Some standard content:
ICS 21. 200
National Standard of the People's Republic of China
GB/Z 19414—2003/ISO/TR 13593:1999 Enclosed gear drives for industrial applications(ISO/TR13593:1999,IDT）
2003-11-25 Issued
General Administration of Quality Supervision, Inspection and Quarantine of the People's Republic of China
2004-06-01 Implementation
This guidance technical document is formulated for the first time. Foreword
GB/Z 19414--2003/ISO/TR 13593: 1999 This guidance technical document is equivalent to the English version of ISO/TR3593:1999 "Enclosed gear drives for industrial applications"). For ease of use, the following editorial changes have been made to this technical guidance document. Some formatting formats have been modified according to Chinese habits; decimal point "\" is used instead of comma "," as a decimal; the foreword of ISO/TR13593:1999 has been deleted. Appendices A to F of this guidance technical document are informative appendices. This guidance technical document is proposed by China Machinery Industry Federation. This guidance technical document is under the jurisdiction of the National Technical Committee for the Promotion of Gear Standardization. This guidance technical document is drafted by Zhengzhou Machinery Research Institute. The main drafters of this guidance technical document are: Wang Qi, Zhang Yuanguo, Yang Xingyuan, Chen Aimin, Wang Changlu. 1 Scope
GB/Z19414—2003/IS0/TR13593:1999 Industrial closed gear transmission device
This guidance technical document is applicable to industrial closed reduction devices and speed increase devices, including spur gears, helical gears, herringbone gears or double helical gears and their combinations of single-stage or multi-stage transmission devices. This guidance technical document provides a method for comparing and selecting gear transmission device designs. It does not mean to guarantee the performance of the assembled gear transmission system. The purpose is to provide experienced gear designers with the ability to select reasonable coefficient values based on the performance of similar designs and the influence of items such as lubrication, deformation, manufacturing tolerances, metallurgy, residual stresses and system dynamics. It is not for use by general engineering personnel.
Maintaining an acceptable temperature in the oil tank of the closed gear transmission is critical to the life of the gear transmission. Therefore, this guiding technical document considers not only the mechanical power of the closed gear transmission, but also the thermal power. The calculation methods and influencing factors in this guiding technical document are limited to closed transmissions of single-stage and multi-stage designs, with pitch line speeds not exceeding 35m/s and pinion speeds not exceeding 4500r/min. The gear tooth calculations included in this guiding technical document are limited to root bending strength and tooth surface contact strength.
This guiding technical document does not include planetary transmission design and application. Detailed analysis of efficiency is not included. Within the scope of this guidance technical document.
Appendix A to Appendix F can be used to make a more detailed analysis of certain calculation coefficients. 2 Normative references
The clauses in the following documents constitute the clauses of this guidance technical document through reference in this guidance technical document. For any dated referenced document, all subsequent amendments (excluding errata) or revisions are not applicable to this guidance technical document. However, the parties who reach an agreement based on this guidance technical document are encouraged to study whether the latest versions of these documents can be used. For any undated referenced document, its latest version applies to the guidance technical document. GB/T3481-1997 Gear tooth wear and damage terminology (idtISO108251995) GB/T8539—2000 General provisions for gear material and heat treatment quality inspection (eqvISO6336-5:1996) GB/T19406-2003 Load capacity of involute spur and helical cylindrical gears Calculation methods Industrial gear applications (ISO9085:2002, IDT
ISO76:1987 Static load ratings of rolling bearings ISO281:1990 Dynamic load ratings and rated life of rolling bearings ISO3448:1992 ISO viscosity classification of industrial liquid lubricants ISO6743-6:1990 Lubricants, industrial lubricants and related products (L-grade) Classification Part 6: Group C (gears) ISO8579-1 Acceptance rules for gearboxes Part 1: Determination of sound power levels of gear unit noise ISO8579-2 Acceptance rules for gearboxes Part 2: Determination of mechanical vibrations of gear units during acceptance tests ISO12925-1:1996 Lubricants, industrial lubricants and related products (L-grade) Group C (gears) Part 1: Lubricant specifications for closed gear systems
