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dynamic load - Search Results
Articles About dynamic load
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1 Dynamic Loads in Parallel Shaft Transmissions - Part 2 (May/June 1990)
Solutions to the governing equations of a spur gear transmission model, developed in a previous article are presented. Factors affecting the dynamic load are identified. It is found that the dynamic load increases with operating speed up to a system natural frequency. At operating speeds beyond the natural frequency the dynamic load decreases dramatically. Also, it is found that the transmitted load and shaft inertia have little effect upon the total dynamic load. Damping and friction decrease the dynamic load. Finally, tooth stiffness has a significant effect upon dynamic loadings the higher the stiffness, the lower the dynamic loading. Also, the higher the stiffness, the higher the rotating speed required for peak dynamic response.
2 Predicted Effect of Dynamic Load on Pitting Fatigue Life for Low-Contact-Ratio Spur Gears (March/April 1989)
How dynamic load affects the pitting fatigue life of external spur gears was predicted by using NASA computer program TELSGE. TELSGE was modified to include an improved gear tooth stiffness model, a stiffness-dynamic load iteration scheme and a pitting-fatigue-life prediction analysis for a gear mesh. The analysis used the NASA gear life model developed by Coy, methods of probability and statistics and gear tooth dynamic loads to predict life. In general, gear life predictions based on dynamic loads differed significantly from those based on static loads, with the predictions being strongly influenced by the maximum dynamic load during contact.
3 Effect of Extended Tooth Contact on the Modeling of Spur Gear Transmissions (July/August 1994)
In some gear dynamic models, the effect of tooth flexibility is ignored when the model determines which pairs of teeth are in contact. Deflection of loaded teeth is not introduced until the equations of motion are solved. This means the zone of tooth contact and average tooth meshing stiffness are underestimated, and the individual tooth load is overstated, especially for heavily loaded gears. This article compares the static transmission error and dynamic load of heavily loaded, low-contact-ratio spur gears when the effect of tooth flexibility has been considered and when it has been ignored. Neglecting the effect yields an underestimate of resonance speeds and an overestimate of the dynamic load.
4 Dynamic Loads in Parallel Shaft Transmissions Part 1 (March/April 1990)
Recently, there has been increased interest in the dynamic effects in gear systems. This interest is stimulated by demands for stronger, higher speed, improved performance, and longer-lived systems. This in turn had stimulated numerous research efforts directed toward understanding gear dynamic phenomena. However, many aspects of gear dynamics are still not satisfactorily understood.
5 A Computer Solution for the Dynamic Load, Lubricant Film Thickness, and Surface Temperatures in Spiral-Bevel Gears (March/April 1986)
Spiral-bevel gears, found in many machine tools, automobile rear-axle drives, and helicopter transmissions, are important elements for transmitting power.
6 Calculating Dynamic Loads, Sizing Worm Gears and Figuring Geometry Factors (May/June 2001)
Q&A is an interactive gear forum. Send us you gear design, manufacturing, inspection or other related questions, and we will pass them to our panel of experts.
7 CBN Gear Grinding - A Way to Higher Load Capacity (November/December 1993)
Because of the better thermal conductivity of CBN abrasives compared to that of conventional aluminum oxide wheels, CBN grinding process, which induces residual compressive stresses into the component, and possibly improves the subsequent stress behavior. This thesis is the subject of much discussion. In particular, recent Japanese publications claim great advantages for the process with regard to an increased component load capacity, but do not provide further details regarding the technology, test procedures or components investigated. This situation needs clarification, and for the this reason the effect of the CBN grinding material on the wear behavior and tooth face load capacity of continuously generated ground gears was further investigated.
8 The Design and Testing of a Low Noise Marine Gear (May/June 2000)
This article offers an overview of the practical design of a naval gear for combined diesel or gas turbine propulsion (CODOG type). The vibration performance of the gear is tested in a back-to-back test. The gear presented is a low noise design for the Royal Dutch Navy's LCF Frigate. The design aspects for low noise operation were incorporated into the overall gear system design. Therefore, special attention was paid to all the parameters that could influence the noise and vibration performance of the gearbox. These design aspects, such as tooth corrections, tooth loading, gear layout, balance, lubrication and resilient mounting, will be discussed.
