validation of bearing girders in marine Diesel engines

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机械液压设备产品说明书

Sleeve Bearing Lubrication Mike JohnsonPlain BearingsThere are two broad types of bearings used in machinery today: plain and rolling element bearings. This article targets the special lubrication requirements of plain bearings, also known as sleeve bearings and journal bearings.The plain bearing consists of a shaft, also called a journal, and a supporting component, which may be a shell around the shaft called a sleeve, a half shell that the shaft fits into, two half shells (top and bottom parts) or a multipart shell.See Figure1Plain bearings are used for high radial loads (perpendicular to the axis of the shaft) and low to high speeds. Typical applications include turbines, large milling systems, engine cranks, compressors, gearboxes, shaft bearing supports, etc.Every journal bearing has some common design characteristics as shown inFigure 2.The components that are separated by the oil film in a plain bearing are the bearing liner and the shaft. The shaft is composed of high-quality, wear-resistant, structurally strong steel. The bearing liner may be made of a single layer or multiple layers, depending on the design features of the equipmentLubrication RegimeUnder normal operating conditions, the lubrication regime will be a hydrodynamic full-fluid film. A hydrodynamic film occurs when there is sufficient lubricant between the lubricated surfaces at the point of loading to form a fluid wedge that separates the sliding surfaces. In this state, the lubricated components do not touch each another, reducing friction and wear.This condition is represented by the equation ZN/P, where Z = viscosity, N = speed (rpm) and P = load. This equation is represented by Figure 4.The curve on this graph is called the Stribeck Curve. It is the classical representation of the relationship between speed, load and friction.Mixed film conditions occur when a loss of the film resulting in momentary contact between the two surfaces is apparent. This can occur in response to momentary variations in loading, called shock-loading, that can collapse the film, resulting in physical contact of opposing asperities.Another condition that can occur is boundary film lubrication. This is when the film that separates the surfaces undergoes significant loss resulting in a high load of metal-to-metal contact. This happens any time the relative motion of component surfaces are slow and no oil film is formed.Lubrication Needs of a Plain BearingOperating under proper speed, surface area, viscosity and oil volume, a plain bearing can support very heavy loads. The balance between these conditions is important. If the load or the speed changes, the lubricant viscosity must be adjusted to compensate for the change. There is no simple formula that is used to calculate the viscosity requirements for oil lubricated plain bearings, but the ZN/P formula demonstrates the results of complex calculations used to arrive at the proper clearance.Criteria to consider once you have identified the proper viscosity grade include oxidation stability, corrosion inhibition, wear protection, water and air separation properties, etc. Because plain bearings can be used in a variety of applications, there is no single set of criteria that should be used. Selection depends on the equipment design and operating conditions.Plain bearings are normally oil lubricated, but may be lubricated with grease for slow-speed equipment, particularly if they are subject to frequent starts and stops or the bearings may be physically difficult to reach.The type and amount of grease depends on continuous replenishment of the body of grease that is held within the dynamic clearances (empty spaces while the bearing is turning) in order to maintain effective lubricant condition and hydrodynamic lift. Equipment with poor sealing characteristics may require a heavier body of lubricant and more frequent replenishment cycles.Under manual (intermittent) relubrication, the volume and the frequency are influenced by operating conditions, grease quality and available time for the task. Grease selection begins with consideration of the oil to be used. Heavy oils are used to formulate greases used to manually lubricate plain bearings in high-duty service.After the proper viscosity oil has been selected, then the soap thickener, oxidation and rust characteristics, worked consistency properties, pumpability (for automatic systems) and load-bearing (EP/AW) properties are considered. For long intervals and very heavy loading, solid additives such as molybdenum disulfide or graphite may be incorporated. The solid additives would serve to mechanically prevent metal contact in mixed film and boundary lubrication conditions.The grease should be pumped into the bearing in front of the load zone and at the location of the grease grooves used for lubricant distribution (Figures 5 and 6).Figure 6Wear and Failure Modes in Plain BearingsThere are several factors that can wipe or damage a plain bearing surface. Abrasive wear is one of the most common. If the wear is caused by a hard particle rubbing between the lubricated surfaces, it is called three-body wear. Wear caused by an asperity on one surface cutting the other surface is called two-body abrasion.Wear can also result from insufficient volume of lubricant (starvation leading to boundary conditions), overheated lubricant (viscosity at operating temperature cannot support the load causing frictional heat and additional oil thinning), rough surfaces (asperities on the journal cause rubbing), imbalance (improper loading of the support element causing shock loading), journal eccentricity (egg-shaped journal causing rubbing on the high spots), and metal fatigue from improper metallurgy. Journal bearing wear can be effectively monitored by oil and ferrographic analysis.See Figure7The telltale indicators that may point to high wear conditions include high metallic particle counts (two levels above norm), darkened metal surfaces, blued metal surfaces and wear metals formed into spirals or platelets. As oils age and become contaminated with moisture or acidic oxidation compounds, we can see evidence of corrosion and metallic oxidation on stationary surfaces in the reservoir.。

中外项目地基承载力特征值异同点探讨

中外项目地基承载力特征值异同点探讨赵树光，陈智勇，杨秋芳（中交第三航务工程勘察设计院有限公司，上海200032）摘要：本文介绍了地基承载力的基本概念，对影响地基承载力因素的敏感性进行了分析。

总结了沿海地区规范承载力特点，结合本单位工程经验，总结了港工项目各类土层地基承载力的取值。

对中英标准的承载力特征值异同点进行了对比分析，对境外项目中地基承载力的确定有一定指导意义。

关键词：英标；地基承载力；承载力特征值；参数敏感性；对比分析中图分类号：TU471 文献标识码：A 文章编号：2097-3519（2024）02-0019-06DOI: 10.16403/ki.ggjs20240205Discussion on Differences and Similarities in Characteristic Value of Foundation Bearing Capacity Adopted in China and Overseas ProjectsZhao Shuguang, Chen Zhiyong, Yang Qiufang( CCCC Third Harbor Consultants Co., Ltd., Shanghai 200032, China )Abstract: Based on the basic concept of foundation bearing capacity, the sensibilities of the factors that affects foundation bearing capacity are analyzed to summarize the characteristics of bearing capacity applying to coastal area, produces the values taken for the foundation bearing capacity of various soil layers by referring to the experience in engineering practice. A comparative analysis is also conducted for the similarities and differences in the characteristics of bearing capacity adopted in Chinese and English Standards. The research has a certain guiding significance for determining the foundation bearing capacity in overseas projects.Key words: British Standard; foundation bearing capacity; characteristic value of bearing capacity; sensitivity to parameter; comparative analysis引言地基承载力是岩土工程勘察中最为常见的概念，在各类岩土勘察报告中一般都需提供土层地基承载力。

地基承载力特征值英语

地基承载力特征值英语The foundation bearing capacity characteristic value, often referred to as the "ultimate bearing capacity" of the soil, is a critical parameter in civil engineering and construction. It represents the maximum load that a soil layer can safely support without exceeding its failurelimit. This value is determined through geotechnical investigations and soil testing, ensuring the stability and safety of structures built upon it.In the realm of geotechnical engineering, the understanding and accurate assessment of foundation bearing capacity are paramount. Incorrect estimations can lead to structural failures, settlement issues, and even complete collapse. Therefore, it is imperative to employ rigorous testing methods and advanced analysis techniques to determine this characteristic value.The methods used to determine foundation bearing capacity vary depending on the type of soil, its properties, and the specific engineering requirements. Commontechniques include load tests, penetration tests, and laboratory tests on soil samples. These tests providevaluable insights into the soil's compressive strength, shear strength, and deformation behavior, among other parameters.The foundation bearing capacity characteristic value is not a static figure. It can be affected by various factors such as soil moisture content, compaction, and the presence of underground obstacles. Therefore, it is essential to monitor and reassess this value periodically, especially during the construction process, to ensure the integrity of the foundation.In conclusion, the foundation bearing capacity characteristic value is a fundamental parameter in civil engineering, guiding designers, engineers, and constructors in their efforts to build safe and stable structures. By employing rigorous testing methods and advanced analysis techniques, we can accurately assess this value and ensure the long-term safety and durability of our built environment.**地基承载力特征值的技术探索**地基承载力特征值，通常被称为土层的“极限承载力”，是土木工程和建筑领域中的一个关键参数。

