Some standard content:
SY/T10003--1996 Standard of the Offshore Oil and Gas Industry of the People's Republic of China
Specification for Offshore Platform Cranes
Cranes1996-08-19 Issued
China National Offshore Oil Corporation
1996-08-19 Implementation
Strategic Specifications
Chapter 1
Chapter 2
Chapter 3
Chapter 4
Chapter 7
Chapter 8
Chapter 9
Chapter 10
Chapter 11
Chapter 12
Chapter 13
Chapter 11
Chapter 15
Appendix A
Crane Ratings
Structural Capacity Determined by Stress Framing
Design Appraisal and Test Test
Wire rope, pulley and drum
Luffing, heavy lifting and slewing mechanism of boom mechanism
Power equipment
Control device
Operational free travel protection device -
Other equipment and requirements
Component material requirements
Connection of main load-bearing components
Destruction inspection of components
Marking·
Example of key components
Minimum purchasing information
(32)
In order to meet the needs of developing offshore gas injection resources in my country, our company adopted the 988 edition of the "Offshore Platform Crane Specification" of the Taiwan Petroleum Institute of the United States, namely AP Spec2: & Suecificatian lor Oifshcre Cranex 1988. It was released as the recommended standard of China National Offshore Oil Corporation.
If there is any objection to the translation of technical standards, the translated text shall be used as the reference. In the design, construction and use of marine engineering, natural gas exploration and development projects, the laws, regulations and rules of the government and other competent authorities of the original country shall be followed. The data and quantitative calculation methods of environmental conditions such as wind, waves, currents, ice temperature and earthquakes in the original standards shall be implemented in accordance with the laws, regulations and rules promulgated by the competent departments of the People's Republic of China. Those that are suitable for my country's actual conditions can be used as reference: otherwise, the data and quantitative calculation methods that are suitable for China's actual environmental conditions shall be used. Regarding these digits, the legal unit is the main one, that is, the legal value is in front, and the corresponding position of the imperial unit is marked in brackets. In order not to change the original formula, curve shape characteristics, constants and coefficients, all the imperial units are still marked with imperial units. China National Offshore Oil Corporation
China National Offshore Oil Standardization Technical Committee 1993.11.15
Policy Statement
1. API publications are necessarily general in nature. When it comes to specific issues, please refer to local, state and federal laws and regulations:
2. API does not undertake the obligation to inform, train or prepare for the health and safety risks and prevention measures of their employees, nor does it assume their responsibilities under local, national or federal laws. 3. Any API mountain! Nothing in this publication shall be construed, by implication or otherwise, as granting any right to make, sell or practice any method, apparatus or product covered by the patent, nor shall anything in this publication be construed as exempting any person from liability for infringement of the patent.
1. Usually, the AP1 standard is reviewed at least once and revised, re-determined or revoked. Sometimes, this review period can be extended for a maximum of two years. As an AII standard, this publication shall be valid for no more than five years from the date of publication. Its validity period shall be extended when the publication is renewed. The status of publication can be checked from the AII editorial office (Tel. 214-748-3341). AFI (12091.ST.NwWashigton.D20005) Each publication and data catalog is updated quarterly. Preface
The American Petroleum Institute (APT) publishes various specifications to assist the purchase of standardized equipment and materials and to provide guidance to manufacturers on equipment or materials covered by API standards. These specifications are not intended to eliminate the need for good engineering skills, nor are they intended to prohibit anyone from purchasing or producing products that conform to other current standards in any way. The preparation and publication of API specifications and API public standards do not intend to prohibit anyone from purchasing products from companies that are not authorized to use the API logo in any way. ||tt ||API specifications are available to anyone who wishes to implement them. While the Society has made every effort to ensure the accuracy and reliability of the data in the specifications, the Society makes no representations, warranties, or guarantees regarding any API specification. The Society expressly disclaims any obligation or responsibility for damages resulting from the use of these specifications, for any violation of any United States, state, or municipal regulations with which the API specification may conflict, or for any infringement of any patent by the Society. Any manufacturer of equipment or materials that claims to comply with an API specification is responsible for complying with all the terms of the specification. However, the American Institute of Alcoholics makes no representations, warranties, or guarantees that such products actually conform to the applicable API label or specification. Manufacturers who wish to obtain a monogram license for their products may contact AF1 Dullaeffice at 211.Frvay.Ste.1700.allas:Texas 7520l Write for an application or purchase a copy of the Compoxite List of Manufacturers Licensed for usc of the AF1Mogram, Order No. 81-000c5. Foreword
