Um die Funktionalität von Getrieben über die Lebensdauer zu gewährleisten, muss der auftretende Verschleiß und die Temperaturentwicklung berücksichtigt werden. Die Oberflächenstruktur ist einer der wichtigsten Faktoren für das Einlaufverhalten. In diesem Beitrag werden die Auswirkungen verschiedener prozessbedingter Oberflächenstrukturen von Stahlritzeln auf das thermische und tribologische Einlaufverhalten eines Stahl-Polyamid-Getriebes untersucht.

Ursprüngliche Morphologie des PA66-Rads und Bereich zur Lokalisierung des Verschleißes

Polyamide

Kunststoff Werkstoffe

Thermoplaste

Tribologie

Betriebsausrüstung / Betriebsmittel

Getriebe

Maschinenelemente

Effekt der Oberflächenstruktur auf das Einlaufverschleißverhalten von Stahl-Polyamid-Getrieben

Bislang musste zur Auslegung von Kunststoffzahnrädern die Zahnweite punktuell und manuell vor, während und nach der Getriebeprüfung vermessen werden. Ein neu entwickelter In-situ-Getriebeprüfstand ermöglicht die Untersuchung von Zahnverformung und Verschleißverhalten während der Getriebeprüfung.

Zahnradverschleiß: Darstellung des Materialabtrags an den Zahnflanken am Beispiel einer Zahnradpaarung gemäß VDI 2736 Baugröße 1

16:9

In-situ-Getriebeprüfung für die anwendungsnahe Untersuchung spritzgegossener  Kunststoffzahnräder

Zahnräder

Halbzeuge und Zwischenprodukte

Kunststoff-Halbzeuge

Messtechnik

Verschleißprüfgeräte

Werkstoffprüfung

Prüfen von Kunststoffen

Zahnradmessgeräte

Form- / Oberflächenmesstechnik

Inline- / Online-Messsysteme

Qualitätssicherung

Qualitätssicherung Kunststoff

Inline-Messtechnik

Mikrometergenau auf den Zahn gefühlt

Getrieben durch nötige Energie- und Kosteneinsparungen finden Kunststoffe vermehrt Anwendung als Primärkomponenten in tribologischen Systemen. Der Trend zeichnet sich durch stete Forschung und Entwicklung hinsichtlich der Effektivität unterschiedlicher Materialkombinationen zur Reduktion von Reibung und Verschleiß aus, wobei die reibinduzierte Wärme zu den größten Herausforderungen zählt.

Gezielte Nutzung der chemischen Umwandlung von Magnesiumhydroxid — ein neuer Ansatz für die Polymertribologie

Die ganzheitliche Betrachtung von Simulation und Design hat bei der BASF eine lange Tradition. In der Zusammenarbeit mit dem Hersteller von Büromöbeln Wilkhahn wird am Beispiel des Freischwinger-Stuhls Metrik deutlich, wie Konstrukteure und Designer effizient zum Entwicklungsziel kommen. Dieses Angebot wird in Zukunft noch weiter ausgebaut. 

Simulation parallel zur Gestaltung verkürzt die Entwicklungszeit des Stuhls Metrik 

Produkt- / Formteildesign

Spritzgießsimulation

Prozesssimulation

Verstärkungsstoffe

Glasfasern / -matten

Virtuelles Probesitzen 

Jahrelang steigerte sich bei technischen Thermoplasten vor allem die Temperaturbeständigkeit, nun bedingen neue Mobilitätsformen eine ganze Reihe anderer Eigenschaften. Obwohl die genauen Spezifikationen für Kunststoffbauteile in Elektrofahrzeugen und die zugehörige Infrastruktur noch diskutiert werden, stehen die ersten serienreifen Materialtypen schon in den Startlöchern. 

Teilkristalline Thermoplaste für elektrische und elektronische Komponenten 

Elektromobilität

Energiemanagement / Ladetechnik

E-Mobility lässt umsatteln 

Nach Ultramid Advanced N stellt die BASF SE, Ludwigshafen, erstmals auf der Fakuma 2018 ein weiteres Polyphthalamid (PPA) vor: Ultramid Advanced T1000 – eine neue Gruppe von Compounds auf Basis von Polyamid 6T/6I. Innerhalb der Polyamide des Herstellers sind die neuen Werkstoffe damit die Produktgruppe mit der höchsten Festigkeit und Steifigkeit sowie mit konstanter Mechanik bei Temperaturen von bis zu 120°C (trocken) und bis zu 80°C (konditioniert). Aufgrund seiner teilaromatischen chemischen Struktur bietet es eine hohe Beständigkeit gegen Feuchtigkeit sowie aggressive Medien. 