Effect of sliding friction on gear noise based on a refined vibro-acoustic

Effect of sliding friction on gear noise based on a reﬁned vibro-acoustic formulationSong He a),Rajendra Singh b)and Goran Pavićc)(Received:3January2008;Revised:5May2008;Accepted:5May2008)An improved source-path-receiver model of a single mesh geared system isdeveloped and validated to quantify the effect of sliding friction between gearteeth on the structure-borne whine noise.The source sub-system of a spur gearpair predicts interfacial bearing forces in the line-of-action and off line-of-actiondirections for two whine excitations(static transmission error and slidingfriction).Next,aﬁnite element model of the gearbox with embedded bearingstiffness matrices is developed to characterize the structural paths and tocalculate the surface velocity distributions.Predictions areﬁrst validated bycomparing with structural modal tests and transfer function measurementsfrom gear mesh to the housing plates.Radiated noise is then estimated by usingtwo approximate methods,namely the Rayleigh integral method and asubstitute source technique.The overall vibro-acoustic model is validated bycomparing radiated sound pressure calculations with measured noise data overa range of operating torques.The proposed formulation provides an efﬁcientanalytical and computational tool to quantify the relative contribution of slidingfriction to the structure-borne noise,which is found to be signiﬁcant when thetransmission error is minimized say via tooth modiﬁcations.©2008Institute ofNoise Control Engineering.Primary subject classiﬁcation:11.1.3;Secondary subject classiﬁcation:751INTRODUCTIONMost gear noise researchers1–3have assumed that the static transmission error(STE)is the main source of whine(steady state noise at gear mesh frequencies and side-bands).Consequently,transmission errors are minimized in a methodical manner via tooth modiﬁca-tions.However,high precision gears are still noisy in many applications.One plausible explanation is that the sliding friction becomes a potential noise source, especially in spur gears at certain torques or tribologi-cal conditions4–7.Accordingly,we consider two concur-rent excitations,namely the unloaded static transmis-sion error and sliding friction,to a geared system,as shown in Fig.1.Objectives of this article are:(1)Develop a reﬁned source-path-receiver model that characterizes the structural paths in two directions; also,propose analytical and efﬁcient computational tools to predict noise radiated from the gearbox panels.(2)Quantify the relative contributions of transmission error versus sliding friction noise to the overall whine noise,and validate predictions of the structural transfer functions and sound pressure with measurements for one example case(NASA gearbox with spur gears). 2LITERATURE REVIEW AND PROBLEM FORMULATIONThe literature on the vibro-acoustic models of the entire geared system2,3,8is rather sparse.For the inter-nal geared system,only a few investigators have incor-porated the torsional and translational motions in both line-of-action(LOA)and off line-of-action(OLOA) directions4–7although many lumped parameter models have been developed over the last four decades1–3.The vibration transmission path through bearings has been well described by the stiffness matrix that was analyti-cally formulated by Lim and Singh9.Rook and Singh10 analyzed the gearbox using the mobility synthesis method and derived a procedure of calculating narrow-band vibratory powerﬂows,which recognizes rollinga)Acoustics and Dynamics Laboratory,The Ohio State Uni-versity,201West19th Avenue,Columbus OH43210USA; email:he.81@b)Acoustics and Dynamics Laboratory,The Ohio State Uni-versity,201West19th Avenue,Columbus OH43210USA;email:singh.3@c)Laboratoire Vibrations Acoustique,Institut National des Sciences Appliquées de Lyon,Bâtiment Saint-Exupéry,25 bis,avenue Jean Capelle,F-69621Villeurbanne Cedex FRANCE;email:goran.pavic@insa-lyon.fr164Noise Control Eng.J.56(3),May-June2008element bearings as a multi-dimensional compliant and dissipative connection.Moreover,the vibration behav-ior of the gearbox housings has been examined by using ﬁnite element analysis (FEA)11,12,experimental modal analysis 13and statistical energy analysis (SEA)14methods.For instance,Lim and Singh 11devel-oped a ﬁnite element model of ﬂexible casing to predict bearing and mount transmissibilities in a simple geared system.Van Roosmalen 12reported that the natural frequencies from a ﬁnite element analysis correlated well with modal tests for a simple gearbox at lower frequencies.Lim and Singh 14developed a two sub-system SEA model which included an analytical description of the coupling loss factor associated with the vibration transmission through rolling element bearings.To predict sound radiation from the gearbox,prior researchers have relied on either simple radiation efﬁciency models or large scale numerical codes (such as the boundary elements).However,a combination of ﬁnite and boundary element models often requires extensive computational time while yielding minimal insight.Jacobson et al.15predicted the radiation efﬁciency of a gearbox plate using ideal radiators like monopole,dipole,cylinder and the like but achieved limited success when compared with in-situ radiation measurements.Such simpliﬁed models yield only global trends and do not adequately describe the modal radiation characteristics of a gearbox.Kartik and Houser 16proposed a semi-empirical frequency-response based model to predict noise radiation from gearbox housings with a multi-mesh gear set.Also,they utilized the broad-band radiation efﬁciency model of a rectangular plate;again their model yields only broad trend over a range of gear mesh frequencies.Recently,Singh et al.17developed a semi-empirical model for predictions of the radiated whine noise by combining a linear time-invariant model of the internalgeared system with measured vibro-acoustic transfer functions of the structural paths (from gear/pinion motions in two directions to the radiated sound).They also found that the friction force dictates the OLOA dynamics and it signiﬁcantly inﬂuences the maximum force in the LOA direction.Overall,the above mentioned studies do not provide a tractable analytical or computational vibro-acoustic system model and all have included only the transmission error as the source except Singh et al.17who included sliding friction as well.We propose to overcome this deﬁciency in our article though we focus on a single mesh spur gear set in a simple gearbox.In our formulation (as conceptually shown in Fig.1),the pinion and gear of the internal spur gear pair sub-system are modeled as rigid disks,and the elastic deformations of the shaft and bearings are modeled using lumped elements.Vibratory angular motions are small in comparison to the mean motion,and the mean load is assumed to be high such that the dynamic load is not sufﬁcient to cause tooth separations 18;this leads to a linear time-varying system formulation.Though both excitations are interrelated,they are assumed to be most dominant in LOA and OLOA directions,respec-tively.Hence,only corresponding structural paths in these two directions are considered by neglecting the moment transfer elements in the bearing stiffness matrices.Also,by assuming the housing mass is much larger than the gears and shafts,an impedance mismatch is created with a rigid boundary condition at the bearing location 2.Thus,the internal geared system could be modeled separately and its resulting forced response provides force excitations to the structural paths.Further,we analytically or numerically describe the entire system model,unlike Kartik and Houser 16or Singh et al.17,who included empirical transfer functions.Finally,for the sake of illustration,we apply our formulation to the NASA test facility gearbox 13and it is assumed that the top plate is the main radiator due to its relatively high mobility as well as the way it is constructed.3SOURCE SUB-SYSTEM MODEL WITH TWO EXCITATIONSThe source sub-system is described by a recently developed 6DOF ,linear time-varying spur gear pair model 19that incorporates the sliding friction and realis-tic mesh stiffness,which is calculated by an accurate ﬁnite element/contact mechanical code 20.Rigid bearings are assumed as boundary conditions due to the impedance mismatch at the interface of shafts and bearings.Overall,the system formulations are summa-rized as follows.The governing equations for the torsional motions ␪p ͑t ͒and ␪g ͑t ͒of pinion and gearare:Fig.1—Vibro-acoustic model of a simpliﬁedgeared system with two excitations at the gear mesh,structure-borne paths through bearings and then radiation from the gearbox.Here,LOA is the line-of-action and OLOA is the off-line-of-action.Noise Control Eng.J.56(3),May-June 2008165J p ␪¨p ͑t ͒=T p +͚i =0n X pi ͑t ͒F pfi ͑t ͒−͚i =0nr bp N pi͑t ͒͑1͒J g ␪¨g ͑t ͒=−T g +͚i =0nX gi ͑t ͒F gfi ͑t ͒+͚i =0nr bg N gi͑t ͒͑2͒where n =floor ͑␴͒in which the “ﬂoor”function roundsoff the contact ratio ␴to the nearest integer (towards a lower value);J p and J g are the polar moments of inertia of the pinion and gear;T p and T g are the external and braking torques;r bp and r bg are base radii of the pinion and gear;and,N pi ͑t ͒and N gi ͑t ͒are the normal loads deﬁned as follows:N pi ͑t ͒=N gi ͑t ͒=k i ͑t ͓͒r bp ␪p ͑t ͒−r bg ␪g ͑t ͒+x p ͑t ͒−x g ͑t ͔͒+c i ͑t ͓͒r bp ␪˙p ͑t ͒−r bg ␪˙g ͑t ͒+x˙p ͑t ͒−x ˙g ͑t ͔͒͑3͒where k i ͑t ͒and c i ͑t ͒are the realistic mesh stiffness and viscous damping proﬁles;x p ͑t ͒and x g ͑t ͒denote the LOA displacements of pinion and gear centers.The sliding friction forces F pfi ͑t ͒and F gfi ͑t ͒as well as their moment arms X pi ͑t ͒and X gi ͑t ͒of the i th meshing pair are derived as:F pfi ͑t ͒=µi ͑t ͒N pi ͑t ͒,͑4a ͒F gfi ͑t ͒=µi ͑t ͒N gi ͑t ͒͑4b ͒X pi ͑t ͒=L XA +͑n −i ͒␭+mod ͑⍀p r bp t ,␭͒,͑5a ͒X gi ͑t ͒=L YC +i ␭−mod ͑⍀g r bg t ,␭͒͑5b ͒where the sliding friction is formulated by µi ͑t ͒=µ0sgn ͓mod ͑⍀p r bp t ,␭͒+͑n −i ͒␭−L AP ͔;␭is the base pitch;“sgn”is the sign function;the modulus function mod ͑x ,y ͒=x −y ·floor ͑x /y ͒,if y 0;⍀p and ⍀g are the nominal speeds (in rad/s);and,L AP ,L XA and L YC are geometric length constants 19.The governing equations for x p ͑t ͒and x g ͑t ͒motions in the LOA direction are:m p x¨p ͑t ͒+2␨pSx ͱK pSx m p x ˙p ͑t ͒+K pSx x p ͑t ͒+͚i =0nN pi ͑t ͒=0͑6͒m g x¨g ͑t ͒+2␨gSx ͱK gSx m g x ˙g ͑t ͒+K gSx x g ͑t ͒+͚i =0nN gi ͑t ͒=0͑7͒Here,m p and m g are the masses of the pinion and gear;K pSx and K gSx are the effective shaft stiffness values in the LOA direction,and ␨pSx and ␨gSx are the damping ratios.Likewise,the translational motions y p ͑t ͒and y g ͑t ͒in the OLOA direction are governed by:m p y¨p ͑t ͒+2␨pSy ͱK pSy m p y ˙p ͑t ͒+K pSy y p ͑t ͒−͚i =0nF pfi ͑t ͒=0͑8͒m g y¨g ͑t ͒+2␨gSy ͱK gSy m g y ˙g ͑t ͒+K gSy y g ͑t ͒−͚i =0nF gfi ͑t ͒=0͑9͒Finally,the dynamic forces at the bearings are as:F pBx ͑t ͒=−K pSx x p ͑t ͒−2␨pSx ͱK pSx m p x˙p ͑t ͒,͑10a ͒F pBy ͑t ͒=−K pSy y p ͑t ͒−2␨pSy ͱK pSy m p y˙p ͑t ͒,͑10b ͒F gBx ͑t ͒=−K gSx x g ͑t ͒−2␨gSx ͱK gSx m g x˙g ͑t ͒,͑11a ͒F gBy ͑t ͒=−K gSy y g ͑t ͒−2␨gSy ͱK gSy m g y˙g ͑t ͒.͑11b ͒Both LOA and OLOA bearing forces are predictedfor the example case (unity-ratio NASA spur gear pair with tip relief)with parameters of the pinion/gear given as follows 19:number of teeth=28;outside diameter=3.738in;root diameter=3.139in;diametral pitch=8in −1;center distance=3.5in;pressure angle=20°;face width=0.25in;tooth thickness=0.191in;and elastic modulus=30ϫ106psi.Predictions are then converted from time domain into frequency domain by using the fast Fourier transform (FFT)analysis method;comparisons at the ﬁrst three gear mesh frequencies are given in Fig.2over a range of the pinion torque T p .Observe that the friction dominated OLOA dynamic responses are less sensitive to a variation in T p .Dynamic interactions between the sliding friction and proﬁle modiﬁcations (embedded in the effective mesh stiffness k )may be analyzed in future work 21.4STRUCTURAL P ATHS ANDCONTRIBUTION FROM SLIDING FRICTION4.1Bearing and Housing ModelsPredicted bearing forces by the source sub-system provide excitations to the multi-input,multi-output (MIMO)structural paths for the gearbox of Fig.3(a).Force excitations are coupled at each bearing via a stiff-ness matrix ͓K ͔Bm (of dimension 5)that is calculated by using the algorithm proposed by Lim and Singh 9.Nominal shaft loads and bearing preloads are assumed166Noise Control Eng.J.56(3),May-June 2008to ensure a time-invariant ͓K ͔Bm .In order to focus onthe transmission error and sliding friction paths in the LOA and OLOA directions respectively,͓K ͔Bm is inten-tionally reduced into a 2by 2matrix by neglecting the moment transfer terms 10and assuming that no axial force is generated by the spur gear sub-system.Calcu-lated nominal bearing stiffness elements 9are K Bx =K By =2.8ϫ106lb/in at the mean operating condition;these are much larger than the shaft stiffness of 1.29ϫ105lb/in.This conﬁrms the impedance mismatch assumption made regarding the shaft/bearing interface.The implementation of ͓K ͔Bm into the ﬁnite element gearbox model of Fig.3(b)requires special attention 11,22.At high excitation (mesh)frequencies (say up to 5kHz),the geometric dimensions of the bearings are comparable to the plate ﬂexural wavelength.Hence the holes may signiﬁcantly alter theplate dynamics and such effects must be modeled 22.A rigid (with Y oung’s modulus 100times the casing steel)and massless beam element (with density 1%of the casing steel)is used to model the interface from shaft to the bearings.Only a small beam is selected in order to ensure that none of the beam resonances is found in the frequency range of interest.The shaft (beam)element is connected to the central bearing node though orthogonal foundation stiffness elements (K Bx and K By )in the LOA and OLOA directions,respec-tively.The central node is then connected to the circumferential bearing nodes by 12rigid and massless beams (one at each rolling element’s angular position)which form a “star”conﬁguration,such thattheFig.2—Dynamic bearing forces predicted under arange of T p given ⍀p =4875RPM and 140°F .(a):LOA bearing force;(b)OLOA bearing force.Key:m is the gear mesh frequency index.Key:᭺—,m =1;ᮀ—,m =2;᭞—,m =3.Fig.3—(a)Schematic of the NASA gearbox;(b)Finite element model of the NASA gear-box with embedded bearing stiffness ma-trices.Noise Control Eng.J.56(3),May-June 2008167displacement of the plate around the bearing hole are equal to the“housing node”at the center.4.2Experimental Studies and Validation ofStructural ModelTheﬁnite element model of Fig.3is created by using I-DEAS23for the NASA gearbox with bearing holes,embedded stiffness matrices͓K͔Bm,stiffening plates as well as clamped boundary conditions at four rigid mounts.Although the internal sub-system with gear pair and shafts is not included,it has been shown11 that an“empty”gearbox tends to describe the global dynamics of the entire system.Table1conﬁrms that the natural frequencies predicted by theﬁnite element model correlate well with measurements reported by Oswald et al.24despite minor structural modiﬁcations made to the gearbox.Mode shape predictions also match well with modal tests;Fig.4gives a typical comparison of structural mode at the8th natural frequency͑f n=2962Hz͒.In order to validate the structural paths,several transfer functions were measured for the NASA gearbox by assuming that the quasi-static system response is similar to the response under non-resonant rotating conditions.The gearbox was modiﬁed to allow controlled excitations to be applied to the gear-mesh and measured25.Brackets were welded to the bedplate of the gear-rig to mount shakers in the LOA and OLOA directions outside the gearbox,as shown in Fig.5(a). Stinger rods were connected from the shakers through two small holes in the gearbox and attached to a collar on the input shaft.Two mini accelerometers were fastened to a block behind the loaded gear tooth to measure the LOA and OLOA mesh accelerations. Band-limited random noise signals were then used as excitation signals and tests were done with only one shaker activated at a time with a600lb-in static preload(design load for the gears).Dynamic responses were measured to generate vibro-acoustic transfer functions.Sensor#1of Fig.5(a)is a tri-axial acceler-ometer mounted on the output shaft bearing cap to measure the LOA,OLOA,and axial vibrations.Sensors #2and#3are unidirectional accelerometers mounted on the top and back plates,respectively.The transfer function of the combined source-path sub-systems is predicted as:H˜S−P͑␻͒=H˜S͑␻͒·H˜P͑␻͒=H˜S͑␻͒·Y˜plate͑␻͒Y˜bearing͑␻͒͑12a͒Y˜plate͑␻͒=V˜plate͑␻͒F˜bearing͑␻͒,͑12b͒Y˜bearing͑␻͒=V˜bearing͑␻͒F˜bearing͑␻͒͑12c͒where Y˜plate͑␻͒and Y˜bearing͑␻͒are the transfer and driving point mobilities for the(top)plate and the bearing;these are derived from theﬁnite element model of the gearbox by using the modal expansion method with1%structural damping for all modes. Further,H˜S͑␻͒is the motion transmissibility from gear mesh to translational bearing responses(in LOA or OLOA direction)by using the8DOF linear time-invariant spur gear model17,25.Note that such a lumped model is insufﬁcient to capture the bending and ﬂexural modes of the gear blanks and shafts.Figure 5(b)shows that the measured motion transmissibility (OLOA direction)from gear mesh to the bearing compares well with predicted͉H˜S͑␻͉͒based on the linear time-invariant model25.In Fig.5(c),the predicted motion transmissibility͉H˜S−P͑␻͉͒from gear mesh to the top plate correlates reasonably well with measure-ment given the complexity of the system.The highest frequency is chosen such that the shortest wave-length is4times larger than the model element dimension on the top plate.Recall that interactions between the shaft and bearings/casing were neglected in our model by imposing the impedance mismatch condition.Conse-quently,an empirical weighting function 20log10͉W˜͑␻͉͒=10dB is added(uniformly over the entire frequency range)to“tune”the͉H˜P͑␻͉͒predic-tion in Fig.5(c)for better comparison.Further work is needed to quantify this effect;Karthik and Houser16 had also noted this issue.Table1—Comparison of measured natural fre-quencies andﬁnite element predictions ofthe NASA gearbox24.Gearbox mode index Measurements24(Hz)Finite elementpredictions(Hz)1658650 21049988 317091859 420001940 522762328 625362566 727222762 829622962 168Noise Control Eng.J.56(3),May-June20084.3Comparison of Structural Paths in LOAand OLOA DirectionsFirst,assume that (i)the bearing forces predicted by the source model 19are in phase at either bearing end for the pinion (or gear)shaft;(ii)the bearing forces of pinion and gear are same in magnitude but opposite in directions due to the symmetry of unity ratio gear pair.Second,the overall structural paths are derived for thetransmission error controlled LOA (or x )path and the friction dominated OLOA (or y )path in terms of thecombined (effective)transfer mobilities Y ˜e ,x͑␻͒and Y ˜e ,y͑␻͒:Y ˜e ,x ͑␻͒=͚nW ˜p ,x ,n Y ˜p ,x ,n ͑␻͒−͚nW ˜g ,x ,n Y ˜g ,x ,n ͑␻͒͑13a͒Fig.4—Comparison of one elastic deformation mode of the gearbox (at 2962Hz ):(a)modal experimentresult 24;(b)ﬁnite element prediction.Noise Control Eng.J.56(3),May-June 2008169Y ˜e ,y ͑␻͒=͚nW ˜p ,y ,n Y ˜p ,y ,n ͑␻͒−͚nW ˜g ,y ,n Y ˜g ,y ,n ͑␻͒͑13b ͒where W˜is the empirical weighting function (10dB applied over the spectrum);and the subscript n is the index of the two ends of pinion/gear shafts.Figure 6compares the magnitudes of Y ˜e ,x ͑␻͒and Y ˜e ,y͑␻͒at the sensor location on the top plate.Different peaks are observed in the LOA and OLOA paths spectra.This implies that at certain frequencies (e.g.650and 1700Hz),the OLOA path (and thus the frictional effects)could be dominant over the LOA path (and thus the transmission error effects)given comparable force excitation levels.The proposed method thus provides an efﬁcient tool to quantify and evaluate the relative contribution of structural path due to sliding friction.The top plate velocity distribution V ˜top͑␻͒could then be predicted by using Eqn.(14),where F ˜p ,B ,x ͑␻͒andF ˜p ,B ,y ͑␻͒are the pinion bearing forces predicted by the source model in the LOA and OLOA directions.Figure 7(a)shows the surface interpolated velocity distribu-tions on the top plate,as deﬁne below,at three mesh harmonics ͑m =1,2,3͒given T p =500lb-in and ⍀p =4875RPM:V ˜top ͑␻͒=12F ˜p ,B ,x ͑␻͒Y ˜e ,x ͑␻͒+12F ˜p ,B ,y ͑␻͒Y ˜e ,y ͑␻͒͑14͒5PREDICTION OF RADIATED NOISE AND CONTRIBUTION FROM SLIDING FRICTION SOURCE 5.1Sound Pressure Prediction Using Rayleigh Integral TechniqueSince the rectangular top plate is the main radiator 24of the gearbox due to its relatively high mobility,Rayleigh integral 26is used to approximate the sound pressure by assuming that the top plate is placed in an inﬁnite rigid bafﬂe and each elementary plate surface is an equivalent point source in a rigid wall.The sound pressure amplitude at frequency ␻(rad/s)is given asfollows where ␳is the air density,Q ˜i ͑␻͒=V ˜i ͑␻͒⌬S iis the source strength of i thequivalent point source with area ⌬S i ,k ͑␻͒is the wave number and r i is the distance from the i th source to thereceiver:Fig.5—(a)Experiment used to measure the struc-tural transfer functions;(b)Comparisonof the transfer function magnitudes from gear mesh to bearings;(c)Comparison of the transfer function magnitudes from gear mesh to a sensor on the top plate (gearbox).Key:—,measurements;ؠ,pre-dictions,—.Fig.6—Magnitudes of the structural path mobili-ties in the OLOA and LOA directions.Response for each (due to excitation at the gear mesh)is calculated at the sensor location on the top plate (gearbox).Key:—,mobility of the OLOA path;-·-·,mo-bility of the LOA path.170Noise Control Eng.J.56(3),May-June 2008P ˜͑␻͒=j ␻␳2␲͚i Q ˜i ͑␻͒r ie −jk ͑␻͒r i ͑15͒For the calculation of whine noise,␻is chosen to coincide with ﬁrst three gear mesh frequencies of inter-est;⌬S i is chosen such that its dimension (on the top plate)is smaller than 1/4of the wave-length at thehighest gear mesh frequency.The overall noise is thencalculated by combining the contributions of all equivalent sources (using Eqn.(15))at the pared with conventional boundary element analy-sis,Rayleigh integral approximates sound pressure in a fraction of the computation time 26.Hence,it is more suitable for parametric design studies.Althoughsome(a)(b)(c)Fig.7—Comparison of the normal surface velocity magnitudes and substitute source strength vectorsunder T p =500lb-in and ⍀p =4875RPM .(a)Line 1:interpolated surface velocity on top plate;(b)Line 2:simpliﬁed 2D gearbox model with 15substitute source points;Key:ؠ,original surface velocity magnitude;ϫ,surface velocity magnitude by substitute sources;*,locations of substi-tute sources.(c)Line 3:substitute source strengths in complex plane for 2D gearbox.Column 1:gear mesh frequency index m =1;Column 2:m =2;Column 3:m =3.Noise Control Eng.J.56(3),May-June 2008171researchers 27have pointed out that Rayleigh integral may give large errors for sound pressure prediction if applied to strongly directional,three dimensional (3D)ﬁelds,such errors are not signiﬁcant in our application due to a ﬂat top plate and favorable surroundings (such as rigid side plates and the anechoic chamber).5.2Sound Pressure Prediction UsingSubstitute Source MethodAs an alternative to the Rayleigh integral technique or the boundary element method,a newly developed algorithm based on the substitute source approach 28is used to compute the radiated or diffracted sound ﬁeld.It is conducted by removing the gearbox and introduc-ing acoustic sources within the liberated space which yield the desired boundary conditions at the box surface (Neumann problem).Solutions are obtained in terms of the locations and/or the strengths of the substi-tute sources by minimizing the error function between original and estimated particle velocity normal to the interface surface 28.Since the surface velocity distributions on the gearbox plate(s)are essentially symmetric along the center lines due to geometric symmetry,velocity distri-butions in Fig.3(b)along the border lines of EFGH plane are chosen to simplify the 3D gearbox into a 2D radiation model for simpler data representation as well as faster computation.Zero (negligible)velocity distri-bution is assumed along lines EF ,FG and HE since the microphone (receiver)is positioned above the center of major radiator,i.e.the top plate.A 2D line source uniformly pulsating with unit-length volume velocity Q Јis chosen as the substitute source.Its radiation ﬁeld is the same in any plane perpendicular to the sourceline.Amplitudes of the sound pressure ͑P˜͒and radial velocity ͑V ˜r ͒of such source are given by the following,where H v ͑2͒is the Hankel function of second kind and order v .P ˜͑␻͒=k ͑␻͒␳c 4Q ˜Ј͑␻͒H 0͑2͓͒k ͑␻͒r ͔,͑16a ͒V ˜r ͑␻͒=−j k ͑␻͒4Q ˜ЈH 1͑2͓͒k ͑␻͒r ͔͑16b ͒A “greedy search”algorithm is used to search for“optimal”substitute sources:First,a large number of candidate source positions within the vibrating body are deﬁned,e.g.at the vertices of a square grid.Second,a single position is ﬁrst found which allows the point source to produce the smallest possible deviation between the original and estimated normal surface velocities.The estimation is then subtracted from the original velocity to get a velocity residual.Third,among the rest of candidate points,a new position is found which makes the second source maximally reduce the velocity residual of the ﬁrst step.Once found,the source strengths of both sources are adjusted for a best ﬁt of the original surface velocity and a new residual velocity.Each subsequent step deﬁnes a new optimum source position among the ones not already used 28.The source strengths are curve-ﬁt by minimiz-ing the root-mean-square (RMS)value of the velocityerror.The vector of complex-valued source strength Q ˜Јis related (as shown below)to the vector V ˜nof complex-valued normal surface velocity at controlpoints via the source-velocity transfer matrix T ˜=wherer ij =͉rជi −r ជj ͉and ␣ij is the angle between vector r ជi −r ជand the outer normal to the surface.Q ˜Ј͑␻͒=T ˜=−1͑␻͒V ˜n ͑␻͒,͑17a ͒T ˜ij ͑␻͒=−j k ͑␻͒4H 1͑2͓͒k ͑␻͒r ij ͔cos ͑␣ij ͒͑17b ͒To minimize the impact of an ill-conditioned matrix,the number of control points is kept well above that of independent source points.Minimization of the RMS error using pseudo-inverse yields the following,where the asterisk signiﬁes the conjugate transpose:Q ˜Ј͑␻͒=͓T ˜=͑␻͒*T ˜=͑␻͔͒−1T ˜=͑␻͒*V ˜n ͑␻͒͑18͒The difference between synthesized and originalsurface normal velocities is:⌬V ˜͑␻͒=⌶=͑␻͒V ˜n͑␻͒,͑19a ͒⌶˜=͑␻͒=T ˜=͑␻͓͒T ˜=͑␻͒*T ˜=͑␻͔͒−1T ˜=͑␻͒*−I ˜=͑␻͒͑19b ͒where I ˜=͑␻͒is the identity matrix.The matrix ⌶˜=͑␻͒appears as a velocity error matrix.The RMS velocity error is normalized by using the RMS value of original velocity as:e ˜RMS ͑␻͒=E ˜RMS ͑␻͒V ˜n ,RMS͑␻͒=ͱV ˜n͑␻͒*⌶˜=͑␻͒*⌶˜=͑␻͒V ˜n ͑␻͒V ˜n ͑␻͒*V ˜n͑␻͒͑20͒This search algorithm described 28is based on engineering “common sense”rather than a rigorous mathematical optimization of the substitute source positions.Consequently,it may not necessarily lead to optimum positioning,i.e.to the solution which gives the smallest possible RMS velocity error.The overall advantage is in its simplicity of application as well as in providing solutions that are much better than those obtained via an arbitrary selection of the source172Noise Control Eng.J.56(3),May-June 2008。