This specification is the work of the API Offshore Engineering Committee. Some of the content in this publication has been changed from the previous edition. The changes are marked by a black line on the side of the paragraph, as shown on the left side of the paragraph. Some changes are significant, but some are merely editorial adjustments. Black lines are provided to draw the reader's attention to the changes, but API does not warrant the use of black lines. The purpose of this specification is to provide standards for offshore cranes suitable for use in drilling and production operations. Note: This edition of the specification replaces the third edition of March 1983. It includes all the changes decided to adopt at the 1957 conference, covering the scope of
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Chapter 1 Scope
This specification specifies the design, manufacture and testing requirements for pedestal-mounted revolving cranes as shown in Figure 1.1. Such revolving cranes are used to transport equipment or personnel to high-rise ships. This specification does not apply to the design, manufacture and testing of lower frames and/or emergency escape arrangements. 1.1.1 includes a method for determining the rated load capacity based on the allowable stress of load-bearing parts rather than the power transmission machinery, and includes the minimum technical requirements for materials, design, manufacture and testing. Detailed technical requirements are given in the text. 1.1.2 The list of structural parts covered by this specification is as follows. Some are shown in Figure 1.1: F&
a. Crane:
h. Top pulley block of boom:
c. Outrigger or ram at static end:
d. Luffing pulley or tightening device;
Gantry, pillar or herringbone:
Figure 1.: Crane assembly
f. Swivel superstructure;
R-swivel ring component:
h. Boom bottom pivot;
. Pulley rail:
Connecting screw or connector;
k Anchor bolt or fastener;
1. Base or foundation;
m. Main column or center column
1.2 Record retention
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Crane manufacturers should keep all inspection and test certificates for 20 years. The record can be found in the quality inspection procedure of the general fault, and its purpose is to correct or eliminate the factors causing faults in design, manufacture or inspection. No.
Boom telescopic back
Boom bottom pivot
Luffing mechanism
Luffing wire rope or boom rope
Boom pulley
Luffing liquid
Boom top pulley block or boom head
Intermediate boom section
Lower boom, bottom boom or root hip
Upper boom, top boom or End joint
Boom connection
Boom upper actuator
Boom top outrigger to form a push rod
Operation room
Balance weight
Luffing pulley block or tensioning rope
Gantry, column or herringbone
Hook block
Main column or center rail
Main hoisting drum
:Hook wire or load-bearing wire rope
Gravity ball
Base or foundation
Slewing parts
Auxiliary wire or auxiliary reinforcement hoisting drum
Auxiliary rope or auxiliary hoisting wire rope
Figure 1. 2 Crane terminology
Types see Figure 1. 1
Rated lifting capacity
Q/HS 7005-93
Crane ratings
Chapter 2
Rated lifting capacity is specified as static rating, which is the load that can be lifted in a quasi-static state when there is no relative motion between the crane and the lifted object. The dynamic rated lifting capacity is the load that can be lifted under the dynamic load conditions when there is relative motion between the crane and the lifted object, which is static lifting capacity! 2.1.1 Static Rated Lifting Capacity The static rated lifting capacity shall be the minimum of the following: a) the first design load of 75%; b) the maximum load determined by the wire rope design factor in accordance with Section 5.3; c) the maximum load determined by the wire rope tension when there is a load at the top of the boom under the wire rope design conditions designed by the manufacturer, and the maximum load determined by the wire rope design factor in Section 5.3 and the winding form of the variable-length wire rope; e) the maximum load determined by the boom rope in Section 5.3: 1) the maximum load determined by the effective tension of the variable-length wire rope under the pure wire rope retraction conditions designed by the manufacturer; In addition to the lifting wire rope itself, the vertical volume of the hook, pulley, hoisting element, etc. should be considered as part of the lifting volume. 1.1.2 Dynamic rated lifting capacity