Für Kontakt mit Chemikalien und Feuchtigkeit ausgelegt 

Neue PPAs Ultramid Advanced T1000 (PA 6T/6I)  

Meinung 

Compound

Meinung

kunststoffe.de

Gemischte Gefühle 

Rund 80 Teilnehmer fanden sich am 13. September in Heidelberg zur Jahrestagung des GKV/TecPart ¿ Verband Technische Kunststoff-Produkte e. V. ein. Wie dessen Geschäftsführer Michael Weigelt eingangs treffend bemerkte, spannte das Programm einen weiten Bogen von den Risiken populistisch beeinflusster Märkte bis zur Marktentwicklung in der Automobilindustrie. Die Zuhörer begegneten dabei einigen Gespenstern. 

Sehenswertes Programm bei der GKV/TecPart-Jahrestagung 

Brennstoffzelle

Kunststoffverarbeitung: Maschinen und Komponenten

Trockner

Spritzgießen

Seminare, Schulungen, Kongresse

KFZ-Zulieferer

Die Gespenster der Neuzeit 

Der Brightlands Chemelot Campus ist als Teil einer kooperativen Initiative auf die Entwicklung und Umsetzung fortschrittlicher generativer Fertigungstechniken ausgelegt. Drei aktuelle biomedizinische Projekte illustrieren die vielfältigen Möglichkeiten für Start-up-Unternehmen in diesem Markt. 

Entwicklungen in der Medizintechnik am Brightlands Chemelot Campus 

Additive Fertigung

Medizintechnik

Nährboden für die additive Fertigung 

Ein neues Joint Venture macht eine hybride Fertigungszelle marktreif. Darin führt ein 6-Achs-Roboter eine schneckenbasierte Plastifiziereinheit. Mit dem neuen Verfahrensansatz lassen sich auch granulatförmige, fasergefüllte Seriencompounds additiv zu Strukturbauteilen verarbeiten. 

Additive Fertigung von faserverstärkten PA6-Strukturbauteilen in hoher Geschwindigkeit 

Kohlenstofffasern / -matten

Flexible Fertigungssysteme

Schichtweise vom Granulat zum Bauteil 

Der Hersteller von Reinigungstechnik Kärcher setzt das umweltverträgliche PA66-Rezyklat Technyl4earth der Solvay Performance Polyamides für Sprühlanzen ihrer Hochdruckreiniger ein. Das Unternehmen hat die Technyl4earth- Aufbereitung als einer der ersten großen internationalen OEMs erprobt und angenommen. Seit dem sollen aus diesem Polyamidrecyclat bereits über eine Million Hochdrucksprühlanzen spritzgegossen worden sein, so der Hersteller.

Solvay nutzt Industrieabfälle aus der Airbag-Produktion 

Kärcher setzt PA66-Rezyklat ein 

Im kommenden Frühjahr soll in einer Kirche im oberbayerischen Altmühldorf eine additiv gefertigte Skulptur eingeweiht werden. Die einzelnen Elemente werden mittels selektivem Lasersintern aus Polyamid hergestellt. 

Detailansicht der Altarskulptur: Die Stangenelemente wurden im SLS-Verfahren aus Polyamid 12 gedruckt und anschließend beschichtet

Zellulare Altarskulptur additiv gefertigt

Selektives Lasersintern von Kunststoff, Metall, Keramik

Verfahren für die additive Fertigung

Pulverbettverfahren

Schöpfungsgeschichte mal anders

In der Automobilzulieferindustrie werden heute sehr komplexe und große Karosseriebauteile spritzgegossen. Um wichtige Eigenschaften wie Leichtigkeit, Stabilität oder Bruchfestigkeit gewährleisten zu können, verwendet die Branche oftmals glasfaserverstärkte Polyamid-Bauteile aus PA6 und PA12. Für Heißkanäle ist glasfaserverstärktes PA jedoch eine Herausforderung: Verschmutzungen und Verstopfungen sind häufig vorprogrammiert, was zu Maschinenstillständen führen kann. 

