-1981 "Hoisting Machinery - Classification of Hoists", 1S(4305-1981 "Determination of Stability of Mobile Cranes", 1S04308-1981 "Crane - Selection of Wire Ropes" and 1S04310-1981 "Test Period and Procedure for Cranes".
2 General
2.1 Crane working level
2.1.1 Crane utilization level
Crane utilization level is divided into ten levels according to the total number of working cycles during the design life of the crane. Table 1 Crane utilization level
Utilization level
Published by National Bureau of Standards on August 3, 1983
Total number of working cycles A
1,6 × 101
3.2 × 104
H.3 × 104
1. 25 × 1rgs
2. 5 × 10
1×106
Infrequent use
Use lightly
Use regularly
Use frequently
Busy use
198405 a1 Implementation
GB 8811-83
2.1.2 Load state of crane
The concept of load state indicates the severity of the load on the crane, which is related to two factors, namely, the ratio of the rated load to the rated load. The graph showing the relationship between (
) and the ratio of the number of actions of a particular lifting load P to the total number of lifting cycles N is called load spectrum. The load spectrum coefficient K is calculated by formula (1), K-2[(
Wu: K-—load spectrum coefficient||tt ||n; ... a load P, the number of actions
the total number of cycles, N-En
the i-th lifting load, P, P, P...P., the maximum lifting load,
index, here take m=3.
The load state of the crane is divided into 4 levels according to the nominal micro-spectrum coefficient, see Table 2 Table 2 Load state of the crane and its nominal micro-spectrum coefficient K, load
chemical meaning E load spectrum coefficient K,
rarely rated high, - can lift light Micro loads sometimes exceed the rated load, medium loads often exceed the rated load, and the lifting capacity is usually lower than the rated load. When the actual load change of the crane is known, first calculate the actual load spectrum coefficient according to formula (1), and select the closest nominal value of this calculation characteristic according to Table 2 as the load spectrum coefficient of the crane. If the actual load condition is not written when designing the crane, it can be calculated according to experience according to Table 2 " Select a suitable auxiliary load status level from the content in the "Instructions" column. 2.1.3 Division of crane working levels
According to the utilization level and load status of the crane, the crane working level is divided into eight levels from A1 to A8, as shown in Table 3. For examples of crane working levels, see Appendix A (examination material).
Table? Division of crane working levels
Nominal estimated harmonic coefficient
Q3· to
Q: Extra heavy
2.2 Calculated load
GB 3811-83
2.2.1 Self-weight load PG
Self-weight load refers to the weight of the crane's structure, mechanical equipment, electrical equipment, storage bins attached to the crane, continuous conveyors and materials on them. Except for the gravity specified in Article 2.2.2. 2.2.2 Lifting load Po
Lifting load refers to the weight of the lifting mass. The lifting mass plate includes the mass plate of the largest effective object that can be lifted, the picking device (lower pulley block, hook, lifting beam, grab, container, lifting electromagnet, etc.), the hanging parts and other equipment in the lifting process. The weight of the lifting wire rope with a lifting height of less than 50m can be ignored. 2.2.3 Overlift impact coefficient P
When the lifting mass is suddenly lifted off the ground or lowered and braked, the heavy load will produce an impact in the opposite direction of its acceleration. When considering the load combination of this working situation, the deadweight load specified in 2.2.1 should be multiplied by the lifting impact coefficient, 0.9≤bar<1.1. 2.2.4 Lifting load dynamic coefficient
When the lifting mass is suddenly lifted off the ground or lowered and braked, additional dynamic load will be generated on the bearing structure and transmission mechanism. When considering the load combination of this working situation, the lifting load specified in 2.2.2 should be multiplied by the lifting load dynamic load coefficient A2 greater than 1. The value is generally in the range of 1.0 to 2.0. The greater the lifting speed, the more rigid the system, the more intense the support, and the greater the value of A. Appendix (reference) provides an estimation method for the value of A.
2.z.5 Sudden unloading impact coefficient A
When the lifting mass is partially or completely unloaded, a dynamic load reduction effect will be generated on the structure. The reduced lifting load is equal to the product of the impact coefficient P of the case and the lifting load specified in Article 2.2.2. P is calculated according to test (2). 9-1
Wu Zhong Am-
Pg = 0.5-
4m=(1 +Bg)
The mass of the part of the lifting mass pan that is suddenly unloaded, kg! Lifting mass pan, kg!