3 Codes, terms and definitions
3.1 General
The codes, terms and definitions contained in this document may differ from those used in other standards. Users of this guidance technical document should check the codes and terms used in this document. GB/Z19414—2003/IS0/TR13593:19993.2 Code
According to the purpose of this guidance technical document, the codes used are given in Table 1. Table 1 Codes used in the formulas
Surface area of the gear transmission
Load applied by the fit
Stress cross section of the fastener
Life adjustment factor for reliability
Height factorwwW.bzxz.Net
Operating time factor
Ambient temperature factor
Non-standard tank temperature factor
Ambient air velocity factor
Width of key
Nominal diameter of threaded fastener
Outer diameter of hub
Inner diameter of hub
Maximum nominal fastener diameter
Outer diameter of shaft
Inner diameter of shaft
Elastic modulus of hub material
Elastic modulus of shaft material
Applied tensile load
Tensile preload of fastener
Load spike frequency factor
Key Height
Actual or minimum possible interference fit
Number of keys
Service factor
Stiffness factor of connection
Selection factor
Torque factor
Heat transfer coefficient
Length of hub
Modified calculated life at 100-n=R% reliabilityCalculated life at basic (90%) reliabilityUnit
kW/( m2-K)
First application
Formula (40)
Formula (21)
Formula (27)
Formula (3)
Formula (41)
Formula (41)
Formula (41)
Formula (41)
Formula (41)
Formula (17)
Formula (28)
Formula (24)||t t||Formula (24)
Formula (3)
Formula (16)
武(6)
Formula (6)
Formula (23)
Formula (23)||t t||Formula (31)
Formula (27)
Formula (20)
Formula (16)
Formula (23)
Formula (16)
Formula (30)| |tt||Formula (1)
Formula (29)
Formula (40)
Formula (22)
Formula (3)
Formula (3)
Clamping length of fastener
Supporting length of key
Bending moment
Clamping torque of fastener
Input power of gear transmission
Bearing power loss
Shaft-hub Pressure on common joint surfaces
Power loss related to load
Power loss in gear meshing
Minimum calculated component power
Power loss independent of load
Nominal power of driven or driving machinePower loss of oil pump
Heat dissipation of gear transmission
Power loss of oil seal
Thermal power
Corrected applied thermal power
Total power loss
Power loss due to windage and oil stirring of bearings
Power loss due to windage and oil stirring of gears
Thread pitch of fasteners
Reliability level
Tensile strength of key material
Minimum safety factor for bending strength
Minimum safety factor for contact strength
Torque of shaft
Table 1 (continued)
GB/Z 19414—2003/ISO/TR 13593:1999
Permissible torque based on the smaller value between Tc and Ts
Permissible torque based on permissible compressive stress
Maximum torque
Minimum calculated component torque
Nominal torque of driven or driven machinery
Friction torque of shaft-hub interface
Permissible torque based on permissible stress of key
Keyway depth of shaft
Life factor of bending strength
First application
Formula (16)
Formula (7)
Formula (29)
Formula (34)
Formula (38)
Formula (22) | | tt | ||Formula (41)
Formula (32)
Formula (39)
Formula (39)
Formula (28)
Formula (4)
Formula (18)
Formula (6)
Formula (16)
Formula ( 20)
Formula (2)
Formula (2)
Formula (21)
Formula (17)
Formula (16)
GB/Z19414—2003/ISO/TR13593:1999
Life coefficient of contact strength
Torsion notch coefficient
Bending notch coefficient
Load distribution coefficient
Total efficiency of transmission device
Friction coefficient
Poisson's ratio of hub material
Poisson's ratio of shaft material
Tensile strength of material
Calculated bending stress of shaft
Allowable bending stress
Calculated tensile stress of fastener
Allowable tensile stress of fastener
Recommended pre-tensile stress
Yield strength of fastener at 0.2% residual
Calculated torsional stress of shaft
Allowable torsional stress
Allowable compressive stress
Allowable shear stress
Terms and definitions
Table 1 (continued)
The following terms and definitions apply according to the purpose of this guidance technical document. Power of gearbox
First application
Formula (10)
Formula (12)
Formula (40)
Formula (16)
Formula (36)
Formula (22)
Formula (23)
Formula (23）
Formula (10)
Formula (7)
Formula (12)
Formula (31)| |tt||Equation (30)