ARAMCO阿美认证检验员考试题及答案

1. What is the purpose of a penetrameter or IQI?Indicates radiographic sensitivity and quality of the techniques.2. What is meant by the term sensitivity with regard to radiography?The ability of a radiographic technique to reveal defects of a specific size.3. What are the limitations of magnetic particle inspection and liquid penetrant inspection?M.P. can be used only on ferromagnetic materials to detect surface subsurface discontinuities.L.P. can be used to detect defects open to the surface.Both M.P. and L.P. require surface preparations before testing.4. What information is contained in a Welding Procedure Specification?Process type, groove (joint) design, material type, material thickness, position of groove, filler metal type, pre-heat requirements, interpass temperature, post weld heat treatment requirements, shielding gas or flux type, electrical characteristics, techniques of welding.5. Why is post weld heat treatment required for some type weldments?Relieve stresses, lower hardness6. What is the basic difference between a DIN and an ASME penetrameter?DIN penetrameter is a wire type penetrameter,ASME penetrameter is a hole type penetrameter.7. What type of defects would you expect to find during visual inspection of a completed weld? Undercutting, excessive or insufficient weld reinforcement, excessive irregularities, incomplete penetration on a single butt-weld, weld spatter, etc..8. What precaution must be taken with low hydrogen welding electrodes?Store in oven when not in use, kept in heated container by welder awaiting use.9. What information normally appears on radiography?Penetrameter identification, Location of markers to ensure complete coverage, the name of the inspecting laboratory, the date, the part number, whether original or subsequent exposure.10. What is the rule of thumb used to determine the amperage for the dry, prod method of magnetic particle inspection?100 – 125 amps / inch.11. What materials are the transducer made from?Quartz, Barium Titanate, Lithium Sulphate and Ceramics.12. What is a film defect?A mark on the film usually caused by improper handling or processing.13. If you were inspecting an item using the prod method and located a weak crack pattern, where would you place the prods to obtain a stronger location?Relocate prods 90 degrees to the crack pattern and re-inspect.14. What typical defects would you expect while inspecting a casting?Sand and slag inclusions, gas porosity, shrinkage, hot tears.15. Describe the pulse echo technique.When an electric current is applied to the crystal, the crystal vibrates transforming the electric energy into mechanical vibrations which are transmitted through a coupling medium into the test material. These pulse vibrations propogate through the object and are reflected as echoes from both discontinuities and the back surface of the test piece and will appear as a vertical deflection on the cathode ray tube or oscilloscope. 16. Which method i.e. magnetic particle examination or liquid penetrant examination, locate non-metallic inclusions open to the surface.Both.17. What is a ―Weld Procedure Qual ification Record?A document which contains, essentially the same information as a WPS but includes the results of the tests necessary to qualify the WPS. Also listed are the ―essential variable‖ of the specific process of processes. 18. What is meant by t he term ―Film Density‖?Measurement or film blackening.测量或胶片的发黑度。