-For grab bucket cranes or similar cranes: -For electromagnetic cranes or similar cranes.fa =1.0-
2.6 Operation impact coefficient?4
When a crane or part of its equipment is running along a road or track, the moving mass will produce vertical impact due to the unevenness of the road or track. When considering this load combination, the load specified in 2.2.1 and 2.2.2 should be multiplied by the operation impact coefficient 1. When running on rails, A is calculated according to formula (3). -1.100.058
Wu Zhong, -
The height difference between the two track surfaces at the first track coupling, mm1Operation speed, m/s.
2.2.7 Horizontal load
2.2.7.1 Operation impact coefficient The force Pm
is calculated by multiplying the inertia force of the lifting mass and the running acceleration of the machine itself by 1.5 times the product of the mass m and the running acceleration, and is not greater than the adhesion between the driving wheel and the rail. "1.6 times" is to consider the dynamic effect of the sudden increase and mutation of the crane driving force. The inertia force acts on the corresponding mass. The lifting mass of the hanging piece is treated as rigidly connected to the crane. Acceleration (deceleration) speed a and the corresponding acceleration (deceleration) time! If the user has no special requirements, it is generally selected according to the recommended values in Appendix C (reference).
2.2.7.2 [Hydraulic half force 1 boom crane during rotation and luffing movement,When the slewing and luffing mechanism moves, the horizontal force generated by the hoisting mass plate (including wind force, inertia force generated during luffing and slewing start and brake, and centrifugal force during slewing movement) is calculated according to the horizontal component force caused by the deflection angle of the hoisting rope relative to the plumb line. 11
G3811—83
When calculating the damage of the motor and the marks and wear of the mechanical parts, the deflection angle of the hoisting rope under the working condition is used as 1. When calculating the strength and anti-overturning stability of the crane mechanism, the maximum deflection angle of the hoisting rope under the working condition is used. The centrifugal force of the crane's own mass is usually ignored. In the calculation of the crane's metal structure, when the slewing and luffing mechanism of the frame crane is started or braked, the horizontal force generated by the crane's own mass plate and the hoisting mass house (at this time, it is regarded as being rigidly connected to the crane arm) is: 1.5 times the product of the acceleration of the mass plate and the mass center. The centrifugal force of the crane's own mass is generally ignored. At this time, the wind direction to which the hoisting mass is subjected shall be calculated separately and superimposed in the most unfavorable direction. When the calculated horizontal force of the hoisting mass is greater than the water stress calculated according to the swing angle, the added inverse value shall be reduced. 2.2.7.3 Horizontal lateral force during crane skew operation The horizontal lateral force P generated by the weight of a bridge-type crane during the operation of a man-car and a vehicle and acting on the wheel rim or the guide wheel in the water shall be calculated according to Appendix E (participating parts). 2.2.8 Collision load
2.2.8.1 The collision load P acting on the buffer. 1. The kinetic energy absorbed by the buffer under the following collision inverse is calculated: For those without dynamic deceleration devices or limit switches, the speed of the trolley at the time of collision is 85% of the rated operating speed, and the trolley is the rated speed limit. For those with dynamic deceleration devices or limit switches, the actual collision speed after deceleration shall not be less than 10% of the rated inverse operating speed.