Die auf thermische Reinigung spezialisierte Schwing Technologies GmbH, Neukirchen-Vluyn, bietet eine schnelle, flexible Lösung auch für größere Heißkanalwerkzeuge an: Das bedienerfreundliche Pyrolyse-System Maxiclean reinigt überspritzte Heißkanalverteiler mit komplizierten Geometrien zuverlässig von Polymer-, Glasfaser- und Kohlenstoffresten sowie anorganischen Verunreinigungen. Wichtige Vorteile für die produzierende Automobilbranche sind die laut Hersteller rückstandslosen Reinigungsergebnisse und die erhöhten Werkzeugstandzeiten. 

Schonende Reinigung auch für große Heißkanalwerkzeuge 

Reinigung

Reinigungsmaschinen allgemein

Fasern

Glasfaserverstärktes Polyamid thermisch entfernen 

Die Verbindung von Kunststoff und Metall bietet wirtschaftlichen Leichtbau bei gleichzeitig hoher Funktionsintegration. Hierbei ist auch die Dichtheit gegenüber Medien ein notwendiges Kriterium für die Qualität der Verbindung. Durch eine Plasmaschicht in Kombination mit gezielter Modifikation von Kunststoffen entstehen äußerst feste Hybridbauteile. 

Plasma-SealTight-Prozess und Materialien für stoffschlüssige Kunststoff-Metall-Verbunde weiterentwickelt 

Dichtungen

Aluminium

Hybridtechnik

Verbindungstechnik

Verbindungstechnik, hybride

Da wird selbst Aluminium schwach 

Eine spezielle Modifikation für ständige und pulsierende Belastungen, wie sie beispielsweise bei Komponenten rund um den Pkw-Motorraum auftreten, stellte Lanxess auf der diesjährigen Fakuma vor. Ziel der Polyamid-Neuentwicklung war, eine der Kerneigenschaften des quasi nicht mehr verfügbaren PA66 mit PA6 abzubilden. 

Neue Polyamid-6-Serie für zyklisch belastete Komponenten als Alternative zu PA66 

Strukturbauteile bleiben länger fit 

Prüfstand zur In Situ-Messung der Verformungseigenschaften von Polymerzahnrädern

In diesem Beitrag wird eine neue Methode zur in situ-Verformungs- und Verschleißmessung von Polymerzahnrädern unter Betriebslast vorgestellt. Dieser Ansatz basiert auf der hochgenauen Messung und Verfolgung von Zeitdifferenzen in den Indeximpulsen von Encodern auf der An- und Abtriebsseite eines Zahnradprüfstandes.

Die Veränderung dieser Zeitdifferenzen über die Prüfdauer korreliert mit der Zahnverformung. Durch eine spezifische Kombination von Lastfällen können elastische, plastische und Verschleißverformungsanteile getrennt werden. Diese Arbeit zeigt außerdem das Potenzial der Methode, den Einfluss von geometrischen und strukturellen Abweichungen auf die resultierenden Betriebseigenschaften von Polymerzahnrädern zu untersuchen.

Die Validierung mit ex situ-Messungen zeigte eine gute Übereinstimmung mit den in situ-Untersuchungen. Die plastische in situ-Deformation der geprüften Paarung betrug 32 µm und konnte einer Kriechdeformation von etwa 9 µm aus einem Getriebekriechtest, einer Verschleißverformung von 25 µm entsprechend Koordinatenmessung sowie einer theoretisch kalkulierten thermischen Ausdehnung von etwa 1.5 bis 3 µm zugeordnet werden. Weitere Forschungen zur Prüfmethodik sind erforderlich, um die automatische Separierung von thermischer, elastischer, viskoelastischer und Verschleißdeformation zu ermöglichen.

Dominik Schubert, Christoph Herzog, Dietmar Drummer Lehrstuhl für Kunststofftechnik, FAU Erlangen-Nürnberg

Test Rig for the In Situ Measurement of the Deformation Characteristics of Polymer Gears

This paper presents a new method for in situ deformation and wear measurement of polymer gears under operating loads. This new approach is based on the highly accurate measurement and tracking of time differences in the index pulses of encoders on the driving and driven side of a gear test rig. The change in these time differences over the test duration correlates with the tooth deformation. Through a specific combination of load cases, elastic, plastic and wear deformation components can be separated. This work also shows the potential of the method to investigate the influence of geometric and structural deviations on the resulting operating properties of polymer gears. The influence of process-related structural deviations or geometric deviations from the ideal shape on operating properties such as vibrations, wear or achievable service life can be investigated in much greater detail. Thus, on the basis of in situ measurements, a deeper understanding of influences on the operating properties of plastic gears can be gained.