美国进口发票要求

IntroductionV.1This manual has been prepared to ensure that our vendors comply with the United States Customs Regulations. By following this manual, Pitney Bowes will be able to import goods into the US without serious delays due to missing or incorrect information. The enclosed data was prepared based on the United States Customs Regulations.There are four sections to this manual. They are:1) Invoicing Standards for Commercial shipments (page 2), Return shipments (page 5), TestShipments (page 8) and Sample shipments (page 11). Each standard consists of threepages.a) The first page explains how to prepare the invoiceb) The second page provides an example of the invoicec) The third page provides an example of a packing list2) Alphabetized product list which requires that the product net weight be listed on thecommercial invoice or packing slip. If part of the product name that you are shipping shows up on the list, you MUST indicate the product’s net weight (page 14).3) Alphabetized product list, which requires additional information to be noted on thecommercial invoice for proper classification to US Customs. You may be requested toanswer the questions on section 4 below. If the product name is on the list, you mustanswer all questions by either sending a copy of the questionnaire with the shipment or by adding the details to the commercial invoice (starts page 15).4) Product specific technical questions, which must be completed to ensure properclassification (starts page 18).Should there be any questions on this manual, call Robert Emma, 203-426-7328, or send email to robert.emma@.COMMERCIAL INVOICE DETAILSBelow you will find a list of items required on the commercial invoice supplied by Pitney Bowes (PB) vendors. If you should require clarity on any item, please contact Robert Emma, 203-426-7328. (NOTE: One invoice should be created for every individual shipment, not each purchase order. A shipment is equal to one bill of lading)1. Supplier Company Name, Address, Telephone and Fax number2. Supplier Invoice Number (same number issued for payment)3. Invoice Date4. Company Name and Address which the goods were sold to5. Company Name and Address where the goods are to be shipped to6. Invoicing Terms (INCO TERMS)7. Form of Currency which PB is being invoiced8. Country of Manufacture (origin)a. If more than one origin, list the origin next to the product/component number.9. Purchase Order Numbera. For multiple purchase orders on one invoice, list the purchase order number prior to the partnumbers shipped against that purchase order.10. Product Number / Component Numbera. The Pitney Bowes product or component number must be listed. Not the supplier part number11. Product Description (*)a. Finished Goodsi. Complete Description of the product – include as much detail as possibleb. Partsi. Complete Description of the product/item.ii. Product Content (ie: plastic, Steel, copper)iii. Describe the function of the partiv. List the finished goods or machine the part is made forv. Belts & Bearings require the name of the actual manufacturer and Country where they were made12. Units Shippeda. List the number of units shipped per part/item number13. Price Per Unit14. Net Weight Per Unit15. Extended Price (Price Per Unit multiplied by the Number of Units Shipped)16. Total Invoice Value17. Provide any details pertaining to Assists for the product on the invoice18. Finished goods where items were supplied or additional payments were made, shall include the details ofthe transaction. For Example:a. “Materials were supplied free of charge by Pitney Bowes, Inc. Under PO _______ and wasvalued at $_______ per unit. These goods were shipped _CIF delivered and are not included inthe value set forth above. <OR>b. Engineering charges of US $ ____ were previously paid by Pitney Bowes Inc. under PONos. __________ and are not included in the value set forth above.19. Provide all Trademark Data20. Solid Wood Packing Material Statement (SWPM) <or> Certificate21. HTS number if known (export only)22. Buying Commissions23. Selling Commissions24. Toxic Substance Control Act Statement(*) Additional information may be required for certain products. See attachments to find a product/part name that requires additional detailCommercial Invoice ExampleABCCompany Date: MM/DD/YYYYUnite 1000 13th FloorCentre 9 Science Museum Road Invoice #: abc123456789OsakaJapanTel:215-09999-9999Fax:215-0999-5555Sold To: Ship To:Pitney Bowes Inc.11 Edmond Road 35 Washington StreetNewtown, CT 06470 Stamford, CT 06926Inco Terms: EXW Osaka Factory PO #: See Below Currency: USDProduct ID Product Name and Description Country ofOrigin UnitsPrice PerUnitExtendedPricePO 4500011111J999 Scale (2lb) Japan 50 $ 35.00 $ 1,750.00 123456789 Seal Moistener China 200 $ 1.25 $ 250.00 PO 450000121119JK9 Inserting Machine China 10 $ 125.00 $ 1,250.00 987654 Steel Screw M 4x16 Japan 1000 $ 0.10 $ 100.00 PO 5500002211321654 Motor - 32V - 12W Hong Kong 25 $ 7.25 $ 181.25 TOTAL 1285 $ 3,531.251. Assist Statement if applicable2. Solid Wood Packing Material Statement (SWPM) <or> CertificateCommercial Packing List ExamplePACKING LISTABCCompanyUnite 1000 13th FloorCentre 9 Science Museum RoadOsakaJapanTel:215-09999-9999Fax:215-0999-5555Ship To:Pitney Bowes Inc.35 Washington StreetStamford, CT 06926PO #: See BelowMarks andNumbers Product ID Product Name andDescriptionCountry ofOrigin UnitsNet WeightKGGrossWeightKGPO 4500011111Carton 1-10 J999 Scale (2lb) Japan 50 100120 Carton 11-13 123456789 Seal Moistener China 200 4550 PO 45000012111Carton 14-18 9JK9 Inserting Machine China 10 90.71105 Carton 19 987654 Steel Screw M 4x16Japan 1000 22.6824.68 PO 5500002211Carton 20-22 321654 Motor - 32V - 12W Hong Kong 25 56.762.5 22 CartonsTOTAL 1285 315.09362.18RETURN SHIPMENT INVOICE DETAILSBelow you will find a list of items required on the commercial invoice supplied by Pitney Bowes (PB) vendors. If you should require clarity on any item, please contact Robert Emma, 203-426-7328. (NOTE: One invoice should be created for every individual shipment, not each purchase order. A shipment is equal to one bill of lading)1. Supplier Company Name, Address, Telephone and Fax number2. Supplier Invoice Number (same number issued for payment)3. Invoice Date4. Company Name and Address which the goods were sold to5. Company Name and Address where the goods are to be shipped to6. Invoicing Terms (INCO Terms)7. Form of Currency which PB is being invoiced8. Country of Manufacture (origin)a. If more than one origin, list the origin next to the product/component number.9. Purchase Order Number (PO)/Return Authorization Number (RA)/PB Export Number (EN)a. For multiple purchase orders on one invoice, list the PO/RA/EN number prior to the part numbersshipped against that purchase order.10. Product Number / Component Numbera. The Pitney Bowes product or component number must be listed. Not the supplier part number11. Product Description (*)a. Finished Goodsi. Complete Description of the product – include as much detail as possibleb. Partsi. Complete Description of the product/item.ii. Product Content (ie: plastic, Steel, copper)iii. Describe the function of the partiv. List the finished goods or machine the part is made forv. Belts & Bearings require the name of the actual manufacturer and Country where they were made12. Units Shippeda. List the number of units shipped per product/component number13. Price Per Unit NOTE: there will be two values listed for each product if the item is a return after repaira. Price per unit for the value of the machine prior to the repair (original sale value to PB)b. Cost to repair the unit. This must encompass all costs contributing to repairing the item.14. Net Weight Per Unit15. Extended Price (Price Per Unit multiplied by the Number of Units Shipped)16. Total Invoice Value17. Provide any details pertaining to Assists for the product on the invoice18. Provide all Trademark Data19. Solid Wood Packing Material Statement (SWPM) <or> Certificate20. HTS number if known (export only)21. Buying Commissions22. Selling Commissions23. Toxic Substance Control Act Statement –Chemicals Only (inks, dies etc.)24. If the repair is FREE OF CHARGE to PB, then the statement “NO CHARGE TO PITNEY BOWES –REPAIR FREE OF CHARGE” must be noted on the invoice.25. If the return is for other reasons than “ after repair”, please state the reason for the return on the invoice.(ie: incorrect goods shipped, returned from exhibition, defective goods, etc.)(*) Additional information may be required for certain products. See attachments to find a product/part name that requires additional detailReturn Shipment Invoice ExampleABCCompany Date:MM/DD/YYYYUnite 1000 13th FloorCentre 9 Science Museum Road Invoice #: abc123456789OsakaJapanTel:215-09999-9999Fax:215-0999-5555Sold To: Ship To:Pitney Bowes Inc.11 Edmond Road 35 Washington StreetNewtown, CT 06470 Stamford, CT 06926Inco Terms: EXW Osaka Factory PO #:Return ID333355555 Currency: USDProduct ID Product Name and Description Country ofOrigin UnitsPrice PerUnitExtendedPriceJ999Scale (2lb) Returned after Repair (*) China 50 $ 35.00 $ 1,750.00 Repair Value for Customs Purposes Only (**) Repaired in Japan $ 148.00NO CHARGE TO PITNEY BOWES - REPAIR FREE OF CHARGETOTAL 50 $ 1,898.001. Assist Statement if applicable2. Solid Wood Packing Material Statement (SWPM) <or> CertificateReturn Shipment Packing List ExamplePACKING LISTABCCompanyUnite 1000 13th FloorCentre 9 Science Museum RoadOsakaJapanTel:215-09999-9999Fax:215-0999-5555Ship To:Pitney Bowes Inc.35 Washington StreetStamford, CT 06926PO #: Return ID 333355555Marks andNumbers Product ID Product Name andDescriptionCountry ofOrigin UnitsNet WeightKGGrossWeightKGCarton 1-10 J999 Scale (2lb) China 50 100120 10 CartonsTOTAL 50 100120TEST EQUIPMENT INVOICE DETAILSBelow you will find a list of items required on the commercial invoice supplied by Pitney Bowes (PB) vendors. If you should require clarity on any item, please contact Robert Emma, 203-426-7328. (NOTE: One invoice should be created for every individual shipment, not each purchase order. A shipment is equal to one bill of lading)1. Supplier Company Name, Address, Telephone and Fax number2. Supplier Invoice Number (same number issued for payment)3. Invoice Date4. Company Name and Address which the goods were sold to5. Company Name and Address where the goods are to be shipped to6. Invoicing Terms (INCO Terms)7. Form of Currency which PB is being invoiced8. Country of Manufacture (origin)a. If more than one origin, list the origin next to the product/component number.9. Purchase Order Number10. Product Number / Component Numbera. The Pitney Bowes product or component number must be listed. Not the supplier part number11. Product Description (*)a. Finished Goodsi. Complete Description of the product – include as much detail as possibleb. Partsvi. Complete Description of the product/item.vii. Product Content (ie: plastic, Steel, copper)viii. Describe the function of the partix. List the finished goods or machine the part is made forx. Belts & Bearings require the name of the actual manufacturer and Country where they were made12. Units Shippeda. List the number of units shipped per product/component numberb. Price Per Unit - A price MUST be established for Test items.13. Net Weight Per Unit14. Extended Price (Price Per Unit multiplied by the Number of Units Shipped)15. Total Invoice Value16. Provide any details pertaining to Assists for the product on the invoice17. Provide all Trademark Data18. Solid Wood Packing Material Statement (SWPM) <or> Certificate19. HTS number if known (export only)20. Buying Commissions21. Selling Commissions22. Toxic Substance Control Act Statement – Chemicals Only (inks, dies etc.)23. If the test item is FREE OF CHARGE to PB, then the statement “Values are for US Customs PurposesOnly. No charge to Importer. Items are for testing purposes only. Not for resale”24. If the test equipment is to be returned to the vendor, then the following statement must be noted on theinvoice “Temporary Import-Te Be Returned After Testing”(*) Additional information may be required for certain products. See attachments to find a product/part name that requires additional detailTest Equipment Invoice ExampleABCCompany Date: MM/DD/YYYYUnite 1000 13th FloorCentre 9 Science Museum Road Invoice #: abc123456789OsakaJapanTel:215-09999-9999Fax:215-0999-5555Sold To: Ship To:Pitney Bowes Inc.11 Edmond Road 35 Washington StreetNewtown, CT 06470 Stamford, CT 06926Atten: John WalkerInco Terms: EXW Osaka Factory PO #: 450000000009Currency: USDProduct ID Product Name and Description Country ofOrigin UnitsPrice PerUnitExtendedPriceJ999 Scale (2lb) Japan 50 $ 35.00 $ 1,750.00 9JK9 Inserting Machine China 10 $ 125.00 $ 1,250.00 Values are for US Customs Purposes only. No charge to Importer.Items are for testing purposes only. Not for resale.To be returned after testingTOTAL 60 $ 3,000.001. Assist Statement if applicable2. Solid Wood Packing Material Statement (SWPM) <or> CertificateTest Equipment Packing List ExamplePACKING LISTABCCompanyUnite 1000 13th FloorCentre 9 Science Museum RoadOsakaJapanTel:215-09999-9999Fax:215-0999-5555Ship To:Pitney Bowes Inc.35 Washington StreetStamford, CT 06926PO #: 450000000006Marks andNumbers Product ID Product Name andDescriptionCountry ofOrigin UnitsNet WeightKGGrossWeightKGCarton 1-10 J999 Scale (2lb) Japan 50 100120 Carton 11-15 9JK9 Inserting Machine China 10 90.7110515 CartonsTOTAL 60 190.71225SAMPLE SHIPMENT INVOICE DETAILSBelow you will find a list of items required on the commercial invoice supplied by Pitney Bowes (PB) vendors. If you should require clarity on any item, please contact Robert Emma, 203-426-7328. (NOTE: One invoice should be created for every individual shipment, not each purchase order. A shipment is equal to one bill of lading)1. Supplier Company Name, Address, Telephone and Fax number2. Supplier Invoice Number (same number issued for payment)3. Invoice Date4. Company Name and Address which the goods were sold to5. Company Name and Address where the goods are to be shipped to6. Invoicing Terms (INCO Terms)7. Form of Currency which PB is being invoiced8. Country of Manufacture (origin)a. If more than one origin, list the origin next to the product/component number.9. Product Number / Component Numbera. Indicate the identification number of the bulk items being shipped (if any)10. Product Description (*)a. Itemsi. Complete Description each item (i.e.: size of envelope/paper)ii. Product Content (i.e.: wood pulp)iii. Describe the function of the item11. Units Shippeda. List the number of units shipped for each itemb. Price Per Unit - A price MUST be established for Test items.12. Net Weight Per Unit13. Extended Price (Price Per Unit multiplied by the Number of Units Shipped)14. Total Invoice Value15. Provide any details pertaining to Assists for the product on the invoice16. Provide all Trademark Data17. Solid Wood Packing Material Statement (SWPM) <or> Certificate18. HTS number if known (export only)19. Buying Commissions20. Selling Commissions21. Toxic Substance Control Act Statement - Chemicals Only (inks, dies etc.)22. If the test item is FREE OF CHARGE to PB, then the statement “Values are for US Customs PurposesOnly. No charge to Importer. Samples for testing purposes only. Not for resale” must be noted on the invoice.(*) Additional information may be required for certain products. See attachments to find a product/part name that requires additional detailSample Shipment Invoice ExampleABCCompanyDate: MM/DD/YYYY29 London AvenueUnitedKingdomInvoice #: abc123456789Tel:215-09999-9999Fax:215-0999-5555Sold To: Ship To:Pitney Bowes Inc.11 Edmond Road 35 Washington StreetNewtown, CT 06470 Stamford, CT 06926Atten: Joe FosterIncoTerms: EXW UK Factory PO #: 450000000009 Currency: USDProduct ID Product Name and Description Country ofOrigin UnitsPrice PerUnit ExtendedPriceJ999 Envelopes - Standard white [net weight 0.2 g]UK 200 $ 0.15 $ 30.009JK9 Paper - plain 8.5 x 11 inch [net weight0.3g} Germany 200 $ 0.10 $ 20.00Values are for US Customs Purposes only. No charge to Importer. Not for resaleSamples for testing machines.TOTAL 400 $ 50.00 1. Solid Wood Packing Material Statement (SWPM) <or>CertificateSample Shipment Packing List ExamplePACKING LISTABCCompany29 London AvenueUnitedKingdomTel:215-09999-9999Fax:215-0999-5555Ship To:Pitney Bowes Inc.35 Washington StreetStamford, CT 06926PO #: 450000000006Marks andNumbers Product ID Product Name andDescriptionCountry ofOrigin UnitsTotal NetWeight KGTotalGrossWeightKGCarton 1 J999 Paper - plain 8.5 x 11 inch UK 200 1.5 1.8 Carton 1 9JK9 Paper - plain 8.5 x 11 inch Germany 200 2 2.21 CartonsTOTAL 400 3.54Alphabetized product list requiring the product net weight .The following list of items REQUIRES a Net Weight. For each item shipped, you MUSTindicate the item net weight on the packing list/commercial invoice. If only part of the itemname is in the product being shipped, then you MUST indicate the net weight also.A4 Sheet Ink CartridgeAirshaft InsertsAngle Complete Keyboard MembraneAnti Static Coating KnobAxel LabelBearing LatchBelt LeafletsBelt Pulley Lens PackersBlade LettersBolt LeverHousingBox LockingBracket MoistenerBracket Mounting Pin NutringBrush OBushing Open Ended Ring SpannerCable Strap Packing InsertCap PaperCardboard PaperRetardCastor PinC-Clip PistonChain Pivot Insert FrameCover Lock Assy Plastic BallCutsheets PulleyCutter RollerDamper ScrewDecal SealDisplay Overlay SealerDust Ring ShaftEccentric Pillar Silicon OilElectrodes SlideAssyEncoder Mounting Plate SpindleEnvelopes SpringFiber Optic Support Steel BallFlange StudFlexible Cable Wires Tape AdhesiveForms TechnicalDocumentation Gear Torx Head ScrewGearbox ValveGenerator WasherClothGlue WettingPivotGrease WheelGround Braid Wick AssyProduct List.DIRECTIONS: Simply click on the page number and you will be brought to the form.Product Description Information Needed for U.S. ClassificationAssignment Part also known as Page #Assemblies What are the components and function of theassembly? See Multifunctional Assemblies Guidefold roller;motor;cupmoistener;docu.hopper37Battery See 'Battery' guide. 18 Bearing See 'Bearing' guide. 19 Belts See 'Belt' guide. 20 Bolt See 'Bolt' guide. 23Bottle/Containers What is the composition (plastic, glass, etc) andvolume (550 ml, etc) of the bottle/container? 55Bracket What is the purpose and the composition of thebracket?55Brake Is the brake electromagnetic or not? 55 Brush What is the use of the brush and its composition? 55 Bushing Confirm this is not a bearing. If a bearing see guide 19 Cable See 'Wire and Cable' guide. 54 Capacitor See 'Capacitor' guide. 24 Cardboard How is the cardboard used and is it corrugated? 55 Castor What is the diameter of the castor with the tyre? 55 Chain See 'Chain' guide. 25Circuit breaker Is the circuit breaker in a molded case and what isthe voltage? 55Circuit, Integrated See ‘Integrated Circuit” Guide (Revision 1) (2 pages)32Clamp What is the purpose and the composition of theclamp?55Clip What type of clip, ie.circlip? What is the compositionof the clip? What is the clip used for? 55Clutch Is the clutch electromagnetic or not? 55Collar What is the composition of the collar and how doesit function? 55Connectors See 'Plugs, Sockets And Connectors' guide. 43 Contactor See 'Switch' guide. (2 pages)50 Control panel Does control panel include the keyboard? 55Cord See 'Electric Cable' guide. connector cord;handset cord 27C-ring See 'Pin' guide. 42 Documents See “printed Documents With Text” guide 45 E-ring See 'Pin' guide. 42 Fan See 'Fan' guide. 28 Filter See 'Filter' guide. 29Folder Is this a table top machine or does it stand on thefloor? 55Fuse See 'Switch' guide. (2 pages) 50 Gasket See 'Gasket' guide. 30 Gear See 'Gear Box' guide. 31General Goods See ‘General Goods’ guide55 Handles & knobs What is the composition (plastic, metal, etc)?55 Harness See 'Electric Cable' guide. wiring harness 27 Hinge What is the composition? 55 Holder What is the function? 55 Hook See 'Screw' guide.47 ICSee 'Integrated Circuit' guide. (Revision 1) (2 pages) 32 Indicator Panel See ‘Indicator Panel’ guide. 56 InkSee ‘INK’ guide57 InserterIs this a table top machine or does it stand on the floor?55 Instruction sheet What is the composition and how many pages? 55 Inverter See 'Power Supply' guide. 44 KitsSee 'Kit' guide.34 Label What is the composition; dimensions and does it contain adhesive? 55 Lamp See 'Lamp' guide. 35 Latch What is the composition and function? 55 LED See 'Diodes, Transistors' guide. 26 Lens Is this optically worked and is it mounted? 55 Lever What is the composition and use? 55 Magnet Is this made of metal?55 Memory See 'Integrated Circuit' guide. (Revision 1) (2 pages) memory cards 32 Mirror Is this optically worked and is it mounted? 55 Motor See 'Motor' guide. 36 Nut See 'Nut' guide. 38 O-ringSee 'O-ring' guide. 39 Paper (blank) See “Blank Paper’ guide (2 pages) 21 Paper with Text See “Printed Documents with Text” guide 45 Pawl What is the composition and use? 55 Pin See 'Pin' guide. 42 PlugSee 'Plugs, Sockets, Connectors' guide. 43 Potentiometer Is this wire wound or variable; what is the wattage? 55 Power supply See 'Power Supply' guide. 44 Printed CircuitSee ‘Printed Circuit’ guide58 Printed circuit board Does it contain relays, circuit breakers, fuses, orswitches?PCB;P C Board 55 Printed wiring board Does it contain relays, circuit breakers, fuses, orswitches?PWB; P W board55 Printer See ‘Printer’ guide. 59 Pulley Is this a grooved pulley? 55 Rectifier See 'Power Supply' guide. 44 Relay See 'Switch' guide. (2 pages)50Resistor See 'Resistor' guide. 46 Ring What is the composition? 55Scale See ‘Scale’ guide. 60 Screws See 'Screw' guide. 47 Seal See 'Seal' guide. 48Sensors Is this a photo sensor, optical coupled sensor, safetylight curtain, or a solid-state switch? 55Shaft See 'Transmission' guide. 52Sheet What is the composition; dimensions and does itcontain adhesive? 55Socket See 'Plugs, Sockets, Connectors' guide 43 Solenoid Is this electromagnetic? 55 Spacer What is the composition and use? 55 Sponge What is the composition and use? 55 Spring See 'Spring' guide. 49 Stopper What is the composition and use? 55 Stud What is the composition and is it threaded? 55 Switch See 'Switch' guide. (2 pages) 50 Terminal See 'Plugs, Sockets, Connectors' guide. 55 Tool How is the tool used? 55Transformer Is this a liquid transformer? What is the kVA rating?If less than 1kVA what is the VA rating? 55Washer See 'Washer' guide. 53Wire See 'Wire and Cable' guide; See 'Electric Cable'guide.54ANY PRODUCTNOT LISTED See ‘General Goods’ guide 55CLASSIFICATION GUIDE FOR BATTERIESPlease answer the following questions regarding BATTERIES (choose 1. Primary OR 2. Electric storage and then the appropriate details):Part#_________________________________1. If PRIMARY Cells or Batteries(Circle a, b, c ,d, e, or ,f, and appropriate details as necessary):a. Manganese dioxideb. Mercuric oxidei. Having an external volume not exceeding 300 cm3ii. Otherc. Silver oxidei. Having an external volume not exceeding 300 cm3ii. Otherd. Lithiume. Air-zincf. Other2. If ELECTRIC STORAGE BATTERIES (Circle a, b, c, d, or , e , and appropriate details asnecessary):a. Lead-acid storage batteries, of a kind used for starting piston enginesi. 12V batteries1. NOT exceeding 6 kg in weight2. exceeding 6 kg in weightii. Otherb. Other lead-acid storage batteriesi. Used as the primary source for electrically powered vehiclesii. 6 V batteriesiii. 12 V batteriesiv. 36 V batteriesv. Otherc. Nickel-cadmium storage batteriesi. Used as the primary source for electrically powered vehiclesii. Sealediii. Otherd. Nickel-iron storage batteriesi. Used as the primary source for electrically powered vehiclesii. Othere. Other storage batteriesi. Used as the primary source of electrically powered vehiclesii. OtherPRODUCT FAMILY CLASSIFICATION GUIDE FOR: BEARINGSI). Please answer the following questions regarding this product line:1) Is the item a ball bearing, roller bearing or combined ball/roller bearing (circle one)?2) Who is the actual manufacturer of the item? _________________________________3) What is the country of manufacture of the item? ______________________________II). If the bearing is a ball bearing, answer the following:1) Does the bearing have an integral shaft (yes or no)?A)If it does have an integral shaft, is the outside diameter more or less (circle one) than 30 mm?2) If the ball bearing does not have an integral shaft, please indicate the specific type:a)___ Thrust bearingb)___ Linear bearingc)___ Angular contact bearingd)___ Radial bearing**see 3 & 4 belowe)___ Ball bearing other then above options3) If the ball bearing is a radial bearing, does it contain single or double (circle one) ball bearings?4) If the radial ball bearing is a single row bearing,a) Is it maximum or full capacity type?b) Please indicate outside diameter ______mmIII). If the bearing is a roller bearing, please indicate the specific type:a)___ Tapered roller bearing, with cup and cone assemblies entered as a setb)___ Tapered roller bearing, with cone assemblies entered separatelyc)___ Spherical roller bearing , single rowd)___ Spherical roller bearing, double or more rowse)___ Needle roller bearing , please indicate roller length ______mm & diameter _____mmf)___ Cylindrical roller bearingg)___ Roller bearings other than above optionsIV). If bearing is a combination ball/roller bearing, please indicate specific type:a)___ Combined ball and spherical roller bearingb)___ Combined ball and needle roller bearingc)___ Combined ball and cylindrical roller bearingd)___ Combined ball/roller bearing other than above optionsV). If the bearing is a plain shaft bearing is it in a housing (yes / no)?a) If housed, is it a rod end bearing (yes / no)?b) If not housed, is it spherical (yes / no)?If other than any of the above please describe, including such items as bushings , bearing housings for ball, roller or other (please specify), flange, take-up cartridge, & hanger units, or other (please specify) and housed bearings incorporating ball or roller bearings (please specify or describe below)____________________________________________________________________________________________________________________________________________________________Part or Item numbers this would apply to:__________________________________________________________________________________________ _____________________________________________________。