2.2.8.2 The fixed connection of the buffer and the buffer stopper shall be calculated according to the condition of the crane hitting the rated speed. 2.2.8.3 When calculating the collision load, for cranes equipped with guides to limit the swing of the load, the load shall be taken into account. For cranes with free swing of the load below, the kinetic energy of the load shall not be taken into account. 2.2.8.4 The distribution of the collision load on the crane depends on the mass distribution of the crane (some cranes also include the constant weight). When calculating, the trolley is considered to be in the most unfavorable position, and the lifting and running impact coefficient or the dynamic load coefficient of the lifting load shall not be considered. 2.2.9 The horizontal overturning force PsT of the trolley with rigid lifting guide frame When the trolley with rigid lifting guide frame hits an obstacle during the operation of the crane, a horizontal overturning force on the trolley is generated. After the lower end of the trolley without reverse wheels hits the obstacle. The limit value of the overturning horizontal force PsL is taken as the smaller of the two cases when the trolley is picked up (as shown in Figure 1a) or when the driving wheel of the trolley is hit. After the lower end of the trolley with reverse rollers hits the obstacle (see Figure 1b), the overturning horizontal force Ps1 is limited only by the slip condition of the driving wheel of the trolley. fr
The existence of the lower Ps working force causes the wheel pressure of the trolley to change. The influence of the trolley with only reverse rollers on the bridge is the greatest when the trolley is lifted up quickly. At this time, all loads (trolley self-support, hanging weight and Ps, force) are borne by the main beam. In addition to the above-mentioned forces, the direct additional load PsL of the Ps force on the main beam must be considered for the trolley with reverse rollers, Figure 1h. GB 3811-83
In the calculation, the lifting coefficient or the dynamic load coefficient is not considered, and the inertia effect is not considered. It is assumed that the component is at the lowest position of the weight and the weight acts on the lowest end of the hanging (the finished product). 2.2.10 Wind load PW
For cranes working in the open air, wind load conditions should be considered and the wind load is considered to be a kind of hydraulic force in any direction. The wind load of cranes is divided into working state wind load and non-working state wind load. Working state wind load Pw. is the maximum allowable wind force that the crane can withstand under normal working conditions. Non-working state wind load Pw. is the maximum allowable wind force that the crane can withstand when it is not working (such as the wind force generated by a storm) 2.2.10.1 Calculation of wind load
Wind load is calculated by formula (4):
Pm=CKhQA
Wu, fw
After the wind load acting on the crane or the object, N, wind force coefficient
K, r-wind pressure gradient variation coefficient,
Calculated wind, N/milk? ,
The windward area of the crane or the object vertically downwind, m*, A
When calculating the wind load of the crane, it should be considered that the wind is acting in the most unfavorable direction on the crane. 2.2.10.2 Calculated wind pressure 9
The wind pressure is related to the air density and wind speed, and can be calculated according to formula (5): 4=0,613V
Where 9-
-calculated wind pressure, N/m,
-calculated wind speed, m/s. The calculated wind pressure is determined by the calculated wind speed at a distance of 10 degrees from the open space. The calculated wind speed in the working state is considered to be the wind speed (instantaneous wind speed), and the calculated wind speed in the non-working state is considered to be the wind speed at 2 minutes. b. There are two types of calculated wind pressure: 41, 41, 41 is the calculated wind pressure of the crane in the working state, which is used to calculate the resistance of the motor power and the heat of the mechanism parts; the maximum calculated wind pressure of the crane in the working state is used to calculate the strength of the machine parts and metal structures. The calculated wind pressure of the crane in the non-working state is used to verify the rigidity and stability, calculate the short-term wear resistance of the drive device and the anti-overturning stability of the whole machine in the soft state, and the design of the whole machine's anti-twist stability and the anti-wind and anti-slip safety of the crane (see 2.3, the applicable specifications of the paragraph), regardless of the type of crane, select different calculated wind pressures according to the specifications. The calculated wind pressure of the crane in the non-working state is shown in the table below. Table 4 Calculation of wind pressure for yellow sails
Taiwan Province and South China Sea
Small working wind
Non-working calculated wind pressure
F
Note. ① Province and sea area This refers to the large sea rat area within 100km from the coastline. Special calculations are allowed for special periods of time for special lifting machines. Mobile lifting machines (i.e. steam cranes, wheel cranes and belt lifting items) are in the upper state (+ or lower pressure, when the lifting machine is less than 50m long, take X1254, m, avoid the length F reduced by 50m13
GB3811-B3 bzxZ.net
when the full use of the type of Hong determination.