Equation (26)
Equation (26)
Equation (6)
Equation (10)
Equation (16)
Equation (17)
The rated value of the total mechanical power of all stationary and rotating parts in a closed transmission is determined by the smallest calculated part power Pm (the weakest part can be determined by the gear teeth, shaft, bolt connection, housing, etc.). 3.3.2 Thermal power
The maximum power that a closed gear transmission can continuously transmit without exceeding the specified tank temperature. Note: This thermal power is equal to or exceeds the transmission power under actual operation. When determining the thermal conditions, the selection factor is not used. Application and design basis
4.1 Application limitations
The gearbox power specified in this guidance technical document is the mechanical load-bearing capacity of the gear transmission parts (selection factor, Ksr-1.0). In some applications, in order to adapt to the adverse effects of environmental conditions, the thermal load capacity of the transmission, the applied load or any combination of these factors, a gear transmission with greater mechanical power must be selected. 4.2 Calculation coefficients
The allowable stress values in this guidance technical document are the maximum allowable values. Based on experience, a certain degree of flexibility is allowed in the selection of specific coefficients in this guidance technical document. For other parameter coefficients in this guidance technical document, a few conservative values should not be adopted. 4
4.3 Metallurgical aspects
GB/Z19414-—2003/ISO/TR13593:1999 Some coefficients of gears affected by material conditions and quality are specified in GB/T8539. 4.4 System analysis
The system of connected rotating parts should be coordinated and not affected by critical speeds, torsional vibrations or other types of vibrations caused by any reason within the specified operating speed range. Unless agreed in the purchase agreement, the designer or manufacturer of the enclosed gear transmission is not responsible for this analysis.
4.5Gearbox power
4.5.1 Application of gearbox power
Gearbox power is the rated value of the total mechanical power of all stationary and rotating parts in the enclosed transmission. The minimum calculated part power Pmc of the enclosed transmission (the weakest part can be determined by the gear teeth, shafts, bolts, housing, etc.) determines the power of the gearbox. Gearbox power is determined under the conditions of 10,000 cycles at 200% load, plus 10,000 hours of operation at 100% load. Gearbox power should also include the effect of the allowable overhung load at a specified distance from the end of the gearbox subject to the overhung load. Note: It is the user's responsibility to specify the peak load conditions. The transmission can be selected so that the peak torque does not exceed the provisions of 4.6. When determining the power of the gearbox, the unit selection factor K=1.D is used. Please refer to Chapter 9 for the discussion of the selection factor K. 4.5.2 Gearbox power requirements
Gearbox power means that all items in the gearbox are designed to meet or exceed the gearbox power. The power of the gear and pinion shall be consistent with the rated values of bending strength and contact strength specified in 5.3. 4.5.3 Application of gearbox power
The power of the gearbox required for a closed transmission is a function of the variables used and evaluated, which affect the total power. These factors include environmental conditions, severity of operation and life. Further explanation can be found in Chapter 9. The application of closed transmissions requires that its gearbox power meets the needs of the actual operating conditions. This can be achieved by reasonably selecting the selection factor K based on field data or experience. The values given in Annex A can be used as a guide. The gearbox power that meets the requirements of the application under consideration can be obtained by a relatively satisfactory method:
Pm ≥P,Kf
Where P. is the nominal power of the driven machine or driving machine. See Chapter 9 and Appendix A. Similarly, when calculating in terms of torque:
Tme T.Ks
Products
+--+++(2)
If the nominal power or nominal torque of the driven machine is used to calculate the power of the gearbox, P must be greater than Pn. The maximum torque occurring in the entire system should be checked. During acceleration or other times, the maximum torque should not exceed 200% of the nominal torque of the driven machine, see 4.6.