《航海英语》第八章翻译

（2349---2690）2349你船靠泊船首在码头并没有拖轮协助。

哪一根缆绳最有用当你操纵船舶靠泊时？首倒缆2350 你船装载不吸湿的货物自寒冷地区到温暖地区。

你应货舱不通风。

2351你船因为GM高度不足导致倾斜。

为降低G在M之下，你应在G下对称地增加重量。

2352 你船左倾4度且横摇周期短。

船壳内有自由流动灭火留下的水。

船舶首倾且首干舷1英尺。

你应最先采取什么措施？排出首尖舱的水2353 你船装载吸湿的货物自温暖地区开往寒冷地区。

哪一句是正确的？你必须连续且旺盛地通风以防止船体出汗2354你船的机舱在船中部并且货物集中装在船的首尾部。

船舶有拉伸主甲板的中拱。

2355 油船满载，并且你发现尾倾过大。

为调整吃水差，你可以转移燃油到船首部。

2356油船满载，并且你发现有轻微的首倾。

为调整吃水差，你可以转移货油到船尾部。

2357 你船装载危险货物。

在日常检查中，你注意到几个箱子的货物移位并开裂。

你首先应立即将情况报告船长并听候指示。

2358你最好把选港货装在二层舱的防堵舱位，这样无论在上海或大连都能够被轻易卸出。

2359你将在常温下装载散装硫磺。

哪一句是正确的？散装硫磺可以被符合所有适用规则而没有特别允许的船舶装载2360 你装运的货物中有一含有一类爆炸品的包裹。

包裹潮湿，发霉和污黑。

根据规则装运这个包裹你应联系托运人并建议撤回，修理或更换。

2361 你很可能移动重量自上二层舱到底舱。

这样一来，船舶将有更大的稳性高度。

2362 你已靠泊在周围有油船的码头。

什么信号表示船舶正在进行转移易燃或可燃液体货物？视野周围可见到一盏红灯2363 你有一定数量的袋装货物装载在三个甲板下二层舱。

哪一种堆装方式最稳定？分层换向堆码2364你们不能完成二舱的装货，能够吗?在肯定句中，用hardly，scarcely等词表示否定时，反意疑问句用肯定动词反问。

2365 在卸货其间，请求你安排必要的理货员在船上进行理货工作。

HYDRUS Model Use, Calibration, and Validation

Submitted for review in September 2011 as manuscript number SW 9401; approved for publication by the Soil & Water Division of ASABE in April 2012. The authors are Jiří Šimůnek, Professor and Hydrologist, Department of Environmental Sciences, University of California, Riverside, California; Martinus Th. van Genuchten, Professor, Department of Mechanical Engineering, Federal University of Rio de Janeiro, Brazil; and Miroslav Šejna, Director, PC-Progress s.r.o., Prague, Czech Republic. Corresponding author: Jiří Šimůnek, Department of Environmental Sciences, University of California-Riverside, Riverside, CA 92521; phone: 951-8277854; e-mail: Jiri.Simunek@.
HYDRUS: MODEL USE, CALIBRATION, AND VALIDATION
J. n, M. Šejna
ABSTRACT. The HYDRUS numerical models are widely used for simulating water flow and solute transport in variably saturated soils and groundwater. Applications involve a broad range of steady-state or transient water flow, solute transport, and/or heat transfer problems. They include both short-term, one-dimensional laboratory column flow or transport simulations, as well as more complex, long-duration, multi-dimensional field studies. The HYDRUS models can be used for both direct problems when the initial and boundary conditions for all involved processes and corresponding model parameters are known, as well as inverse problems when some of the parameters need to be calibrated or estimated from observed data. The approach to model calibration and validation may vary widely depending upon the complexity of the application. Model calibration and inverse parameter estimation can be carried out using a relatively simple, gradient-based, local optimization approach based on the Marquardt-Levenberg method, which is directly implemented into the HYDRUS codes, or more complex global optimization methods, including genetic algorithms, which need to be run separately from HYDRUS. In this article, we provide a brief overview of the HYDRUS codes, discuss which HYDRUS parameters can be estimated using internally built optimization routines and which type of experimental data can be used for this, and review various calibration approaches that have been used in the literature in combination with the HYDRUS codes. Keywords. Calibration, HYDRUS-1D, HYDRUS (2D/3D), Numerical model, Optimization methods, Parameter estimation, Solute transport, Unsaturated soils, Validation, Water flow.