The non-working calculation of wind pressure is: inland North China. Central China and South China are suitable for the minimum value! Northwest, southwest and northeast regions are suitable for the maximum value. The coastal area is bounded by the sea. The smaller value is taken to the north of the sea and the larger value is taken to the south. In the windy areas of mountains, rivers, lakes, valleys, areas often affected by strong storms (such as Hongjiang, etc.), or in the light wind area, the wind speed calculation of the operation point should be based on the annual maximum wind speed provided by the local meteorological data. The calculation formula (5) is used for floating cranes operating at sea. 9 = 10/m can be taken, but the wind pressure coefficient changes, that is, K. 1. 2.2.10.3 Wind pressure height variation coefficient K
The height variation is not considered in the calculation of wind pressure in the working state of the crane (K-1). The height variation is considered in the calculation of all cranes in the non-working state. The wind pressure height variation coefficient K is shown in the table. Table 5 Wind pressure height variation coefficient K
Height from ground (sea) surface
1.001.231.391
1.511.62.71
1.791.601.931.992.052.112.162.202.252.451.52.1.51.at-61.64j,n71,hg1.72j1.321.001.15 [1.25
1.321.381.43t.4?
Note, when calculating the accumulated wind load, the height can be divided into equal wind pressure zones of 20m, and the wind pressure can be calculated by multiplying the coefficient K of the midpoint height of the section. 2.2. 10.4 Wind coefficient C
The wind coefficient is related to the shape and size of the structure and is determined according to the following situations: a.
-The wind coefficients of single-piece structures and single-root members of general cranes are shown in Table 6. Table 6 Wind force coefficient of single-piece structure C
P-shaped frame made of steel (full rate A-0.3-0.6) steel, steel plate, profile frame, steel plate and box-shaped structure and pipe structure
Closed engine room, machine room, 4 balance, wire rope and items, etc. 5
Method: Where 1 is the length of the structure or structural member, h is the distance from the windward side, m4 is the estimated wind pressure (see Table 4), N/m, is the outer diameter, m.
The driver's room on the added surface takes C=1.1, and the empty one takes C=1.2. The wind force coefficient of the overall structure of the space structure composed of two parallel plane trusses can be based on the wind force coefficient of the single-piece structure, and the total b
front weight should be based on 2.2.10.5 items are calculated. r4
GB 3811—88
When the wind blows in the diagonal direction of the rectangular frame or box-shaped structure, when the length ratio of the sides of the rectangular surface is less than 2, the calculated wind load is taken as 1.2 times the wind force when the wind acts in the direction of the long side of the rectangle. When the length ratio of the sides of the rectangular surface is equal to or greater than 2, it is taken as the wind force when the wind acts in the direction of the long side of the rectangle.
The wind load of the space truss with a triangular cross section can be calculated by taking 1.25d.
times of the wind force on the projected area of the frame perpendicular to the wind direction.
The lower chord double-force steel sheet is a space truss with a normal triangular cross section. Under the action of lateral wind force, the centroid of its wind force coefficient is taken as 1.3.
When the wind blows at a certain angle to the long axis (or plane) of the structure, the wind force on the structure can be calculated by decomposing it into two directions f.
. The wind force along the wind direction can be calculated by formula (6): Pw-CKrqAsin2H
Windward area, m\
Where:
C-wind force coefficient,
the angle between the wind direction and the longitudinal axis of the structure.
2.2.10.5 Windward area 1
The windward area of the crane structure and its contents should be calculated according to the most unfavorable windward direction and the projection area on the vertical downwind plane. The windward area of a single-piece structure is:
Where: A
The outer contour area of the structure or object, as shown in Figure 2, is Ah,u", the structural fullness rate, that is, Ba =
, as shown in Table 7.
Figure 2 Schematic diagram of the area contour size of the structure or object? Structural fullness rate
Entity structure and objects:
Wind-bearing structure type and objects
Type of driving made of
The pipe frame structure
For two structures of the same type with the same height and parallel arrangement, consider the wind-blocking effect of the front piece on the dirty piece, and the total windward area is: A = , + F42
Where: 4,=P4r
The windward surface of the pure structure of the front piece:
Ag -pA
GB3811-83
The windward area of the rear plate structure:
--The wind reduction coefficient of the front plate of two adjacent frames to the rear plate, which is related to the fullness ratio of the first plate (front plate) structure and the fullness ratio a/(see section), as shown in the wind direction
Figure S parallel structure spacing ratio
Table truss structure wind reduction coefficient
Here, the wind reduction coefficient of other structures can be obtained by referring to the Appendix F (structure document). u.4
For parallel structures with the same plate type and the same spacing, under the action of longitudinal force, the multiple wind reduction effect of multiple plates should be considered. The total windward area of the structure is determined by the following formula: A=(+n+n?