The dynamic rated lifting capacity shall be the minimum of the following: a) The load obtained by dividing the Class 1 design load by the applicable dynamic load factor (or (r)) in Section 2.2; b) The load obtained by dividing the design static load of the base (also using the center column) by 1.5 times the applicable dynamic load factor (C, or C,) in Section 2.2; according to 3.1, the static load of the base can be determined by multiplying the Class 1 design load by 1.5 times the m; c) If applicable, the design static load of the slewing device shall be determined by dividing the applicable dynamic load factor (C or (r) in Section 2.2 by 3.75, according to 7.3.1 .The design static load of the slewing ring components can be determined by multiplying the Category 1 design load by 3.75: l) The maximum load determined based on the lifting wire rope threading pattern and the wire rope design factor in Section 5.3; e) When the boom head is loaded, the maximum load determined based on the rope threading pattern designed by the crane manufacturer and the effective tension of the lifting wire rope; f) The maximum load determined based on the boom luffing rope threading pattern and the wire rope design factor in Section 5.3; ) The maximum load determined based on the boom rope in Section 5.3; h) The maximum load determined based on the effective tension of the boom luffing rope and the rope threading pattern designed by the manufacturer. 2.1.3 Rated lifting capacity for personnel
The rated lifting capacity for personnel shall be the minimum of the following:) 25 mN Class II design load;
h) Maximum load determined by drawing the load-bearing wire rope and the wire rope design factors in accordance with Sections 5.3 and 5.1; c) Maximum load determined by the tension of the lifting wire rope when the boom head is under load under the drawing conditions designed by the manufacturer. In addition to the weight of the lifting wire rope, the net weight of the hook, personnel, etc. shall be considered as part of the lifting capacity. 2.2 Dynamic load factor
The dynamic load factor for cranes mounted on a supporting structure or on a floating structure shall be determined by the manufacturer according to the following. 2.2.1 Bottom-supported structure
a) When the purchaser provides a total forward tilt , heel, wind speed and the absolute vertical velocity at the lifting point on the cargo plate and the minimum effective hook velocity, the dynamic load coefficient (should be calculated using the following formula:
G.--I+(V.+V)
Where: C-dynamic load coefficient (bottom-supported structure). C is not less than 1.33;1 yuan (Note in Section 3.1.1, the fixed value on the floating structure. K:
Q/11S7005-93
V.--: Absolute vertical velocity of the hook: n/s1/s); V.--Absolute vertical velocity at the lifting point on the cargo pole. mn/s (I/) see the attached calculation ((Note); K---Vertical stiffness of the hook, N/milh/ft)8-Gravity acceleration. 9.81m/s (32.2 ft/*): L is the weight of the crane, N (II). L is an unknown number, so it is calculated step by step by approximation method. The most basic starting value of I. is the difference of the Class II undesigned load.
h) In the absence of other data provided by the purchaser, the forward tilt, side tilt and wind speed are taken into consideration, and the dynamic load factor is taken as 2.0. Unless otherwise specified by the purchaser, the crane should reach a minimum effective hook speed of 12m/min (40F1/min) at the first wire rope of the hoisting drum when lifting the maximum rated dynamic load according to the rope threading conditions specified on the lifting weight characteristics plate. The effects of forward tilt, side tilt and wind speed are shown in 3.1.2.2.2.2.2.2.
The purchaser should provide detailed operating conditions of the crane: including forward tilt, side tilt, wind speed and load board for each rated condition. Vertical speed of crane boom end. Dynamic load coefficient (calculated by the following formula: Iki
Cf=1+(Vn+Vt)
Formula, ——Dynamic load coefficient (floating coefficient). C, not less than 1.33: V!-Absolute vertical speed of hook. m/s (ft/s): Relative vertical speed at the lifting point of the cargo board relative to the top of the crane, m/(ft/): See Appendix C (Explanation) K-Vertical angle of hook, N/tn (lb/t); g-Gravity speed, 9.8m/g (32.2ft/s); L-Load, N (1b), 1. is an unknown number, so the step-by-step inverse method is used to calculate Cr. The best value of L is the second design load. The influence of frequency and wind speed before
is shown in 3.1.2.2. 2. 3 Lifting Capacity Table
Each crane shall be equipped with a durable and durable lifting capacity plate with clear and conspicuous words and graphics. The plate shall be securely fixed in a place where it is easily visible to the operator and shall provide the following information: a) For the specified lifting length and jib length, the rated lifting capacity approved by the manufacturer shall be corresponding to the horizontal angle of the boom.