船舶检验英语

目录名词部分船舶船舶与海上设施的种类………………………………………… P.3-5数据与资料……………………………………………………… P.6-8舱室处所………………………………………………………… P.8-11高级船员和船员………………………………………………… P.11-12船级……………………………………………………………… P.12-13 船体船体结构………………………………………………………. P.13-23舾装……………………………………………………………. P.23-26甲板机械………………………………………………………. P.26-28 轮机1．操舵装置………………………………………………………. P.282．锅炉与受压容器………………………………………………. P.28-313．汽轮机和燃气轮机……………………………………………. P.31-324．柴油机…………………………………………………………. P.32-365．轴、轴承以及螺旋浆…………………………………………. P.36-396．泵、阀、柜、管和舱底附件…………………………………. P.39-437．齿轮箱及其它装置……………………………………………. P.43-48 电气电力推进装置及配套设备和辅助电气设备………………….. P.48-50无线电设备……………………………………………………. P.50-52发电机与电动机………………………………………………. P.52-53配电系统………………………………………………………. P.53-56变流机、变压器等装置以及开关等………………………….. P.56-62电缆与照明系统……………………………………………….. P.62-67报警系统和信号设备………………………………………….. P.67-68 消防……………………………………………………………… P.68-69救生设备………………………………………………………… P.69-71焊接……………………………………………………………… P.71-72动词部分船舶处于或遭遇的状态或情况…………………………………. P.72-85缺陷与损坏的类别与原因……………………………………… P.85-103修理方法………………………………………………………. P.103-107检查与试验……………………………………………………. P.107-109短语句子部分短语（1-133）……………………………………………….. P.110-119句子（134-443）有关船舶以及证书报告等方面的叙述…………………… P.119-123有关各种原因、目的、条件等的叙述…………………… P.123-134有关船舶及船、机、电等状况的叙述…………………… P.134-148有关检查、试验与修理等情况的叙述…………………… P.148-156报告部分全况检验……………………………………………………………….P.156-164制造中缺陷…………………………………………………………….P.164-176火灾事故……………………………………………………………….P.176-178遭遇坏天气…………………………………………………………….P.178-182遭遇大雾……………………………………………………………….P.182-183碰撞损坏（螺旋浆被灯船锚链缠绕继而发生碰撞）……………….. P.183-190 碰撞损坏（机动货驳碰撞后沉没，已无修理价值）……………….. P.190-193 碰撞损坏（渔船船首被碰撞）……………………………………….. P.193-196 搁浅损坏……………………………………………………………….P.197-202腐蚀…………………………………………………………………….P.202-206进水损坏……………………………………………………………….P.206-209锚损坏………………………………………………………………….P.209-210货舱损坏……………………………………………………………….P.210-216舱盖损坏……………………………………………………………….P.216-218浪击损坏……………………………………………………………….P.219-220浪损…………………………………………………………………….P.220-223螺旋浆损坏…………………………………………………………….P.223-229可调节螺旋浆轴联轴器安装缺陷……………………………………..P.229-230主机损坏（连杆轴承下盖的潜在缺陷所致）……………………….. P.231-235主机损坏（推力轴承没有起到止推作用曲轴前移所致）……………P.235-244 主机损坏（主机飞车曲轴后臂红套移动所致）………………………P.244-249 主机损坏（缸套裂缝所致）………………………………………….. P.249-250 付机损坏（柴油发电机爆炸，已无修理价值）………………………P.250-253 付机损坏（活塞、缸套长期在高热应力中运转而产生裂缝所致）…P.253-255 缸套、活塞损坏………………………………………………………...P.255-256 增压器损坏……………………………………………………………. P.256-258尾轴油封装置渗漏……………………………………………………. P.258-261离合器损坏……………………………………………………………. P.261-262起重机损坏……………………………………………………………. P.262-263门式起重机损坏………………………………………………………. P.263-266履带式起重机回转支索损坏…………………………………………. P.266-267垃圾箱损坏……………………………………………………………. P.267-269码头损坏………………………………………………………………..P.269-270钻井平台远洋拖航……………………………………………………. P.270-272一．名词部分船舶1．船舶与海上设施的类型Type of Ships and Offshore Installations 货船Cargo Ship杂货船General cargo ship干货船Dry cargo ship散货船Bulk carrier矿沙船Ore carrier运煤船Coal carrier集装箱船Container ship滚装货船Ro/Ro ship冷藏船Refrigerated ship运畜船Cattle carrier运木船Timber carrier近海供应船Offshore supply ship散装矿砂船Bulk Ore carrier混装船Combination carrier载驳母船Barge Carrier汽车运输船Car carrier液货船Liquid Cargo Carrier油船Oil tanker化学品液货船Chemical tanker液化气体船Liquefied gas carrier油矿两用船Oil/ore carrier油散两用船Oil/bulk carrier油散矿三用船Oil/bulk/ore carrier客船Passenger Ship客船Passenger ship豪华旅游客船Cruise ship旅游船Tourist ship高速客船High speed passenger craft 双体客船Passenger catamaran客货船Passenger-cargo ship客箱船Passenger container ship客滚船Ro/Ro Passenger Ship高速船High Speed Craft全垫升气垫船Air-cushion Vehicle水面效应船Surface Effect Ship双体气垫船Air-cushion Catamaran侧壁气垫船Side-wall Hovercraft高速双体船High Speed Catamaran高速单体船High Speed Monohull Craft地效翼船Wing-in Ground Craft水翼船Hydrofoil Craft动力支承船Dynamically Supported Craft两栖船Amphibious Craft小水面单体船Small Waterplane Area Single Hull Ship 小水面双体船Small Waterplane Area Twin Hull Ship 驳船Barge客驳Passenger Barge货驳Cargo Barge敞口驳Open Barge甲板驳Deck Barge集装箱驳Container Barge分节驳Integrated Barge开底驳Hopper Barge油驳Oil Barge趸船（箱形驳）Pontoon拖船Tug港作拖船Harbour Tug打捞拖船Salvage Tug顶推船Pusher近海供应拖船Offshore tug/supply ship工程船Engineering Ship挖泥船Dredger耙吸式挖泥船Trailing suction dredger绞吸式挖泥船Cutter suction dredger链斗式挖泥船Bucket dredger抓斗式挖泥船Grab dredger铲斗式挖泥船Dipper dredger吹泥船Reclamation craft开底泥驳Hopper Barge对开泥驳Split Hopper Barge起重船Floating Crane浮船坞Floating Dock打桩船Floating Pile Driver布缆船Cable Layer潜水工作船Diving Boat港区工作船Harbour Operating Ship破冰船Ice breaker消防船Fire Boat救护船/救助船Rescue Ship引水船Pilot Vessel海关船Customs Boat巡逻船Patrol Boat布标船Buoy Layer灯标船Beacon Boat交通艇Traffic Boat垃圾船Garbage Boat浮油回收船Oil Recovery Ship污水处理船Sewage Disposal Vessel海水淡化船Distilling Ship渡船Ferry乘客渡船Passenger Ferry火车渡船Train Ferry车客渡船Vehicle Passenger Ferry海峡渡船Channel Ferry渔船Fishing Vessel渔品加工船Fish-Factory Ship拖网渔船Trawler围网渔船Netter捕鲸船Whaling Ship活鱼运输船Live Fish Carrier其他船舶科学调查船Research ship训练船Training Ship特殊用途船Special purpose ship内河船Inland Waterways Ship海上设施Offshore Installations海上移动平台Mobile Offshore Unit海上移动钻井平台Mobile Offshore Drilling Unit水面式平台Surface Unit船式平台Ship-type Unit驳船平台Barge-type Unit自升式平台Self-elevating Unit柱稳式平台Column-stabilized Unit半潜式平台Semi-submersible Unit坐底式平台Submersible Unit采油平台Production Unit储油平台Storage Unit生活平台Accommodation Unit修理平台Repair Unit海上固定平台Fixed Offshore Platform海底管道Submarine Pipeline潜水系统和潜水器Diving System and Submersible单点系泊Single Point Mooring (SPM)浮式生产与储油装置Floating Production and Storage Unit(FSUs)浮式生产、储存及卸载系统Floating Production, Storage andOffloading System (FPSOs) 2．数据与资料Data and Information数据总长Length overall(L OA)垂线间长Length bet. perpendiculars (L BP)首、尾垂线Forward and after perpendiculars型宽Moulded breadth型深Moulded depth建造日期Date of build签订建造合同日期Date of building contract龙骨安放日期Date of keel laid交船日期Date of delivery下水日期Launching date重大改建Major conversion安放龙骨或船舶处于相似建造阶段的日期Date on which keel was laid or ship was at a similar stage of construction 签订改建合同日期Date of conversion contract改建完工日期Date of completion of conversion船舶所有人Owner经营人Operator承租人Charterer船舶编号或呼号Distinctive number or letters航行区域Navigation area/Service area/Trade area曾用过的船名Former Name姐妹船Sister Ship总吨位Gross tonnage净吨位Net tonnage排水量Displacement载货量Cargo weight载重量Deadweight空船重量Light(-ship) weight吃水(首、尾、平均) Draft ( fwd, aft, mean)稳性Stability完整稳性Intact stability破舱稳性Damaged stability分舱（抗沉性）Subdivision初稳性高度Metacentric height衡准数Criterion numeral剖面模数Section modulus惯性矩Moment of inertia纵总强度Longitudinal strength局部强度Local strength方形系数Block coefficient静水弯矩Still water bending moment重心垂直高度Vertical height of centre of gravity屈服应力Yield stress标准舷弧Standard sheer防火分隔Fire division航区限制Navigation area restriction海况限制Sea state restriction天气限制Weather restriction最大抗风暴能力Max. weatherliness储备浮力Reserve buoyancy续航力Endurance渗透率Permeability盲区Blind area共振区域Resonance region容许载荷Permissible load核定载客数Number of persons certified to carry 干舷：Freeboard热带干舷Tropical freeboard夏季干舷Summer freeboard冬季干舷Winter freeboard北大西洋冬季干舷Winter North Atlantic freeboard热带木材干舷Timber tropical夏季木材干舷Timber summer冬季木材干舷Timber winter北大西洋冬季木材干舷Timber winter North Atlantic freeboard 淡水宽限Allowance for fresh water减少干舷的B型船舶Type B with reduced freeboard增加干舷的B型船舶Type B with increased freeboard载重线：Load line载重线标志Loadline marks资料防火控制图Fire control plans海图( up-to-date最新) Charts航路指南Sailing direction灯塔表Lists of lights航行通告Notices to mariners潮汐表Tide tables航海出版物Nautical publications应变部署表Muster list国际信号规则International Code of Signals航海日志Deck log book机舱日志Engine room log book无线电日志Radio log book线型图Lines稳性资料Stability information装载手册Loading manual干舷计算书Freeboard calculations配载图Stowage plan操作说明书Operation instructions维修计划Maintenance plan训练手册Training manual船上维修保养指南Instructions for on-board maintenance 弃船训练演习手册Abandon ship training and drill manual3．舱室处所Compartments or Spaces舱室工作和设备舱室：驾驶室wheel house海图室chart room报务室radio room雷达室radar room声纳室sonar room主机舱main engine room主机操纵室main engine control room辅机舱auxiliary engine room锅炉舱boiler room机炉舱engine and boiler room减速器舱reduction gear room舵机舱steering gear room通风机室fan room变流机室commutator room空调室air-conditioner room应急发电机室emergency generator room冷冻机室refrigerator room灭火装置室fire control room蓄电池室battery room陀螺罗经室gyro-compass room方位水平仪室azimuth level room计程仪舱log room导弹舱missile room弹药舱magazine深弹舱depth charge room弹药转运舱ammunition lobby声纳舱sonacelle, sonar nacelle机修间workshop电工间electrician’s store木工间carpente r’s store锚链舱chain locker桅屋mast house洗消室decontamination room居住舱室：居住舱室Accommodation, living accommodation 客舱Cabin船员舱室crew’s cabin墙壁wall天花板top ceiling侧壁板side ceiling里子板lining装饰decoration家具furniture书桌desk衣橱wardrobe梳妆台dressing table书柜bureaux餐具柜dresser椅子chair沙发sofa桌子table帷幔drapery窗帘curtain地毯carpet货舱：货舱cargo hold（详见船体部分的货舱）货油舱cargo oil tank, cargo tank集装箱舱container hold冷藏货舱refrigerated cargo hold液化天燃气舱liquefied natural gas tank邮件舱mail room行李舱luggage room汽车舱vehicle hold液舱liquid tank燃油舱fuel oil tank滑油舱lubricating oil tank压载水舱ballast tank淡水舱fresh water tank污水舱bilge tank储藏室store, store room帆缆间hawser store油漆间paint room粮食库provision store冷藏库refrigerating chamber其他：首尖舱fore peak tank尾尖舱aft peak tank顶边舱：topside tank甲板强横梁deck transversevertical side plating ( in line with hatch) 舱口垂向列板（与舱口一直线的垂直边板）船壳板shell plating斜板sloping plating底边舱：hopper tank斜板sloping plating双层底舱double bottom tank翼舱wing tank边舱side tank平衡舱heeling tank深舱deep tank残油舱sludge/oil residue tank隔离舱cofferdam空舱void tank处所货物处所：Cargo spaces货舱Cargo hold货油舱Cargo tank液货舱Liquid cargo tank围壁通道Trunk起居处所：Accommodation spaces公共处所Public space走廊Corridor盥洗室Lavatory住所Cabin办公室Office医务室Hospital放映室Cinema游戏室Game room娱乐室Hobby room理发室Barber shop配膳室(无烹调设备) Pantry(containing no cooking appliances) 公共处所：Public spaces:大厅Hall餐室Dining room休息室Lounge类似的固定围闭处所Similar permanently enclosed spaces 服务处所：Service spaces：厨房Galley配膳室(设有烹调设备的) Pantry (containing cooking appliances) 储物间Locker邮件舱Mail room贵重物品室Specie room储藏室Store room工作间Workshop围壁通道Trunk特种处所：Special category spaces：舱壁甲板以上或以下围闭的车辆处所Enclosed vehicle spaces above and below the bulkhead deck机器处所：Machinery spaces：A类机器处所Machinery space of category A装有下列机械的处所推进机械；锅炉；燃油装置；蒸汽机和内燃机；发电机和主要电动机；加油站；冷藏机；防摇装置；通风机；空气调节机械。