The fullness rate of the front piece (first piece) structure is the outer wheel area of the front piece (first -) structure, and 2. -5
The windward area A calculated by formula (9) is used to calculate the total wind load of the structure by formula (4). Because the structural types of each piece are relatively low, it is only necessary to multiply it by the wind force coefficient of the whole piece in the formula
The windward area of the product
The windward area of the selected product should be determined by the projection of its actual wheel size on the wind direction plane. When the wheel size of the product is unclear, it is allowed to use an approximate method for calculation. 2.2.11 Temperature load
is generally not considered. When it is necessary, the user provides relevant information for calculation. 2.2.12 Installation load
GB 381183
When designing a crane, the load generated during the crane rigging process must be considered. For cranes working outdoors, the wind pressure during installation shall be calculated as 100N?㎡2.
2.2.13 Slope load
The slope load of the crane shall be calculated as follows: Mobile counterweight machine: Consider the specific situation when necessary. a.
b For track-mounted cranes, the slope load shall not be calculated when the track slope does not exceed 0.5%, otherwise it shall be calculated as per the actual Calculate the slope load. 2.2.14 Earthquake load
Generally, it is not considered.
Yes! Cranes working in underground areas can be inspected according to the order form requirements and the horizontal load of earthquakes can be considered. The horizontal load of earthquakes shall be determined according to the relevant underground specifications.
2.2.15 Technological load
The load generated by the crane during the operation due to the production process is the "technical load". It is used as a special load or special load.
2.2.16 Test load
Before the crane is used, it must be subjected to overload dynamic test and overload dynamic test. The test site should be solid and neat, the wind speed should not exceed 8.3m/s,
. Dynamic test load P.
The test load should act on the most unfavorable position of the crane, and the various movements and joint movements required to be completed by the crane during the test should be considered. The P value is taken as 110% of the rated load Pma. The dynamic coefficient A is calculated according to formula (10): -
b: Static test load cycle ar
Psr value is taken as 125% of the rated load Pmx. The test load is the most unfavorable position of the crane under the action of micro stress, and it should be semi-stable without impact. For cranes with special requirements, the test load is adjusted by the user and the manufacturer to be specified. 7.3 Crane anti-overturning stability and wind and anti-slip safety Mobile cranes should have a higher anti-overturning stability. Cranes operating on rails must also be calibrated for wind resistance. 3.1 Crane anti-frequency stability 1.1 Crane grouping Due to the different structural shapes and working conditions, the requirements for the anti-frequency stability of various cranes are also different. When checking their anti-frequency stability, the cranes should be divided into crane groups according to Table 9. Cranes with large mobility (such as section belt cranes and individual cranes), cranes with a history of non-critical operations (such as flow cranes), bridge-type cranes with extended site conditions (such as gantry cranes and external bridge cranes), cranes with high speed and high-speed operation, cranes with frequent changes in site conditions (such as non-travel cranes for loading and unloading) 2.3, 1.2 Calculation conditions GB 3811- 83
The anti-tilt stability of the crane shall be checked according to the conditions listed in Table 10. The verification of the installation status of tower cranes and the stability of floating cranes is shown in Appendix G (reference). Table 10
Verification of the working flow
Wind static
Wind dynamic
Non-working load under wind intrusion or load shedding
Note: 1. When checking the conditions 1, 4 and 1 group of cranes in Table 9, do not Consider the frequency of the overturning or overturning. The wind pressure is calculated according to the non-working state. 2.3.1.3 The anti-overturning stability of the crane should be tested under the most favorable load combination conditions according to the conditions listed in 11. If the sum of the moments of the various loads on the overturning side including the crane itself is greater than or equal to zero (≥0), the crane is considered stable. The calculation specifies that the sign of the moment acting on the crane is positive, and the sign of the moment causing the crane to overturn is negative. Consider various loads. The actual degree of influence on stability When checking the anti-overturn stability of the crane, each load factor should be multiplied by a load factor, as shown in Table 11.
Lifting unit system
Test conditions
Auxiliary factor
Load factor
Hydraulic force
[Including items]
i.25o.1po
Self-comparison and repair
Collect the static force and other numbers!