h) The calculation of the rated value shall be clearly stated and shall comply with all applicable provisions of this specification (except that the weight of the hook block, sling, etc., shall be part of the lifting capacity, except the lifting wire rope). c) A rope threading diagram or sketch (shown on the plate or with reference to the detailed crane operator's sketch) shall recommend the number of ropes for each lifting and the size and type of each load wire rope used on the overweight machine. d) It shall be marked with precautions or warnings of limitations on equipment and operating procedures. Chapter 3 Structural Capacity Determined by Stress Analysis 3.1 Analysis
The design of all critical structural components (except as noted in 3.1.3) when subjected to daylight and the design and horizontal loads in 3.1.2 shall be based on the allowable stresses specified in the American Institute of Steel Construction (AISC) Specification for Design, Fabrication, and Erection of Structural Steel Buildings, Eighth Revised Edition, November 1, 19781
The design base and center column should be based on the self-load plus 1:1.5 times the Category 1 design load condition. For structural steel not listed in the American Institute of Steel Construction (AIS) specifications, consistency with AISC applicable stresses shall be confirmed and documented through discussion with the AISC technical staff. The shear stresses at the bottom of the connection joints (welded, pinned or bolted) shall be determined by the AISC allowable values. The strength of the connection shall be determined based on the loads or AIS allowable values and shall never be less than 53% of the main member tensile strength. The allowable shear stress and thickness-to-width ratio shall be in accordance with the appropriate AISC specifications.
3.1.1 Add or Load
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For the purpose of analysis, assume that the crane is horizontal (ideal climbing point rotation) and the load is estimated to be straight and level. The net state is corrected to the crane operator. For cranes installed on floating structures, the effects of sway, heave and transverse loads on the crane are considered. The variable is the tilt angle of the crane. The ratio of the lateral horizontal load to the load is the same as the tilt angle of the crane. 3.1.2 Design load
When making a rated value for a known crane structure! The main reason for determining the "design load" is that, in the actual size of the structure, the design can be solved based on the required rated load. For static conditions, the design load from the top of the crane is 1.33 of the required rated lifting capacity, and additional lateral or horizontal loads, lateral horizontal loads, etc. are added. The design load of the crane is relatively heavy on the ground. For dynamic conditions, the maximum design load at the end of the boom is the dynamic load factor (, or (2.2) Multiply by the required dynamic rated load. The basic design or derivation should also include the corresponding horizontal load. For cranes, the basic design load is mostly determined by the required dynamic rated load (horizontal load) and the size of other structural components is mostly determined by the static rated load. The appropriate design loads for static ratings (called Class 1) and appropriate design loads for dynamic ratings (called Class 2) are as follows: 3.1.2.1 Class 1 Design Loads
This type of design load is the downward load from the crane head. At the same time, there are 2 other types of design loads as lateral horizontal loads. The combined load strength of the upper and lower pulley blocks does not exceed the AISC allowable load. It is important to note that although the maximum loads described are used during operation, they are relatively independent, that is, the downward design load (Class 1 design load does not include a load of 100%. Www.bzxZ.net
3.1.2.2 Class 1 Design Loads
This type of design load is the downward load from the crane head. At the same time, there are 2 other types of design loads as lateral horizontal loads. The combined load strength of the upper and lower pulley blocks does not exceed the AISC allowable load.