适用于轴承故障诊断的数据增强算法

2021577轴承故障诊断在制造业的故障预测和健康管理中起着十分重要的作用。

除了传统的故障诊断方法以外，学者们将改进过的机器学习[1-4]和深度学习算法[5-8]应用于故障诊断领域，其诊断效率与准确率得到了较大的提高。

在大部分应用中，这些算法有两个共同点[9]：第一、根据经验风险最小化原则（Empirical Risk Minimization，ERM）[10]训练故障诊断模型。

第二、使用此原则训练的诊断模型的性能优劣主要取决于所使用的训练样本的数量和质量。

但在工业应用中，数据集中正负样本的比例不平衡：故障数据包含着区分类别的有用信息，但是所占比例较少。

此外由于机器的载荷、转轴转速等工况的不同，所记录的数据并不服从ERM原则中的独立同分布假设。

这两点使得ERM原则不适用于训练工业实际场景中的故障诊断模型，并且文献[11]表明使用ERM原则训练的模型无法拥有较好的泛化性能。

数据增强算法是邻域风险最小化原则[12]（Vicinal Risk Minimization，VRM）的实现方式之一，能够缓解ERM原则所带来的问题。

在VRM中通过先验知识来构建每个训练样本周围的领域区域，然后可从训练样本的领域分布中获取额外的模拟样本来扩充数据集。

例如，对于图像分类来说，通过将一个图片的领域定义为其经过平移、旋转、翻转、裁剪等变化之后的集合。

但与机器学习/深度学习中的数据不同，故障诊断中的数据（例如轴承故障诊断中的振动信号）具有明显的物理意义和机理特征，适用于机器视觉的数据增强方法可能导致物理意义的改变。

因此，本文从信号处理和信号分析的角度出发，设计了一种适用于轴承故障诊断中振动信号的数据增强方法。

适用于轴承故障诊断的数据增强算法林荣来，汤冰影，陈明同济大学机械与能源工程学院，上海201804摘要：针对在轴承故障诊断中存在的故障数据较少、数据所属工况较多的问题，提出了一种基于阶次跟踪的数据增强算法。

该算法利用阶次跟踪中的角域不变性，对原始振动信号进行时域重采样从而生成模拟信号，随后重新计算信号的幅值来抵消时域重采样以及环境噪声对原始信号能量的影响，最后使用随机零填充来保证信号在变化过程中采样长度不变。

某隧道主体结构内力计算及配筋设计

交通与土木工程河南科技Henan Science and Technology总第872期第1期2024年1月某隧道主体结构内力计算及配筋设计孙建波1 李登寿1 史金录1 刘渊2 徐大桥2（1.中信建设有限责任公司，北京 100027；2.中国市政工程中南设计研究总院有限公司，湖北武汉 430000）摘要：【目的】为完成隧道衬砌结构设计，需要对隧道围岩压力和隧道主体结构内力进行计算。

根据隧道受力特点进行合理的计算假定。

【方法】基于国道321线，采用SAP84软件对最不利断面的不同工况进行设计计算和模型分析并进行验证。

【结果】结果表明，此隧道主体结构在三种最不利断面的工况下，配筋内力计算结果和验证情况均符合规范要求。

【结论】该项目配筋设计时在正常使用状态下的计算结果，结合承载能力极限状态下的计算结果进行验证，能够快速有效地确定最终配筋结果，为配筋提供了理论依据，为今后隧道衬砌结构设计提供参考。

关键词：隧道结构设计；结构内力计算；SAP84；配筋设计中图分类号：U455.43 文献标志码：A 文章编号：1003-5168（2024）01-0061-06DOI ：10.19968/ki.hnkj.1003-5168.2024.01.012Structural Internal Force Calculation and Reinforcement Design of theMain Structure of a TunnelSUN Jianbo 1 LI Dengshou 1 SHI Jinlu 1 LIU Yuan 2 XU Daqiao 2（1. CITIC Construction Co., Ltd., Beijing 100027,China;2. China Central and South Municipal Engineering Design and Research Institute Co., Ltd., Wuhan 430000,China ）Abstract: [Purposes ] To complete the design of tunnel lining structure, it is necessary to calculate thepressure of tunnel surrounding rock and the internal force of the main structure of the tunnel. Reasonablecalculation assumptions should be made based on the stress characteristics of the tunnel. [Methods ] Based on the national highway 321, this paper used SAP84 software to conduct design calculation, model analysis, and results verification in three different working conditions of the most unfavorable section.[Findings ] The results indicate that the calculation results and verification results of the reinforcement internal force of the main structure of this tunnel meet the requirements of the specifications under the three most unfavorable cross-sectional conditions.[Conclusions ] The calculation results of the rein⁃forcement design of the project in the normal use state are verified by the calculation results of the bearing capacity limit state, which can quickly and effectively determine the final reinforcement re⁃sults and provide a theoretical basis for the reinforcement and a reference for the design of tunnel lin⁃ing structure in the future.Keywords: tunnel structure design; structural internal force calculation; SAP84; reinforcement design收稿日期：2023-06-29作者简介：孙建波（1982—），男，硕士，工程师，研究方向：建筑与市政施工技术。

轴承故障特征分析

• Lubrication and how it works • Maintenance Practices / Operating Environments • Bearing number system • How should a bearing look after operating over a period of time • Damage and wear patterns of the components. Photos and Hands on.
– Disassembly / Cleaning / Writing a report • Data collection and writing understandable reports for machine tracking • Corrective Action Discussion. • Review Test: Question and Answer • Wrap up.
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Failure Analysis Agenda
DAY 2
• Tour the SKF/FEI Facility (Industrial Service Center) • Review bearing conditions seen on Day 1. More Hands-on • Any questions after seeing these conditions • Have you seen any of these conditions on your applications • Discuss and learn how to read a bearing failure backwards to find the cause • Workshop, tools and “how to” disassemble bearings for analysis • Where to and Where not to “cut” a bearing to preserve evidence • Know what dismounting damage looks like compared to mounting damage • How to LOOK at a lubrication to help find the cause of a failure • Do a analysis on your own bearing. A “Team” effort.

基于遗传算法的滚动轴承的多目标优化设计翻译.

Multi-objective design optimisation of rolling bearings using genetic algorithms 基于遗传算法的滚动轴承的多目标优化设计Shantanu Guptaa Rajiv Tiwari b, and Shivashankar B. Nair a,aDepartment of Computer Science and Engineering计算机科学与工程系Indian Institute of Technology Guwahati, 印度理工学院GuwahatiGuwahati 781039, Assam, India 印度阿萨姆邦，781039，GuwahatibDepartment of Mechanical Engineering 机械工程系Indian Institute of Technology Guwahati, 印度理工学院GuwahatiGuwahati 781039, Assam, India 印度阿萨姆邦，781039，GuwahatiReceived 8 March 2006; revised 6 September 2006; accepted 2 October 2006. Available online 28 December 2006.Abstract 摘要The design of rolling bearings has to satisfy various constraints, e.g. the geometrical,kinematics and the strength, while delivering excellent performance, long life and high reliability.This invokes the need of an optimal design methodology to achieve these objectives collectively, i.e. the multi-objective optimisation.In this paper, three primary objectives fora rolling bearing, namely, the dynamic capacity (C d), the static capacity (C s) and the elastohydrodynamic minimum film thickness (H min) have been optimized separately, pair-wise and simultaneously using an advanced multi-objective optimisation algorithm: NSGA II(non-dominated sorting based genetic algorithm). These multiple objectives are performance measures of a rolling bearing, compete among themselves giving us a trade-off region where theydesign become “simultaneously optimal”, i.e. Pareto optimal. A sensitivity analysis of various parameters has been performed, to see changes in bearing performance parameters, and results show that, except the inner groove curvature radius, no other design parameters have adverse affect on performance parameters.滚动轴承的设计，要满足各种制约因素，如几何、运动学和强度，同时还要提供优异的性能、长寿命和高可靠性。

香港科技大学土工离心机先进模拟技术在岩土工程中的应用_英文_

CLC number: TU41
1 Introduction In tackling some complex geotechnical problems, centrifuge modelling is often considered as a preferred experimental method. According to a survey conducted by the British Geotechnical Society in 1999, centrifuge modelling was ranked fifth in the list of the most important developments in geotechnics over the previous 50 years (Fig. 1). The ranking was based on responses from 68 geotechnical experts in academia, consulting, contracting and research organisations. It is clear from the survey that centrifuge modelling plays a key role in geotechnical engineering. In this paper, the kinematics, fundamental prin§ *
This ZENG Guo-xi Lecture (4th) was delivered on Nov. 27th, 2010 Project supported by the Program for Changjiang Scholars and the Innovative Research Team in the University of Ministry of Education of China (No. IRT1125), and the 111 Project (No. B13024), China © Zhejiang University and Springer-Verlag Berlin Heidelberg 2014

测量深沟球轴承径向游隙的补偿问题

测量深沟球轴承径向游隙的补偿问题英文回答：Measuring Radial Clearance in Deep Groove Ball Bearings.Radial clearance is the amount of play between theinner and outer rings of a deep groove ball bearing. It is an important factor in determining the bearing's load capacity, speed capability, and noise level.There are two main methods for measuring radial clearance in deep groove ball bearings:Dial indicator method: This method uses a dialindicator to measure the movement of the outer ringrelative to the inner ring. The bearing is mounted on ashaft and the dial indicator is placed against the outer ring. The shaft is then rotated and the dial indicator is used to measure the amount of movement.Feeler gauge method: This method uses a feeler gauge to measure the gap between the inner and outer rings. The bearing is mounted on a shaft and the feeler gauge is inserted between the inner and outer rings. The feeler gauge is then used to measure the thickness of the gap.The radial clearance of a deep groove ball bearing is typically measured in thousandths of an inch (mils). The ideal radial clearance for a particular bearing will depend on the application. In general, a smaller radial clearance will result in a higher load capacity and a lower speed capability. A larger radial clearance will result in a lower load capacity and a higher speed capability.It is important to note that the radial clearance of a deep groove ball bearing can change over time. This can be caused by wear, contamination, or other factors. If the radial clearance becomes too large, the bearing may become noisy or fail prematurely.中文回答：深沟球轴承径向游隙的测量方法。