Convert to the rate|| tt||Together with the load-carrying street
the impact will exceed the annual machine must be verified L
（）Longitudinal (and)
stability (1 condition..2>
（2）Moving direction)
stability (.1 condition4)
think of the mutual chaos must be verified single yellow
stability≤flow4
birth: () the object has no wind scoop and the object water half inertia force can be combined together, the area is sure to obtain the angle of elasticity water half force (see 2.2.7.2 period). GB 381183
The load coefficient of the first phase (tire type and steam type) of the vertical machine is applicable to the same working conditions. @The frame can be rotated under the wind, and the frame can be rotated again. Ken channel and place the side rain, with the half balance jade direction blowing people's boom. 2.3.1.4 Cranes with operating mechanisms that are only used for fixed-point lifting without lifting load displacement must comply with 2.3.1.3, check the stability of each overturning edge of the supporting polygon (the line connecting the wheel or support and the ground contact point). You can also use the resultant force trajectory after multiplying all the loads of the crane by the stability coefficient selected according to Table 11 to check all overturning edges at the same time. When this resultant force trajectory is within the supporting polygon, the crane can remain stable in all directions. See Appendix (reference). The crane with load is also placed against the corresponding dangerous tilting edge (generally perpendicular to the moving direction) to verify the anti-tilting stability during operation. 2.3.2 Crane wind resistance and anti-microbial safety test: 2.3.2.1 Normal working state Paal.iPwi+ Pa-P Where: Pz Braking force generated by the brake of the operating mechanism, N: P-.-The maximum wind force on the crane in the working state (in the direction of flow), N: Fr Sliding force caused by the slope, N,-Crane operating friction resistance, calculated according to the recommended operating friction coefficient in Table 12, N. When the power P is greater than the adhesion between the wheel and the track, the adhesion between the wheel and the track is used instead, and the adhesion coefficient is 0.12. 12 Operating friction coefficient
Operating drag coefficient (center
sliding bearing
2.a.2.2 Non-operating state
Operating image resistance
Total wind pressure
P2>1.iPw,+P,-P,
Formula, P=
- The central braking force generated by the operating mechanism rail clamp along the track direction, N,- The maximum wind force (along the operating direction) received by the crane in the non-working state. When there is no fixing device, it is calculated according to the maximum non-operating wind pressure that may occur in the area. When there is a fixing device, it is calculated according to 600~80uN/m". The friction coefficient between the rail and the rail pin (with notches on the surface and high fire rate) is taken as 0.25, which is generally larger than the operating rail clamp pin of 1 operation. The force shall not be greater than 200N.
2.4 Safety protection of cranes
In order to ensure the safe and reliable operation of cranes, cranes should be equipped with corresponding safety devices, such as brakes, lifting load limiters. Torque brakes, travel limiters, buffers, windproof rail clamps, end fixation devices and electrical protection devices. 2.4.1 Brakes
The lifting mechanism and the variable mechanism must be equipped with reliable brakes. The selection principle of the brake can be found in 1 mechanism. 2.4.2 Lifting load limiter
For cranes with possible torsional load, when the user department makes a request, a lifting load limiter should be installed, and the overall error of the lifting load limiter should not be greater than the receiving.
2.4.9 Torque limiter
GB 3811-83
For cranes with lifting loads that vary with amplitude, force limiters should be installed, and their combined error should not exceed:%. 2.4.4 Stroke limiter
For all mechanisms that limit the travel of movement, corresponding stroke limiters should be installed. 2.4.6 Buffer
When the operating speed of the rail-type hoisting mechanism exceeds 0.33m/s, a buffer should be installed. The design principles of the buffer refer to 2.2.8 and 4.1.6.
2..6 Deflection indicator and limiter
Old gantry cranes and overhead cranes should be equipped with deflection indicators and limiters. 2.4.7 Anemometer
Anemometers should be installed for tall cranes in the external industry, and their height should be placed at the part of the hoist that is not blocked by the wind. When the wind speed reaches the operating limit wind speed, an alarm to stop the operation should be issued. . 2.4.B Track change, pinning device
Outdoor operation track type crane should be equipped with track real-time device. For gantry crane, when the non-working state exceeds 600N/m, and for other cranes, when the non-working state wind pressure exceeds 8N/m2, it must be equipped with a cable or other type of pinning device.