4.6 Transient overload
When the closed transmission is subjected to transient overload, motor direct-on-line starting, braking, stall conditions and low-cycle fatigue, the calculation conditions should ensure that the strength limit of any part is not exceeded. As for the bending strength of the gear under transient overload, the maximum permissible stress is determined by the permissible fatigue limit of the material. The deformation of the shaft, bearings and housing has an important influence on the gear tooth meshing during transient overload. When calculating the closed transmission, it is necessary to ensure that the response to transient overload does not lead to local high stress concentration or permanent deformation due to excessive tooth mismatch. In addition, the influence of external loads such as cantilever, lateral bending and axial destructive load must be calculated. The gear transmission calculated in this guiding technical document is suitable for situations where the number of stress cycles does not exceed 10,000 times, the peak load does not exceed 200% of Pm, and the minimum tooth load factor is determined by analysis under the conditions of 100% load to 200% load. 4.7 Efficiency calculation
When calculating the efficiency of the closed transmission, it should be determined based on the transmitted power and the given operating conditions. The calculation method should include the influence of each part in the closed transmission and the shaft transmission accessories agreed upon by the manufacturer and the user. Unless otherwise agreed between the user and the manufacturer, prime movers, couplings, external driven loads, motor drive accessories, etc. are not included in the efficiency calculation of closed transmissions. Efficiency calculations are given in Chapter 7.
4,8 Alternating loads
The effect of alternating torque on closed transmissions can be considered by selecting appropriate selection factors for the application (e.g. stroke transmission). In specific calculations and analyses, the effect of alternating loads can be considered as equivalent loads. 5 Parts
5.1 Basis of calculation
When designing the various parts of a gear transmission, all possible loads applied during operation should be properly considered. These loads include not only the torque load acting on the parts through the gear transmission, but also external loads, i.e. cantilever loads, external thrust loads, dynamic loads (e.g. from cantilever pinions), etc. These components should also be designed to withstand any assembly forces that may exceed the operating loads. When designing, it should be considered that the operating loads occur in the worst possible direction and the worst possible load combination, including 200% instantaneous peak starting loads. The calculation of parts should be within the limits specified in this guidance document. When user requirements or technical specifications specify different design criteria, such as higher bearing life, this should be agreed upon. Another method of calculating parts based on test data or field experience is allowed. The gear manufacturer should indicate and document all changes made.
The power of the gearbox can also include the value of the allowable overhang load, which is usually referred to as the distance from the surface of the box or housing part to a shaft diameter. The stresses in the relevant components caused by these overhang loads must also be within the requirements of this guidance document. According to the purpose of this guidance document, when determining the load capacity of the parts, their calculations are closely related to the gearbox power specified in Section 4.5.1.
Note: The separate calculation requirements are linked to the gearbox power and application conditions. 5.2 Housing
The structural design of the gearbox should enclose the integrated assembly of gears, shafts and bearings, and ensure the necessary rigidity so that the gears can mesh normally. The housing should maintain the consistency of the gear tooth direction under the conditions of the specified internal and external loads. For housings with a low-speed center distance greater than 460mm, at least two reference surfaces should be machined parallel to the mounting surface to achieve the self-leveling of the gear transmission.
5.3 Gear
5.3.1 Calculation criteria
The basic calculation formula for closed gear transmissions should be in accordance with GB/T19406-2003. The calculation method of the calculation coefficient for each gear may be modified, and the gear designer must specify all changes when using GB/T19406-2003. The contact strength is a function of the Hertzian contact (compressive) stress between two curved surfaces or tooth surfaces. It is proportional to the square root of the load acting on the gear teeth. Bending strength is determined based on the bending (tensile) stress in the cantilever plate. It is proportional to the same gear tooth load. The different nature of the stresses induced on the gear tooth surface and on the tooth root is reflected in the corresponding difference in contact stress limit and bending stress limit for the same material and load intensity.