Postech P238 螺旋桩技术规格书说明书

NORMATIVEINFORMATIONMANUFACTURER:Pieux Vistech - Postech Screw Piles10260, Bourque boulevardSherbrooke QC J1N 0G2Tel. : 819.843.3003Toll free: 1.866.277.4389Fax. : 819.868.0793Rev. 05-2020PRODUCT CHARACTERISTICSPhysical and Chemical propertiesSTEEL GRADE Conform to CAN/CSA G40.21-350W and/or ASTM A500 class CARC WELDING Conform to CSA W59-18HOT DIP GALVANIZATION Conform to ASTM-A123MTHERMAL INSULATION Unique polyurethane foamStandard characteristicsTUBING DIAMETER60 mm (2 3/8 in)BLADE DIAMETER From 200 to 405 mm (8 in and 16 in)TUBING LENGTH Standard of 2.1 m and 3 m (7 ft. and 10 ft.)TUBING THICKNESS 3.9 mm (0.154 in)BLADE THICKNESS8 mm (5/16 in) for diameters from 200 to 300 mm (8 to 12 in)9.5 mm (3/8 in) for diameter of 355 mm (14 in)12.7 mm (1/2 in) for diameter of 405 mm (16 in)ADAPTER HEADS Various forms as needed according to the project specificationsEXTENSIONS Available according to project specifications120 kN(1) (27 000 lb.)BENDING MOMENT OF TUBING 2.5 kN.m (1845 lb. ft)4650 N.m (3400 lb. ft)SLS = Service Limit StateDESIGN INFORMATIONIn all cases, please refer to the CCMC 13102-R Assessment Report. All applicable loads must bevalidated by an engineer licensed to practice under the appropriate provincial or territorial legislation.BEARING CAPACITYPostech products are designed to bear compressive, tension and lateral loads through the bladeat the bottom of the shaft. The design of the shaft and the size of the blade depend on the loadand on the bearing capacity of the soil. The monitoring of the applied torque on site allows for theconfirmation of the allowable bearing capacity (SLS) of the soil. All capacities listed on this datasheet must be applied at the pile head less than 0.3 m (1 ft) above ground.THERMAL INSULATIONPostech products are insulated by a process of injecting polyurethane foam in the piles shaft. Therevolutionary insulation system ensures that the inside of the pile is maintained at a temperaturethat will prevent ice or frost build-up at the base of the pile; providing optimal protection againstground motion using our planet’s heat.SCREW PILE ADVANTAGES• Product and installation is supplied, you only need to mark the spot!• Can be installed in all climates, weather or ground conditions;• No excavation usually required, minimal impact to your property;• No waiting time, you can build as soon as the installation is ready;• Reusable and recyclable, environmentally friendly;• Can be installed under an existing structure;• The most reliable & economical solution available.(1) The maximum support value is applicable to steel tube only. The resistance is conditional on the composition of the on-site soil (granularand / or cohesive) and that the pile must be supported laterally. In all cases, the mechanical capacity of the steel tube must be certified by anauthorized engineer. (Not applicable in the presence of liquefiable or loose soils, water, air, peat bogs, etc.)NORMATIVEINFORMATIONMANUFACTURER:Pieux Vistech - Postech Screw Piles10260, Bourque boulevardSherbrooke QC J1N 0G2Tel. : 819.843.3003Toll free: 1.866.277.4389Fax. : 819.868.0793Rev. 05-2020APPLIED TORQUES(LB-FT)ALLOWABLE LOADS (kN)(kN)(Lb)(kN)(Lb)50020 4 500490075024 5 4008 1 8001 00029 6 525112 4751 250347 65014 3 1501 500398 77518 4 0501 750449 90021 4 7252 0004911 02525 5 6252 2505311 92531 6 9752 5005813 05031 6 9752 7506314 175357 8753 0006815 300409 0003 2507316 425449 9003 5007817 5504810 800COHESIONLESS SOILS(SIL T, SAND OR GRAVEL)• For cohesionless soils, the safety factor varies from 2.0 to 3.0 in compressive loads and from 2.0 to 2.4 intensile loads.• The safety factor for the lateral loads varies from 2.0 to 6.4, for cohesionless and cohesive soils.• If there are any boulders (> 200 mm in diameter) in the granular matrix, the above mentioned capacities willbe overstated. In this case, the allowable loads will be established on-site using a confirmatory test.SOIL DENSITIESALLOWABLE LATERAL LOADS (2)(kN)(Lb)18 1.636020 1.738022 1.9425SLS = Service Limit State(2) Lateral loads are applicable at the pile head, less than 0.3 m (1 ft) above ground, and the pile must be supported laterally by theground. However, lateral loads do not apply in the presence of liqueﬁ able or loose soils, water, air and peatlands. The lateral capacity of apile must always be certiﬁ ed by an engineer licensed to practice under the appropriate provincial or territorial legislation.NORMATIVEINFORMATIONMANUFACTURER:Pieux Vistech - Postech Screw Piles10260, Bourque boulevardSherbrooke QC J1N 0G2Tel. : 819.843.3003Toll free: 1.866.277.4389Fax. : 819.868.0793Rev. 05-2020CompactionindexesNAllowablebearingcapacitiesof soils(kPa)*ALLOWABLE LOADS (kN)35043648611815115756410714101914251861007512916122317302281251071611221630223929101501292014272038284936111751310211630224230544013200161125193526493664471625019143123433260442030024183929544076≥25≥ 3503022493668Undrainedshearstrengths(kPa)Allowablebearingcapacities ofsoils(kPa)*ALLOWABLE LOADS (kN)3050548511715920124475751181610221429175810097151021132918382373125129191326173722298815014102315322027102175161227183723117200191430202714525023173825≥175≥3002821ALLOWABLE LOADS VALUESOF POSTECH SCREW PILESThe geotechnical calculations for Postech’s screw piles were carried out in accordance with therequirements of sub-section 4.2.4 of National Building Code (NBC). We used the design methodsset out in Chapters 19 and 20 of the Canadian Foundation Engineering Manual (CFEM). Thesecalculations are based on the physical and mechanical properties of the on-site at the blade depthand along the steel tubing.SLS = Service Limit State* Note: For a conventional strip footing with a width of less than 1 m.NORMATIVEINFORMATIONMANUFACTURER:Pieux Vistech - Postech Screw Piles10260, Bourque boulevardSherbrooke QC J1N 0G2Tel. : 819.843.3003Toll free: 1.866.277.4389Fax. : 819.868.0793Rev. 05-2020APPLIED TORQUES(LB-FT)ALLOWABLE LOADS(kN)(Lb)(kN)(Lb)7508 1 8006 1 3501 000112 4758 1 8001 25014 3 150102 2501 50017 3 82512 2 7001 75019 4 27514 3 1502 00022 4 950163 6002 25025 5 62519 4 2752 50028 6 30021 4 7252 75031 6 97523 5 1753 000337 42525 5 6253 250368 10027 6 0753 500398 77529 6 525COHESIVE SOILS(CLAY)• For cohesive soils, the safety factor varies from 2.0 to 2.9 in compressive and in tensile loads.• The safety factor for the lateral loads varies from 2.0 to 6.4, for cohesionless and cohesive soils.• If there are any boulders (> 200 mm in diameter ) in the granular matrix, the above mentioned capacitieswill be overstated. In this case, the allowable loads will have to be established on-site using a confirmatorytest.SOIL DENSITY ALLOWABLE LATERAL LOAD (2)(kN)(Lb)16 1.4315SLS = Service Limit State(2) Lateral loads are applicable at the pile head, less than 0.3 m (1 ft) above ground, and the pile must be supported laterally by theground. However, lateral loads do not apply in the presence of liqueﬁ able or loose soils, water, air and peatlands. The lateral capacity of apile must always be certiﬁ ed by an engineer licensed to practice under the appropriate provincial or territorial legislation.。

Twin City Fan 风扇产品说明书

All fans have bearings and proper lubrication of the bearings helps ensure maximum life. Direct drive and belt driven fans have bearings in the motors. For motor lubrication requirements, please follow the manufacturer’s recommendation. This document is intended as a quick reference to address the general bearing maintenance requirements of drive bearings on belt driven fans.All Twin City Fan fans are equipped with decals indicating relubrication intervals for normal operating conditions. (See the tables on the following page for typical lubrication data.) However, every installation is different and the frequency of relubrication should be adjusted accordingly. On high moisture applications, the lubrication frequency may need to be doubled or tripled to adequately protect the bearings. Double the relubrication frequency on fans with vertical shafts. Observation of the conditions of the grease expelled from the bearings atthe time of relubrication is the best guide as to whether theBearing Maintenance Guideregreasing intervals and the amount of grease added should be altered. Greases are made with different bases. There are synthetic base greases, lithium base, sodium base, etc. Avoid mixing greases with different bases, because they could be incompatible and result in rapid deterioration or breakdown of the grease. The lubrication sticker identifies a list of acceptable lubricants for bearings with lithium-based grease. Most bearings are filled with a lithium-based grease before leaving the factory, unless another grease was requested. When the fans are started, the bearings may discharge excess grease through the seals for a short period of time. Do not replace the initial discharge because leakage will cease when the excess grease has worked out. Sometimes the bearings tend to run hotter during this period. There is no reason for alarm unless it lasts over 48 hours or gets very hot (over 200°F). When relubricating, use enough grease to purge the seals. Rotate bearings by hand during relubrication.BEARING LIFEUnder laboratory conditions with controlled loads and proper lubrication, bearings fail due to fatigue. Bearing life is a statistical calculation of when a percentage of a population of bearings will fail based on bearing geometry, bearing load and speed. All bearings have a finite life and will eventually fail.L-10 LIFEA statistical estimate of hours that 10% of a population of bearings at a given speed and loading condition will fail.L-50 LIFE OR AVERAGE LIFE- Occasionally, the term “average life” or L-50 is used. A statistical estimate of hours 50% of a population of bearings at a given speed and loading condition will fail.- It is calculated by multiplying the L-10 life by five. For example, a bearing with an L-10 life of 40,000 hours has an L-50 life of 200,000 hours.BEARING LIFE STANDARDS(The examples below depict life in years based on these calculations.)- Most Twin City Fan fan models offer a bearing life of L-10–40,000 hours.- Some models are offered at L-10–20,000, L-10–40,000, L-10–60,000, L-10–80,000 and L-10–100,000 hours.-See the product catalogs for the bearing life specifications by model.Bearing Life OverviewTWIN CITY FAN & BLOWER | WWW.TCF .COM5959 Trenton Lane N | Minneapolis, MN 55442 | Phone: 763-551-7600 | Fax: 763-551-7601©2022 Twin City Fan Companies, Ltd.Safety & Bearing Lubrication InstructionsIf you have additional questions, please contact your local Twin City Fan sales representative. To find your local sales representative, please visit .。

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端面承压英语

端面承压英语End face bearing, a concept often overlooked in mechanical engineering, plays a crucial role in ensuring the stability and longevity of various structures.This type of bearing is essential for applications where axial loads are present, and it distributes the load evenly across the end faces of the components, preventing deformation and wear.In the realm of construction, end face bearings are vital in supporting large columns and beams, ensuring that the weight is managed efficiently and the structural integrity is maintained.The design of end face bearings must consider factors such as material properties, load capacity, and environmental conditions to guarantee optimal performance and durability.Proper installation and maintenance of these bearings are also critical, as misalignment or neglect can lead to premature failure and potential safety hazards.In the context of machinery, end face bearings are often used in conjunction with other types of bearings to provide a comprehensive support system, enhancing the overallefficiency and reliability of the equipment.For engineers and designers, understanding the principles of end face bearing is fundamental to creating robust and long-lasting designs that can withstand the test of time.In conclusion, while end face bearings may not always be the central focus in engineering projects, their contribution to the overall stability and performance of systems cannot be underestimated.。

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Maintenance scheduling and production control of multiple-machine manufacturing systems Original Research ArticleComputers & Industrial EngineeringInformation requirements for e-maintenance strategic planning: A benchmark study in complex production systems Original Research ArticleComputers in IndustryStructure property correlation study of a service exposed first stage turbine blade in a power plant Original Research ArticleMaterials Science and Engineering: Aproduction quantity model for randomly failing production process with minimal repair and imperfect maintenance Original Research ArticleInternational Journal of Production EconomicsThis study applies periodic preventive maintenance (PM) to economic production quantity (EPQ) model for a randomly failing production process having a deteriorating production system with increasing hazard rate: minimal repaired and reworked upon failure (out of control state). The minimal repair performs restorations and returns the system to an operating state (in-control state). It is assumed that, after each PM, two types of PM are performed, namely imperfect PM and perfect PM. The probability that PM is perfect depends on the number of imperfect maintenance operations performed since the last renewal cycle. Mathematical formulas for the expected total cost are obtained. For the EPQ model, the optimum run time, required to minimize the total cost, is discussed. Various special cases are considered, including the maintenance learning effect. Finally, a numerical example is presented to illustrate the effect of PM and setup, breakdown and holding cost.Article Outline1. Introduction2. General model3. Special cases3.1. Case 1:;(j=1,2,…)3.2. Case 2:; (j=1,2,…), 0≤q<1,3.3. Case 3:; ; (j=1,2,…), 0<r<13.4. Case 4:;(j=1,2,…),0≤q<1,α>03.5. Case 5:;,(j=1,2,…)3.6. Case 6: C r→0; C m→03.7. Case 7: C h→04. Example and analysis5. Concluding remarksAcknowledgementsAppendix AReferencesproduction, maintenance and lockout/tagout control policies in manufacturing systems Original Research ArticleInternational Journal of Production Economicsintelligent maintenance system for continuous cost-based prioritisation of maintenance activities Original Research ArticleComputers in Industrymodel for the characterization of friction contacts in turbine blades Original Research ArticleJournal of Sound and Vibrationmodelling of anisotropic creep deformation in single crystal blade alloys SRR99 and CMSX-4Original Research ArticleInternational Journal of PlasticityMaterial property as an opened or closed system? Practical view on the aircraft components failures in GCF area Original Research ArticleInternational Journal of Fatiguesystem reliability in multi-factory production networks by maintenance approach Original Research ArticleExpert Systems with ApplicationsMaintaining the reliability of a system is one of the most critical and challenging tasks for factories during production. A reliable system is not only significant for improving a system’s productivity and products quality, but worth even more in multi-factory production because the failure of one entity may induce a vigorous chain reaction to the others. Maintaining the reliability in an acceptable level requires an optimal maintenance strategy and planning for each entity in the network. The objective of this paper is to propose a double tier genetic algorithm approach for multi-factory production networks, aiming to keep the system’s reliability in a defined accep table level, and minimize the makespan of the jobs. The optimization algorithm simultaneously schedules perfect and imperfect maintenance during the process of distributed scheduling. The optimization reliability of the proposed algorithm is demonstrated through three numerical examples, including its ability to maintain the system’s reliability in a defined acceptable level, the relationship of the acceptance level to production scheduling, and that of the machine age reduction factors to production scheduling.Article Outline1. Introduction2. Literature review3. Problem modeling3.1. Maintenance modeling3.2. Modeling of multi-factory production network4. Genetic optimization methodology4.1. Encoding of chromosome4.2. Mechanism of genetic optimization4.3. Formation of mating pool4.4. Crossover operation4.5. Mutation operation5. Numerical examples5.1. Example 15.2. Example 25.3. Example 36. ConclusionReferencesLiquid rocket engine test facility engineering challenges Original Research Article Acta Astronautica。