2.4.9 Relevant electrical protection requirements
Crane should be equipped with a fault switch, grounding protection, overhead obstacle signal light, etc. Cranes with special working needs should also be equipped with overspeed protection devices. Design principles are shown in 5 Electrical. 2.4.10 Driver's cab, walkway and handrail
2.4.10.1 The design of the driver's clearance size, operating instruments, display instruments, pendants, etc. should include relevant regulations for dynamic protection and safety.
The driver's cab should have a good view, and the position and size of the frame should not hinder the observation of the machine working conditions. The glass for the driver shall be tempered glass or other shatterproof glass. 2.4,10.$ When the suitable working temperature of the driver's cab is greatly different from the working environment temperature, measures to reduce or remove the spillage shall be taken in the engine room. 2.4.10.4 For other special working environments (such as dust and toxic hazards, radioactive hazards, etc.), the driver's cab shall take corresponding protective measures.
2.4.10.5 Walkway and handrails
The design of the walkway and handrails shall comply with Article 39.5. 3 Structure
3.1 Calculation principle
The allowable stress method shall be used for calculation in the wood specification. The strength, stability and rigidity of the crane's structural parts shall be calculated to meet the specified requirements, and the influence of material resistance shall generally not be considered. The fatigue strength calculation of the crane's components and connections shall be carried out in accordance with the provisions of Article 3.7. 3.2 Structural working class
The working class of crane structures is divided into eight classes, A1 to A8, according to the stress state (nominal stress spectrum coefficient) and the number of stress cycles (stress cycle coefficient) in the structural members. The classification method of crane structural working class is the same as that of crane working class, see the rules in Article 2.1. When referring to Table 1, Table 2 and Table 3, the "crane working class", "total number of working cycles", "load", "load concept", "load value", "nominal load spectrum coefficient" and "utilization level" in the table should be changed to "structural level", "total number of stress cycles", "stress", "stress state", "stress value", "nominal load spectrum coefficient" and "stress cycle level" accordingly. In formula (1), m is an index related to the fatigue calculation of structural members, which can be selected according to the actual situation of the structure. The load spectrum and working cycle number of the crane are the basis for determining the stress spectrum and stress cycle number of the component. The structural working class is not necessarily the same as the crane working class, depending on the specific situation.6 Buffers
When the running speed of the rail-type hoist exceeds 0.33m/s, a buffer should be installed. The design principles of the buffer refer to 2.2.8 and 4.1.6.
2..6 Skew indicators and limiters
Old gantry cranes and overhead cranes should be equipped with skew indicators and limiters. 2.4.7 Anemometers
A wind speed meter should be installed on tall cranes used in outdoor operations. Its height should be set at the part of the hoist that does not block the wind. When the wind speed exceeds the operating limit, an alarm should be issued to stop the operation. 2.4.B Track change and fixed installation
Track type hoists for outdoor operations should be equipped with track verifiers. For gantry cranes, when the pressure in the non-operating state exceeds 600N/m, and for other cranes, when the pressure in the non-operating state exceeds 8N/m2, a guying cable or other type of safety device must be installed.
2.4.9 Relevant electrical protection requirements
Crane should be equipped with a safety switch, grounding protection, overhead obstacle signal lights, etc. Cranes with special working requirements should also be equipped with overspeed protection devices. For design principles, see 5 Electrical. 2.4.10 Driver's cab, platform and handrail
2.4.10.1 The design of the driver's cab clearance size, operating instruments, display instruments, pendants, etc. shall include relevant regulations for dynamic protection and safety.
The driver's cab should have a good view, and the position and size of the frame should not hinder the observation of the machine. The glass component for the driver should be tempered glass or other shatterproof glass. 2.4,10.$When the suitable working temperature of the driver's cab is greatly different from the working environment temperature, measures to reduce or remove the overflow should be taken in the engine room. 2.4.10.4 For other special working environments (such as dust and toxic hazards, radioactive hazards, etc.), the driver's cab components shall take corresponding protective measures.