3.1.2.2 Class 1 This type of design load is a load that is suspended from the boom end. It also has lateral horizontal loads (described below) and positive water loads (described below). Both are applied to the boom head sheave pin. In addition, there are white loads and wind loads (described below). The total sag should not exceed the AISC allowable unit stress. The water loads and wind loads of the design loads are as follows: &: The lateral water load should be equal to % of the design load, where X=: 100% (lateral load) || t The main horizontal load is the vertical design load, where the tilt angle is determined by the main design angle. The horizontal load is located in the plane of the boom and points away from the crane. The wind load is calculated by the formula that the wind pressure varies with wind speed. As shown in the text, it is not suitable to calculate the wind load coefficient for the specific part of the crane. The wind load should be checked to see if the crane structure can bear the load. The components are, frame, training mechanism (drive force and gear load), rotation option, anchor bolts (or fasteners 1) and foundation. The wind load of the product arm is as follows:
(1) The wind load acting on each surface of the lifting object should be added to the lateral horizontal load and the working load of the arm section in the form of a percentage of the step design load. Each water load (lateral and positive) should be determined according to the minimum wind volume exposed (meters) and it is assumed that it is a cubic meter. The volume of the body is determined based on the assumption that the average strength is 1.4 kN/m (2 ulb/ft\), and the total weight is equal to the vertical design load: This table area (\ or \) can be determined as: "Vertical calculation load. "
i Vertical calculation load, k,
can be replaced by the actual wind load area in the formula 1 US time-level structure society.looNar:hMichgan4venwe.Chicago.oci:Q/HS 7305-93
(2) The wind load on the upper and lower sides of the boom can be converted into an equivalent lateral water load (at the original part of the boom). It will produce a similar horizontal moment on the bottom pivot of the boom, which is called the design engineer's feeling. (3) The wind load on the boom at the peak of the boom should be converted into an equivalent distributed line load: it acts directly on the boom and increases the bending. The wind load component coaxial with the center line of the boom can be ignored in the analysis of the boom. 3.1.3 Exceptions to the AIS specification
Slewing bearings and their bolts and anchor bolts are generally not analyzed according to the AIS specification. The detailed design requirements for slewing bearings and bolts are introduced in Chapter 1.
3.1.4 Fatigue
In the absence of data on the expected frequency and size of the crane during its expected life, each critical structural member shall be designed to withstand at least 25,000 cycles of the basic design loads and associated horizontal loads (determined in accordance with Section 3.1.2) based on an allowable fatigue stress, as specified in Appendix B of the AIS: Specification.
In addition, the designer shall give due consideration to the hot spot stresses in the base metal adjacent to the weld edge, especially those welds and sections that constitute the primary load path rather than the cross section, i.e., the "weak link in the stress flow". This hot spot stress may be defined as the stress measured by the strain gauges adjacent to the weld edge after reaching a stable stress cycle in a prototype test (run test). Finite element analysis appropriate to this definition may be used to calculate this stress, or an appropriate empirical formula may be used based on the results of this analysis or test. The fatigue curves in Section 2.5.3d of API RP2A\ shall be used to obtain the allowable stress that meets this definition. If the manufacturer provides the frequency and size of the loads, the designer may apply the fatigue curves in Appendix B of the AISC Specification or Chapter 10 of AWS D1.180:
h. Dimension components to meet fatigue requirements during the design phase. Or h. Perform fatigue analysis based on cycle data provided by the purchaser to determine the expected fatigue life of the existing structure. 3.2 Certification
The purchaser shall keep confidential the design calculation results, corresponding drawings, and other information necessary to ensure compliance with this specification. The manufacturer shall certify in writing that the cranes used in this specification meet the material and dimensional specifications used in the calculations. Chapter 4 Design Qualification and Testing
4.1 Design Qualification
The manufacturer shall ensure that the prototype design or any significant structural changes to the design have been tested in accordance with one of the following: a: Resistive Strain Gage Test This test is conducted in accordance with SAE Recommended Practice J987\ with the crane subjected to 1.33 times the static rated load and the corresponding increase in side load. The crane manufacturer shall further ensure that all strength limits in J987 are met under the above specified conditions.
b. Suspension load hoisting test This test shall include only the shortest and longest booms, and for each boom length, the minimum, medium and maximum amplitude hoists with a side load of 2.0 times the static rated hoisting capacity and a side load equal to 1% of the static rated hoisting capacity. After all hoisting operations are completed, the crane, including the slewing ring components, are completely disassembled and the appropriate inspection method is selected from the following (depending on the component) to fully meet the "designated" purpose: (1) Dye penetrant: (2) Magnetic particle: (3) Radiography; (4) Supersonic wave: The standard for passing this test should be that the critical component does not show plastic deformation, bending, indentation or defect. Special attention should be paid to bolted and welded connections. An additional requirement of this test is that the stress calculated based on the test load specified above shall not exceed the AISC recommended stress, 1 For example: See AP1 RP 2A, January 1382 2.3.2 C: AP12A "Recommended Practice for Planning, Design and Construction of Designed Offshore Platforms". 6
4.2 Certificate
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The purchaser shall provide documentation of the results of the monthly force tests selected by the manufacturer in contact. The manufacturer shall certify in writing that the hoisting structure provided has been qualified in accordance with this specification.