Prüfstand zur In Situ-Messung der Verformungs-eigenschaften von Polymerzahnrädern

In diesem Beitrag wird eine neue Methode zur in situ-Verformungs- und Verschleißmessung von Polymerzahnrädern unter Betriebslast vorgestellt. Dieser neue Ansatz basiert auf der hochgenauen Messung und Verfolgung von Zeitdifferenzen in den Indeximpulsen von Encodern auf der An- und Abtriebsseite eines Zahnradprüfstandes. Die Veränderung dieser Zeitdifferenzen über die Prüfdauer korreliert mit der Zahnverformung. Durch eine spezifische Kombination von Lastfällen können elastische, plastische und Verschleißverformungsanteile getrennt werden. Diese Arbeit zeigt außerdem das Potenzial der Methode, den Einfluss von geometrischen und strukturellen Abweichungen auf die resultierenden Betriebseigenschaften von Polymerzahnrädern zu untersuchen. Der Einfluss von prozessbedingten Strukturabweichungen oder von geometrischen Abweichungen von der Idealform auf Betriebseigenschaften wie Schwingungen, Verschleiß oder erreichbare Lebensdauer kann wesentlich detaillierter untersucht werden. So kann auf der Grundlage von in situ-Messungen ein tieferes Verständnis von Einflüssen auf die Betriebseigenschaften von Kunststoffzahnrädern gewonnen werden.

In Situ Test Rig for the Measurement of the Operating Characteristics of Polymer Gears

Polymer parts are increasingly important for tribological applications because of their advantageous characteristics such as dry run capability and economic mass production by injection moulding [1]. However, parts made of plastic show significantly lower wear resistance in comparison to metal parts [1]. The wear behaviour of plastic and metal pairings typically consists of a run-in stage, characterised by higher non-stationary wear rates, and a following steady state at lower constant wear rates [2]. This is due to the alignment between the contact surfaces, the formation of wear reducing interlayers composed of wear particles and the transition from the edge area to the more resistant core area [3, 4]. A variety of geometric and microstructural factors can influence the run-in and the steady state; among others surface roughness [5] and structure [4, 6] of the metal pinion, degree of crystallinity and spherulite size [3], or tooth modifications [7]. Consequently, the in situ wear measurement is of interest as it permits the wear determination over time and therefore a distinction between the run-in and the steady stage. This knowledge allows for a better estimation of necessary wear addendums [8]. Therefore, a new approach for the in situ wear measurement of plastic gears paired with steel pinions is presented and applied to determine geometric and structural influences on the operating properties of a polyamide-steel gear set.

2.1. Current methods and designs for in situ gear testing

Various in situ test methods for gears are described in the literature. There are two main approaches: test rigs for wear and lifetime measurement, and test stands for condition monitoring. The goal of condition monitoring is to decrease maintenance and repair cost by monitoring the health of a critical system [9], e.g. a gear drive. In condition monitoring test rigs sensor data, like acoustic or mechanical vibrations are recorded and the corresponding gears checked for signs of failure. Changes in these signals are correlated to certain types of failures, be it pitting, cracking of teeth or flanks [10], or excessive wear [11]. With corresponding models of the interaction of failure causes and vibrational profiles, inexpensive sensor systems to monitor a critical gear drives health can be built, using easily available vibrational data [12]. However, the underlying process for the gear defect, for example wear, cannot be quantified or analysed with these systems. For this reason, a variety of wear and lifetime test rigs has been designed. Almost all types of gear test rigs can determine gear lifetime trivially. The measurement of gear temperature by either thermographic camera or thermocouples is also widely established. However, there are only three main approaches to characterise the wear during operation: Gravimetric or tactile measurement or analysis of a system reaction.