9 Comparative Load Capacity Evaluation of CBN-Finished Gears (May/June 1990)
Cubic boron nitride (CBN) finishing of carburized gearing has been shown to have certain economic and geometric advantages and, as a result, it has been applied to a wide variety of precision gears in many different applications. In critical applications such as aerospace drive systems, however, any new process must be carefully evaluated before it is used in a production application. Because of the advantages associated with this process, a test program was instituted to evaluate the load capacity of aerospace-quality gears finished by the CBN process as compared to geometrically identical gears finished by conventional grinding processes. This article presents a brief description of the CBN process, its advantages in an aerospace application, and the results of an extensive test program conducted by Boeing Helicopters (BH) aimed at an evaluation of the effects of this process on the scoring, surface durability, and bending fatigue properties of spur gears. In addition, the results of an x-ray diffraction study to determine the surface and subsurface residual stress distributions of both shot-peened and nonshot-peened CBN-ground gears as compared to similar conventionally ground gears are also presented.
10 Parallel Axis Gear Grinding: Theory & Application (November/December 2000)
The goal of gear drive design is to transit power and motion with constant angular velocity. Current trends in gear drive design require greater load carrying capacity and increased service life in smaller, quieter, more efficient gearboxes. Generally, these goals are met by specifying more accurate gears. This, combined with the availability of user-friendly CNC gear grinding equipment, has increased the use of ground gears.
11 Determination and Optimization of the Contact Pattern of Worm Gears (March/April 2003)
The load capacity of worm gears is mainly influenced by the size and the position of the contact pattern.
12 Influence of Geometrical Parameters on the Gear Scuffing Criterion - Part 2 (May/June 1987)
In ParI 1 several scuffing (scoring) criteria were shown ultimately to converge into one criterion, the original flash temperature criterion according to Blok. In Part 2 it will be shown that all geometric influences may be concentrated in one factor dependent on only four independent parameters, of which the gear ratio, the number of teeth of the pinion, and the addendum modification coefficient of the pinion are significant.
13 Influence of Geometrical Parameters on the Gear Scuffing Criterion - Part I (March/April 1987)
The load capacity rating of gears had its beginning in the 18th century at Leiden University when Prof. Pieter van Musschenbroek systematically tested the wooden teeth of windmill gears, applying the bending strength formula published by Galilei one century earlier. In the next centuries several scientists improved or extended the formula, and recently a Draft International Standard could be presented.
14 Local 3-D Flank Form Optimizations for Bevel Gears (September/October 2003)
Optimizing the running behavior of bevel and hypoid gears means improving both noise behavior and load carrying capacity. Since load deflections change the relative position of pinion and ring gear, the position of the contact pattern will depend on the torque. Different contact positions require local 3-D flank form optimizations for improving a gear set.
15 Application of Miner's Rule to Industrial Gear Drives (January/February 1990)
We need a method to analyze cumulative fatigue damage to specify and to design gear drives which will operate under varying load. Since load is seldom constant, most applications need this analysis.
16 FZG Rig-Based Testing of Flank Load-Carrying Capacity Internal Gears (June/July 2012)
Micropitting, pitting and wear are typical gear failure modes that can occur on the flanks of slowly operated and highly stressed internal gears. However, the calculation methods for the flank load-carrying capacity have mainly been established on the basis of experimental investigations of external gears. This paper describes the design and functionality of the newly developed test rigs for internal gears and shows basic results of the theoretical studies. It furthermore presents basic examples of experimental test results.
17 Calculation of Tooth Root Load Carrying Capacity of Beveloid Gears (June 2014)
In this paper, two developed methods of tooth root load carrying capacity calculations for beveloid gears with parallel axes are presented, in part utilizing WZL software GearGenerator and ZaKo3D. One method calculates the tooth root load-carrying capacity in an FE-based approach. For the other, analytic formulas are employed to calculate the tooth root load-carrying capacity of beveloid gears. To conclude, both methods are applied to a test gear. The methods are compared both to each other and to other tests on beveloid gears with parallel axes in test bench trials.
18 Optimal Modifications on Helical Gears for Good Load Distribution and Minimal Wear (June 2015)
Helical gear teeth are affected by cratering wear particularly in the regions of low oil film thicknesses, high flank pressures and high sliding speeds. The greatest wear occurs on the pinion in the area of negative specific sliding. Here the tooth tip radius of the driven gear makes contact with the flank of the driving gear with maximum sliding speed and pressure.
19 Influences on Failure Modes and Load-Carrying Capacity of Grease-Lubricated Gears (January/February 2016)
In order to properly select a grease for a particular application, a sound knowledge of the influence of different grease components and operating conditions on the lubrication supply mechanism and on different failure modes is of great benefit.