Chapter 5 Wire Ropes, Sheaves and Drums
5.1 General
Wire ropes, sheaves, drums and stringing accessories for cranes equipped in accordance with this specification shall be selected in accordance with the following factors. 5.2 Wire Rope Construction
The wire rope shall be of the construction specified by the crane manufacturer. APISJec:9A\API Wire Rope Specification\1976, Revised 22nd Edition shall be the minimum requirement for wire ropes for offshore semi-trailers. Anti-rotation wire ropes made of fiber-cored steel shall not be used for luffing wire ropes. 5.3 Wire Rope Design Factor
The design factor for wire ropes shall be the total nominal strength of the total number of ropes in the wire rope system divided by the force acting to withstand the following loads. a. ) For hoist wire, it is the pure lifting load; h) For other wires, it is the white weight plus the lifting load. 5.3.1 Minimum design factor
The following criteria assume that all wire rope end joints (in the system) have the same strength as the wire rope. a) The design factor for the running rope wound on the drum or passing through the pulley shall not be less than 2.5 times ((or,) or 5.C, whichever is greater. b) The design factor for the boom suspension rope or static wire rope shall not be less than 2.0 times C (or C) or 4.0, whichever is greater. :) For hoisting wire ropes, including anti-rotation wire ropes, the design factor shall not be less than 2.5 times C (or C) or 5.0, whichever is greater. d) When lifting personnel, the design factor of the wire rope shall not be less than 10.0. 5.4 Pulley size
The pitch circle (PD) of the pulley in the variable, hoisting and hook pulley block shall not be less than 18 times the nominal diameter (R) of the wire rope used. 5.5 Pulley design
a) According to the crane manufacturer's drawings, the pulley should be flat and free of defects that could cause damage to the wire rope. b) According to the crane manufacturer's drawings, the radius of the groove bottom cross section should be a close fit to the size of the wire rope used. c) According to the crane manufacturer's drawings, the two sides of the groove should be sufficiently open to facilitate the entry of the wire rope into the groove. d) According to the crane manufacturer's drawings, the flange angles should be rounded and the wheel flange should rotate relative to the axis. (F) All pulley bearings should be equipped with lubricating devices except for permanently lubricated shafts. 5. 6 Pulley anti-expansion cover
All pulleys, including movable pulleys, should be equipped with anti-expansion covers or other suitable devices to prevent the wire rope from escaping from the wheel groove. 5.7 Wire rope accessories and end treatment
a) The end of the eyelet should have at least two fastening knots. Other specific requirements can be determined by the crane manufacturer. b) For U-clip installation, the U-clip should be installed at the short end of the dead end, and the bracket should be installed at the live rope end or the long rope end. The distance between the clips, the torque and the number of clips should be in accordance with the regulations of the crane manufacturer. c) When the recovery sleeve is used in conjunction with the rope clip, the rope clip can only be clamped at the unloaded end of the rope (dead rope end). d) The installation procedure of the rope end accessories should be carried out in accordance with the regulations of the crane manufacturer. 5.8 Lifting hook, gravity ball device and lifting pulley For the length of the boom and the number of ropes in use, the lifting hook, gravity ball device and lifting pulley should have enough weight to prevent the wire rope from slacking when the drum is unwound at the maximum speed. The additional weight of cast iron material is not allowed. The hook weight ball assembly year Kia pulley should 1 See "Terms"
2 SAF Promotion Practice 1987\Crew Structure 15096
3 See Example Standard Section 14.4.
Test Methods\, United Kingdom Society of Automotive Engineers, 4ouCumnnwcalth1)rive, Werrendaie.P47
Q/HS 70, -99
The requirements for long-term marking their weight and rated capacity should be equipped with a balance safety lock to prevent the other rope from being unhooked in the event of a loosening
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Figure: Sliding light ruler on the cabinet
6.1 Lifting
5.2 The method of clamping the dead butterfly during the credit model performance card Chapter 6 Luffing, heavy lifting and boom telescopic mechanism Luffing and heavy lifting should be determined by the manufacturer of the lifting machine to be suitable for a lifting person, and be marked on its label. The entire hoist should meet the performance and operability requirements set forth below.