A relatively easy way is to measure the weight loss of the system [13]. This method however, requires a substantial amount of wear leaving the system and does not allow the direct quantification of the reduction in tooth thickness. One tactile system uses a profile measurement to directly quantify gear wear [14]. This and similar systems using tactile measurements, however, require the gears to be big enough to be measured and the test rig to be stopped during the test run. Another approach is to measure a system reaction to the wear. For example, a test rig design be Hooke et al. [15] uses a pivoting gear block with a loading arm in contact with a fixed gear block. The rotation of the loading arm corresponds to the wear in the system. Due to its construction, this test rig might be highly susceptible to vibrations. To mitigate all these disadvantages, a new test rig for the in situ analysis of the deformation of gear sets under operating conditions was developed and validated at the Institute of Polymer Technology, LKT, which is now presented and employed in this work.

2.2. Influence of form and structural deviations

In general, geometric deviations from the ideal form lower product quality and function [16]. This is especially true for gears. Different tooth profiles [17], tooth geometries [18] and form deviations [19] can significantly influence the operating properties of polymer gears, like efficiency, transmission error, operating temperature, achievable lifetime or wear. Additionally, the structural properties, i.e. the makeup of the crystalline microstructure, can also significantly influence the operating properties of polymer machine elements [3]. With an increase in crystallinity and spherulite size the material strength [20], stiffness [21] and wear resistance [3] increase, whereas ductility and damping are decreased [21]. Using this knowledge to generate a favourable microstructure in polymer gears can lead to significantly improved lifetimes. However, little to no research has been done regarding the interaction of form and structural deviations. Most literature sources analyse either the one or the other. As of now, it is not known, whether the beneficial effects of a favourable morphology can outweigh the drawbacks of higher form deviations, and vice versa. For this reason, this work will present findings showing the influence of both, form and structural deviations, and their interaction on the operating properties of a polyamide gear set using a new in situ gear test rig.

A wire cut steel pinion and polyamide 66 (PA 66) gears with a geometry according to VDI 2736, module 1 mm, were chosen for this research to represent a typical gear size in actuating drives, see Table 1. The chosen material, Ultramid A3K, a PA 66 by BASF SE, Ludwigshafen, Germany, is often used in gear applications due to its high wear resistance.

Table 1:  Technical specifications of the gear set

To analyse the influence of form deviations on the operating properties of the gear set, two different mould contours were manufactured, based on the same specifications. One contour was generated using the software KissSoft 2019 by KissSoft AG, Bubikon, Switzerland, the other was designed by Frenco GmbH, Altdorf, Germany, using their Spline Calculator.

The flank lines generated with the two programmes differ in the number of exactly calculated vertices of the contour and the interpolation between them. The KissSoft contour approximates the involute contour between the geometrically exactly calculated vertices with line segments, whereas Frenco uses splines. Due to these approximations, there will be small deviations from the geometrically exact involute curve in the low micrometre to nanometre range.

In addition to these approximation errors, inaccuracies in the generation of the overall gear contour from the individual flank lines can lead to variations for example in the tooth thickness over the circumference of the gear. Both mould inserts were manufactured on the same wire erosion machine with the same processing settings. As will be shown, these differently generated contours lead to differences in transmission error and vibration. The same wire cut pinion made out of 100Cr6 steel, flanks hardened to HRC 55 and ground to Rz 1 µm, was used for all tests.

The polymer gears were produced by injection moulding using an Arburg 370U-700–30–30 by Arburg GmbH & Co. KG, Loßburg, Germany. To determine the effect of structural deviations, two separate mould temperatures, TMould = 60 °C and 100 °C, were chosen to generate different morphological properties. Table 2 shows the main processing parameters.

.2. Functional principle of the new in situ gear test rig

The experimental setup used for the in situ deformation and wear measurement is shown in figure 1. Generally, the gear test rig consists of a DC motor, type DSM150N by Baumüller, Nuremberg, Germany, that drives the steel pinion on the input side. A hysteresis brake, type CHB-12 by Magtrol, Rossens, Switzerland, generates a braking torque on the output shaft, on which the plastic gear is mounted.

To analyse the gear temperature a thermocouple, Type K, can be used. Its signals are sent to the data logging PC via telemetry, type TEL1-PCM-IND by Kraus Messtechnik GmbH, Otterfing, Germany. The high resolution and accuracy of the torque transducers, type TMB307, by Magtrol, Rossens, Switzerland allow to closely examine the variations in operating torque of the gear set and their frequency spectrum.

The essential components of the measurement technology of the newly developed gear test rig are two rotary encoders, type A020 by Fritz Kübler GmbH, Villingen-Schwenningen, Germany, on the input and the output shaft. Deformation of the polymer gear’s teeth, for example due to elasticity, thermal expansion, wear or creep, lead to a change in the relative angular displacement of the input and output shaft over time, see figure 2.