2.4.10.5 Walkways and handrails
The design of walkways and handrails shall comply with Article 39.5. 3 Structures
3.1 Calculation principles
The allowable stress method is used in the wood specification. The strength, stability and rigidity of the crane's structural parts shall be calculated to meet the specified requirements, and the influence of material properties is generally not considered. The fatigue strength calculation of crane components and connections shall be carried out in accordance with the provisions of Article 3.7. 3.2 Structural working class
The working class of crane structures is divided into eight classes, A1 to A8, according to the stress state (nominal stress spectrum coefficient) and the number of stress cycles (stress cycle coefficient) in the structural members. The classification method of crane structural working class is the same as that of crane working class, see the rules in Article 2.1. When referring to Table 1, Table 2 and Table 3, the "crane working class", "total number of working cycles", "load", "load concept", "load value", "nominal load spectrum coefficient" and "utilization level" in the table should be changed to "structural level", "total number of stress cycles", "stress", "stress state", "stress value", "nominal load spectrum coefficient" and "stress cycle level" accordingly. In formula (1), m is an index related to the fatigue calculation of structural members, which can be selected according to the actual situation of the structure. The load spectrum and working cycle number of the crane are the basis for determining the stress spectrum and stress cycle number of the component. The structural working class is not necessarily the same as the crane working class, depending on the specific situation.6 Buffers
When the running speed of the rail-type hoist exceeds 0.33m/s, a buffer should be installed. The design principles of the buffer refer to 2.2.8 and 4.1.6.
2..6 Skew indicators and limiters
Old gantry cranes and overhead cranes should be equipped with skew indicators and limiters. 2.4.7 Anemometers
A wind speed meter should be installed on tall cranes used in outdoor operations. Its height should be set at the part of the hoist that does not block the wind. When the wind speed exceeds the operating limit, an alarm should be issued to stop the operation. 2.4.B Track change and fixed installation
Track type hoists for outdoor operations should be equipped with track verifiers. For gantry cranes, when the pressure in the non-operating state exceeds 600N/m, and for other cranes, when the pressure in the non-operating state exceeds 8N/m2, a guying cable or other type of safety device must be installed.
2.4.9 Relevant electrical protection requirements
Crane should be equipped with a safety switch, grounding protection, overhead obstacle signal lights, etc. Cranes with special working requirements should also be equipped with overspeed protection devices. For design principles, see 5 Electrical. 2.4.10 Driver's cab, platform and handrail
2.4.10.1 The design of the driver's cab clearance size, operating instruments, display instruments, pendants, etc. shall include relevant regulations for dynamic protection and safety.
The driver's cab should have a good view, and the position and size of the frame should not hinder the observation of the machine. The glass component for the driver should be tempered glass or other shatterproof glass. 2.4,10.$When the suitable working temperature of the driver's cab is greatly different from the working environment temperature, measures to reduce or remove the overflow should be taken in the engine room. 2.4.10.4 For other special working environments (such as dust and toxic hazards, radioactive hazards, etc.), the driver's cab components shall take corresponding protective measures.
2.4.10.5 Walkways and handrails
The design of walkways and handrails shall comply with Article 39.5. 3 Structures
3.1 Calculation principles
The allowable stress method is used in the wood specification. The strength, stability and rigidity of the crane's structural parts shall be calculated to meet the specified requirements, and the influence of material properties is generally not considered. The fatigue strength calculation of crane components and connections shall be carried out in accordance with the provisions of Article 3.7. 3.2 Structural working class
The working class of crane structures is divided into eight classes, A1 to A8, according to the stress state (nominal stress spectrum coefficient) and the number of stress cycles (stress cycle coefficient) in the structural members. The classification method of crane structural working class is the same as that of crane working class, see the rules in Article 2.1. When referring to Table 1, Table 2 and Table 3, the "crane working class", "total number of working cycles", "load", "load concept", "load value", "nominal load spectrum coefficient" and "utilization level" in the table should be changed to "structural level", "total number of stress cycles", "stress", "stress state", "stress value", "nominal load spectrum coefficient" and "stress cycle level" accordingly. In formula (1), m is an index related to the fatigue calculation of structural members, which can be selected according to the actual situation of the structure. The load spectrum and working cycle number of the crane are the basis for determining the stress spectrum and stress cycle number of the component. The structural working class is not necessarily the same as the crane working class, depending on the specific situation.
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