20 Increased Tooth Bending Strength and Pitting Load Capacity of Fine-Module Gears (September/October 2016)
The common calculation methods according to DIN 3990 and ISO 6336 are based on a comparison of occurring stress and allowable stress. The influence of gear size on the load-carrying capacity is considered with the size factors YX (tooth root bending) and ZX (pitting), but there are further influences, which should be considered. In the following, major influences of gear size on the load factors as well as on the permissible tooth root bending and contact stress will be discussed.
21 Inclusion-Based Bending Strength Calculation of Gears (May 2017)
Reduced component weight and ever-increasing power density require a gear design on the border area of material capacity. In order to exploit the potential offered by modern construction materials, calculation methods for component strength must rely on a deeper understanding of fracture and material mechanics in contrast to empirical-analytical approaches.
22 Calculating Face Load Distribution Factor (March/April 2015)
How should we consider random helix angle errors fHβ and housing machining errors when calculating KHβ? What is a reasonable approach?
23 Application and Improvement of Face Load Factor Determination Based on AGMA 927 (May 2014)
The face load factor is one of the most important items for a gear strength calculation. Current standards propose formulae for face load factor, but they are not always appropriate. AGMA 927 proposes a simpler and quicker algorithm that doesn't require a contact analysis calculation. This paper explains how this algorithm can be applied for gear rating procedures.
24 Tooth Root Optimization of Powder Metal Gears - Reducing Stress from Bending and Transient Loads (June/July 2013)
This paper will provide examples of stress levels from conventional root design using a hob and stress levels using an optimized root design that is now possible with PM manufacturing. The paper will also investigate how PM can reduce stresses in the root from transient loads generated by abusive driving.
25 Improvement in Load Capacity of Crossed Helical Gears (January/February 1987)
Crossed helical gear sets are used to transmit power and motion between non-intersecting and non-parallel axes. Both of the gears that mesh with each other are involute helical gears, and a point contact is made between them. They can stand a small change in the center distance and the shaft angle without any impairment in the accuracy of transmitting motion.
26 Load Distribution Analysis of Spline Joints (May 2014)
A finite elements-based contact model is developed to predict load distribution along the spline joint interfaces; effects of spline misalignment are investigated along with intentional lead crowning of the contacting surfaces. The effects of manufacturing tooth indexing error on spline load distributions are demonstrated by using the proposed model.
27 New Methods for the Calculation of the Load Capacity of Bevel and Hypoid Gears (June/July 2013)
Flank breakage is common in a number of cylindrical and bevel gear applications. This paper introduces a relevant, physically based calculation method to evaluate flank breakage risk vs. pitting risk. Verification of this new method through testing is demonstrably shown.
28 Load-Sharing Model for Polymer Cylindrical Gears (November/December 2011)
This paper presents an original method to compute the loaded mechanical behavior of polymer gears. Polymer gears can be used without lubricant, have quieter mesh, are more resistant to corrosion, and are lighter in weight. Therefore their application fields are continually increasing. Nevertheless, the mechanical behavior of polymer materials is very complex because it depends on time, history of displacement and temperature. In addition, for several polymers, humidity is another factor to be taken into account. The particular case of polyamide 6.6 is studied in this paper.
29 Influence of Relative Displacements Between Pinion and Gear on Tooth Root Stresses of Spiral Bevel Gears (July/August 1985)
The manufacturing quality of spiral bevel gears has achieved a very high standard. Nevertheless, the understanding of the real stress conditions and the influences. of certain parameters is not satisfactory.
30 Longitudinal Load Distribution Factor of Helical Gears (July/August 1985)
The contact lines of a pair of helical gears move diagonally on the engaged tooth faces and their lengths consequently vary with the rotation of the gears.
31 Load Carrying Capacity of Screw Helical Gears with Steel Pinions and Plastic Wheels (July/August 2004)
There is an increasing significance of screw helical and worm gears that combine use of steel and plastics. This is shown by diverse and continuously rising use in the automotive and household appliance industries. The increasing requirements for such gears can be explained by the advantageous qualities of such a material combination in comparison with that of the traditional steel/bronze pairing.
32 Surface Damage Caused by Gear Profile Grinding and its Effects on Flank Load Carrying Capacity (September/October 2004)
Instances of damage to discontinuous form ground and surface-hardened gears, especially of large scale, have recently increased. This may be attributed partly to a faulty grinding process with negative effects on the surface zones and the surface properties.