6.1.1 Brake retention
6.1.1.1 Power release and clutch
Both the brake and the clutch should be equipped with an adjustment mechanism to compensate for wear and maintain sufficient spring force when necessary.6.1.1.2 Power Brake
When the power-acting brake mechanism and the control mechanism are broken and there is no continuous mechanical linkage to control the load, a dynamic brake should be installed to prevent the load from falling in the event of brake power failure. 6.1.1.3 Static brake
The static brake can stop the rated load for a long time without operation or supervision. The static brake should be automatically braked when the control lever is pulled. The static brake of the stopped hoisting reel should have sufficient braking force to retain 1.5 times the rated lifting torque. 6.1.1.4 Dynamic brake
The lowering of the boom or load can only be selected through the power transmission system. The lowering of the boom or load is not allowed Main fall type descent. a: When the winch is designed to control the descent of the load or the boom only through differential friction, it should be able to continuously lift and lower the rated load for 15 hours at the maximum design speed within the height range of 15m51). The pause time between the lifting and lowering operations should not exceed seconds. The coolant flow rate should be maintained within the limits specified by the winch manufacturer. At the end of the test, the brake should have sufficient capacity to smoothly brake 10% of the rated load running at the maximum design speed in the descending mode. b. When the winch is designed to control the descent of the load or the boom by adjusting the input speed, it should be able to smoothly brake 110% of the rated load descending at the maximum speed. The temperature rise of any drive system component shall not exceed the temperature limit specified by the manufacturer. Except as noted below, the hoist should be equipped with a dynamic friction brake device that can automatically operate to brake the winch smoothly in the event of a force-control failure or power failure. When the lifting device is designed to control the descent of the load or boom by allowing the power fluid to flow from a cylinder or a motor connected to the winch, a dynamic friction brake system may not be required in the following cases: (1) The control device is connected to the hook lowering fluid outlet without a hose; (2) The control device requires a positive force from the power source, which can be released dynamically in the event of a force-control failure or power failure.It should be able to raise and lower the rated load continuously for 12 hours at the maximum design speed within the height range of 15m51). The rest time between raising and lowering operations should not exceed seconds. The coolant flow rate should be maintained within the limits specified by the winch manufacturer. At the end of the test, the brake should have sufficient capacity to smoothly brake 10% of the rated load in the lowering mode when running at the maximum design speed. b. When the winch is designed to control the descent of the operator or other arm by adjusting the input speed, it should be able to smoothly brake 110% of the rated load descending at the maximum speed. The temperature rise of any drive system component shall not exceed the temperature limit specified by the manufacturer. Except as described below, the winch should be equipped with dynamic friction Friction brake device: In case of force-control failure or power failure, the device can automatically operate to brake the winch smoothly. When the lifting device is designed to control the descent of the weight or the boom by squeezing the hydraulic fluid from the cylinder or the motor connected to the winch, the dynamic friction brake system is not required in the following cases: (1) The control device is connected to the hook lowering fluid outlet without a hose; (2) The control device needs a positive force from the power source, which can be released dynamically in the case of force control failure or power failure.It should be able to raise and lower the rated load continuously for 12 hours at the maximum design speed within the height range of 15m51). The rest time between raising and lowering operations should not exceed seconds. The coolant flow rate should be maintained within the limits specified by the winch manufacturer. At the end of the test, the brake should have sufficient capacity to smoothly brake 10% of the rated load in the lowering mode when running at the maximum design speed. b. When the winch is designed to control the descent of the operator or other arm by adjusting the input speed, it should be able to smoothly brake 110% of the rated load descending at the maximum speed. The temperature rise of any drive system component shall not exceed the temperature limit specified by the manufacturer. Except as described below, the winch should be equipped with dynamic friction Friction brake device: In case of force-control failure or power failure, the device can automatically operate to brake the winch smoothly. When the lifting device is designed to control the descent of the weight or the boom by squeezing the hydraulic fluid from the cylinder or the motor connected to the winch, the dynamic friction brake system is not required in the following cases: (1) The control device is connected to the hook lowering fluid outlet without a hose; (2) The control device needs a positive force from the power source, which can be released dynamically in the case of force control failure or power failure.
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