The term "gear failure" is a subjective concept and the source of many disagreements. One observer's "failure" may be another observer's "running-in". For a more complete description, see GB/T3481.5.3.1.1 Alternating loading
For gears subjected to alternating loading for each cycle, see GB/T8539.5.3.1.2 Local deformation
This guidance document does not include transmissions with stress values greater than the allowable stress value for cycles of 10° or less. Because in this range, both the bending stress and the tooth surface compressive stress will exceed the elastic limit of the gear tooth. Depending on the material and the applied load, when the stress of a single stress cycle exceeds the limit stress for cycles less than 103, plastic deformation of the gear tooth will occur. 5.4 Bearings
5.4.1 Bearing selection
GB/Z19414--2003/IS0/TR13593:1999 The shaft can be installed in bearings of any size, type and load capacity. The bearings should be able to withstand radial and axial loads caused by the most severe operating conditions.
5.4.2 Liquid oil film bearings
When designing liquid oil film bearings, the pressure on the bearing design surface should not exceed 6N/mm2. The speed of the shaft diameter should not exceed 8m/s under non-pressure oil supply conditions. When the manufacturer has experience or test data, a higher value can be used. 5.4.3 Selection of roller and ball bearings
5.4.3.1 Selection basis
When roller and ball bearings are selected, according to the calculation of the bearing manufacturer, based on the gearbox power and gear transmission selection coefficient equal to 1, there should be a minimum L10 life of 5000h. L1o life is the running time that 90% of the bearings with the same appearance must reach or exceed before the fatigue debris generated in the subsurface reaches a predetermined size. When selecting bearings, the following parameters should be considered: - Lubrication;
- Temperature;
- Load zone;
Axial consistency;
- Bearing material.
5.4.3.2 Other issues
The life calculation method used by bearing manufacturers is based on sub-surface fatigue damage that leads to chipping. The existence of other types of bearing damage should include but not be limited to surface chipping caused by scratches caused by lubricant contamination, cage failure, plastic deformation, spalling caused by extreme instantaneous overload, and severe scratches or bonding caused by instantaneous loss of oil film. 5.4.3.3 Reliability
The bearing life for reliability levels other than 90% is calculated using the following formula: Lna = a, Lioa
where:
the calculated life adjusted at 100-n-R% reliability; -the calculated life at 90% basic reliability, including factors a2 and a3; the reliability life adjustment factor, as described in ISO 281: For reliability R ≥ 90%
For reliability R < 90%,
Formulas (4) and (5) are based on the Weibull distribution and are adapted from the data of leading bearing manufacturers. 5.5 Shafting
5.5.1 Design basis
(3)
(4)
·(5)
The shaft should be designed to withstand both internal loads (caused by gear meshing) and external loads. Both the strength and rigidity of the shaft are important. Sufficient shaft strength will avoid fatigue or plastic deformation, while sufficient rigidity will maintain the axial alignment of the gear and bearing. 5.5.2 Calculation of shaft stress
The nominal stress of the shaft is calculated according to the following formula. Formula (6) and formula (7) can be applied to the design of thin-walled shafts, where the ratio dbi/dh < 0.9 is not allowed.
16000Td she
Yuan(dthe - dsh)
·（6)
GB/Z 19414--2003/ISO/TR 13593 ; 1999 In the formula:
32000Md she
T(dihe -- dsh:)
-calculated torsional stress of the shaft, in Newton per square millimeter (N/mm); T—-torque of the shaft, in Newton meter (N·m)); d she
outer diameter of a shaft, in millimeter (mm); inner diameter of a shaft, in millimeter (mm); calculated bending stress of a shaft, in Newton per square millimeter (N/mm2); M bending torque, in Newton meter (Nm).
For solid shafts, formulas (6) and (7) are simplified to: 16000T
5.5.3 Allowable stress
32000M
(7)
(8)
(9)
The calculated stresses caused by bending and torsion should not exceed the allowable stress values determined from formulas (10) to (15). These formulas are simplified forms of DIN743 and are subject to the following restrictions. (1) Formulas (10) to (15) are applicable to shaft diameters within the following range: 25 mm ≤ dshe ≤ 150 mm
For shaft diameters outside this range, the following conditions shall apply: If dshe ≤ 25, take dshe = 25 mm;
If 150
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