33 An Investigation of the Influence of Shaft Misalignment on Bending Stresses of Helical Gears with Lead Crown (November/December 2008)
In this study, the combined influence of shaft misalignments and gear lead crown on load distribution and tooth bending stresses is investigated. Upon conclusion, the experimental results are correlated with predictions of a gear load distribution model, and recommendations are provided for optimal lead crown in a given misalignment condition.
34 Experience with Large, High-Speed Load Gears (July 2007)
The main theme of this article is high-capacity, high-speed load gears in a power transmission range between 35 MW and 100 MW for generators and turbo-compressors driven by gas or steam turbines.
35 CFD Technology for Rotorcraft Gearbox Windage Aerodynamics Simulation (August 2009)
A computational fluid dynamics (CFD) method is adapted, validated and applied to spinning gear systems with emphasis on predicting windage losses. Several spur gears and a disc are studied. The CFD simulations return good agreement with measured windage power loss.
36 Comparing Standards (September/October 1998)
One of the best ways to learn the ISO 6336 gear rating system is to recalculate the capacity of a few existing designs and to compare the ISO 6336 calculated capacity to your experience with those designs and to other rating methods. For these articles, I'll assume that you have a copy of ISO 6336, you have chosen a design for which you have manufacturing drawings and an existing gear capacity calculation according to AGMA 2001 or another method. I'll also assume that you have converted dimensions, loads, etc. into the SI system of measurement.
37 Transient EHL Analysis of Helical Gears (August 2016)
This paper addresses the lubrication of helical gears especially those factors influencing lubricant film thickness and pressure. Contact between gear teeth is protected by the elastohydrodynamic lubrication (EHL) mechanism that occurs between nonconforming contact when pressure is high enough to cause large increases in lubricant viscosity due to the pressure-viscosity effect, and changes of component shape due to elastic deflection. Acting together, these effects lead to oil films that are stiff enough to separate the contacting surfaces and thus prevent significant metal-to-metal contact occurring in a well-designed gear pair.
38 Thermal Behavior of Helical Gears (May 2007)
An experimental effort has been conducted on an aerospace-quality helical gear train to investigate the thermal behavior of the gear system as many important operational conditions were varied.
39 The Effect of Manufaturing Microgeometry Variations on the Load Distribution Factor and on Gear Contact and Root Stresses (July 2009)
Traditionally, gear rating procedures consider manufacturing accuracy in the application of the dynamic factor, but only indirectly through the load distribution are such errors in the calculation of stresses used in the durability and gear strength equations. This paper discusses how accuracy affects the calculation of stresses and then uses both statistical design of experiments and Monte Carlo simulation techniques to quantify the effects of different manufacturing and assembly errors on root and contact stresses.
40 The Effect of Start-Up Load Conditions on Gearbox Performance and Life Failure Analysis, With Supporting Case Study (June 2009)
If a gear system is run continuously for long periods of timeor if the starting loads are very low and within the normal operating spectrumthe effect of the start-up conditions may often be insignificant in the determination of the life of the gear system. Conversely, if the starting load is significantly higher than any of the normal operating conditions, and the gear system is started and stopped frequently, the start-up load may, depending on its magnitude and frequency, actually be the overriding, limiting design condition.
41 Analysis of Load Distribution in Planet Gear Bearings (September 2011)
In epicyclic gear sets designed for aeronautical applications, planet gears are generally supported by spherical roller bearings with the bearing outer race integral to the gear hub. This article presents a new method to compute roller load distribution in such bearings where the outer ring cant be considered rigid.
42 Comparison of Test Rig and Field Measurement Results on Gearboxes for Wind Turbines (October 2011)
This article describes some of the most important tests for prototypes conducted at Winergy AG during the product development process. It will demonstrate that the measurement results on the test rig for load distribution are in accordance with the turbine measurements.
43 Scoring Load Capacity of Gears Lubricated with EP-Oils (October/November 1984)
The Integral Temperature Method for the evaluation of the scoring load capacity of gears is described. All necessary equations for the practical application are presented. The limit scoring temperature for any oil can be obtained from a gear scoring test.
44 Controlling Tooth Loads In Helical Gears (March/April 1986)
Helical gears can drive either nonparallel or parallel shafts. When these gears are used with nonparallel shafts, the contact is a point, and the design and manufacturing requirements are less critical than for gears driving parallel shafts.
45 Size and Material Influence on the Tooth Root, Pitting, Scuffing and Wear Load-Carrying Capacity of Fine-Module Gears (September 2011)
In this study, limiting values for the load-carrying-capacity of fine-module gears within the module range 0.31.0 mm were determined and evaluated by comprehensive, experimental investigations that employed technical, manufacturing and material influence parameters.
46 Flank Load Carrying Capacity and Power Loss Reduction by Minimized Lubrication (May 2011)
The objective of this study was to investigate the limits concerning possible reduction of lubricant quantity in gears that could be tolerated without detrimental effects on their load carrying capacity.
47 Generating Interchangeable 20-Degree Spur Gear Sets with Circular Fillets to Increase Load Carrying Capacity (July/August 2006)
This article presents a new spur gear 20-degree design that works interchangeably with the standard 20-degree system and achieves increased tooth bending strength and hence load carrying capacity.
48 Pitting Load Capacity of Helical Gears (May 2008)
Influences of Load Distribution and Tooth Flank Modifications as Considered in a New, DIN/ISO-Compatible Calculation Method
49 Influence of Grinding Burn on Pitting Capacity (August 2008)
This paper intends to determine the load-carrying capacity of thermally damaged parts under rolling stress. Since inspection using real gears is problematic, rollers are chosen as an acceptable substitute. The examined scope of thermal damage from hard finishing extends from undamaged, best-case parts to a rehardening zone as the worst case. Also, two degrees of a tempered zone have been examined.
50 Practical Analysis of Highly-Loaded Gears by Using the Modified-Scoring Index Calculation Method (September/October 1986)
The power of high speed gears for use in the petrochemical industry and power stations is always increasing. Today gears with ratings of up to 70,000kW are already in service. For such gears, the failure mode of scoring can become the limiting constraint. The validity of an analytical method to predict scoring resistance is, therefore, becoming increasingly important.


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Lurraga House
Lurraga House offers superior accommodation at an affordable price, located on the Dingle Peninsula, just 15 mins drive from Tralee town, and it is an ideal base from which to discover all that Kerry has to offer.
This modern custom built family run B&B has two guest bedrooms which have been beautifully appointed with your comfort in mind. All are en-suite and feature satellite television, wireless internet access, hairdryers and tea/coffee-making facilities. Guests can relax after a busy day touring in our well maintained gardens or sun lounge.
An extensive breakfast menu is served in our breakfast room, the perfect way to start your day and it is included in the rates.
Lurraga House is within walking distance of a sandy beach, the local village of Camp with its lively bars, nearby restaurants and The Dingle Way Walk. Guests can enjoy the many nearby outdoor pursuits including hiking, fishing and windsurfing as well as golfing and swimming.
Availability & RatesTo view availability and prices please select dates and click 'Update Dates'
B&B Facilities & Policies
- Free Breakfast
- Free WiFi
- Hair Dryers
- Internet Access
Cancellation PolicyThis property has a 3 day cancellation policy. Failure to cancel within this time will result in a cancellation charge equal to the first night of your stay.
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Directions: From Tralee
Take the R559(N86 The Dingle road) past the village of Blennerville which also has a restored windmill and steam train for you to visit. Continue as far as the turning towards Camp. You then continue straight onto R560 towards Castlegregory. Passing the old petrol station on the right hand side of the road drive for 1 kilometer and you will approach a restaurant on your right, turn right at the junction and Lurraga House is on the left!
Directions From Kerry International Airport (KIR)
1.Head northwest 15 m
2.Exit the roundabout 50 m
3.Turn left at N23 1.3 km
4.Turn right at N22 (signs for Tra Li/Tralee) 11.7 km
5.At the roundabout, take the 1st exit onto N21
Go through 1 roundabout 3.6 km
6.At the roundabout, take the 1st exit onto Haig's Terrace/N21
Continue to follow Haig's Terrace 350 m
7.Continue onto Killierisk Rd/N22 650 m
8.At the roundabout, take the 2nd exit onto Castlemaine Rd/N70
Continue to follow N70 550 m
9.At the roundabout, take the 1st exit onto Dan Spring Rd/N86
Continue to follow N86 Go through 1 roundabout 3.0 km
10.Turn left at Dingle Rd/N86
Continue to follow N86 12.3 km
11.Continue onto R560 2.1 km
Turn Right at Restaurant Junction
12.Lurraga House is on the left hand side just past the restaurant
Located Near
Lurraga House is located near
Dingle Peninsula
Dingle Way
Golf, horse riding, wind surfing, angling & miles of golden beaches.
Tralee town centre 10 miles
Castlegregory village 5 miles
Blennerville windmill and steam train

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