The encoders are used to calculate the angular displacement between the two shafts based on the increase in time differences between the index pulses of the encoders. Initially there is a time difference t0 between the index pulses on the input and the output shaft. Due to deformation, this time difference increases during the test run to t1. The change in time differences, Δt = t1 – t0, represents the increase in angular displacement. Using the fact that the time between two index pulses of the output shaft, T, is needed for one rotation, the increase in angular displacement can be calculated according to the following formula:

As a result of the measuring method, the calculated angular displacement is an integral measure of the tooth deformation. However, for the design of gears the local reduction in tooth thickness over the lifetime is the relevant design criterion to avoid premature failure due to wear. Thus, the angular displacement should be converted in an – albeit mean – change of local tooth thickness. Assuming a uniform and sufficiently small deformation over the tooth height, the change in tooth thickness Δs, at the diameter of interest, usually the pitch circle d, can be determined from the change in angular displacement Δφ, using equation (2):

In order to ensure comparability to existing measuring methods for tooth wear at the Institute of Polymer Technology (LKT), the measuring diameter dMWk = 38.146 mm according to DIN 3977 is used for calculating the tooth deformation. To achieve a sufficiently high accuracy, the encoders’ signals are sampled at a frequency of 80 MHz using a data acquisition module, type NI 9401 by NI, Austin, Texas, USA. Thus, the experimental setup detects the time-dependent angular displacements with an accuracy of approximately ±0.0003° at 1 000 min-1. This corresponds to a measurement error in tooth deformation of ±0.1 µm given a plastic wheel with a 39 mm pitch diameter. Disturbing influences, like vibrations or speed fluctuations, could increase the measurement error; nevertheless, the system is still very accurate compared to other concepts and reaches the accuracy of common displacement transducers.

In order to distinguish between the wear and plastic tooth deformation on the one hand and the elastic deformation of the plastic tooth on the other hand, a load spectrum is applied. The test rig automatically switches between a high or “testing” torque and a low or “measuring” torque after a set amount of load cycles. During the “high” cycles, the gear is subjected to the testing conditions. The load in the “low” cycles is reduced as far as possible without risking smooth meshing. The reduction in torque leads to a decrease in elastic deformation. By setting the deformation measurement of the first “low” cycle to zero, the following measure-ments in the “low” state only include the lasting deformations, creep and wear, see figure 3. As a result of this method, the experimental setup does not have to be disassembled in order to determine the gear wear and creep. However, as of today, the test rig does not analyse thermal expansion, creep and wear separately. Further research into load spectrums and operating modes to separate these effects is currently being done at the LKT.

3.3. Validation of the new wear testing method

The results of the new test rig were validated on the gear tests of the spline contour gears manufactured at 60 °C mould temperature. The gear test was performed on three specimens at an output speed of 1 000 min-1 for a duration of 106 load cycles, i.e. rotations. This results in a duration of 0.06 s per rotation on the output side, and about 1.0 s until the same teeth of pinion and gear mesh again, which is hereafter referred to as one meshing cycle. During the test the output torque was switched between the “high” setting of 1.0 Nm for 200 meshing cycles ( = 3 333 load cycles), and 0.3 Nm for 40 “low” meshing cycles ( = 666 load cycles). The deformation data was separated by load setting and compared to results of ex situ tests.

The design of this test collective is of particular importance. Ideally, the test rig is switched to the low cycles only for time it takes to collect sufficient data to evaluate the elastic deformation component. However, too fast changes between both states, e.g. by a very small number of low cycles, can lead to additional vibration whereas too slow changeover leads to the formation of two distinct deformation and temperature states. The combination of high and low cycles used in this work was chosen based on preliminary investigations to achieve a balanced measurement process. In further work, the influence of the test conditions on the measurement results will be investigated in more detail to develop an optimised testing strategy.

Compared to metals, polymers have a high thermal expansion. Due to frictional heating, the gear warms up during operation which reduces the measured deformation. The thermal expansion of the tooth Δs can be estimated with the following approximation.

The coefficient of linear expansion for Ultramid A3K is given as α = 98 × 10–6/K by BASF SE [22]. The tooth thickness in the pitch circle was measured as 1.438 mm. Assuming symmetrical expansion, half of the tooth thickness, 0.719 mm, can be used as the initial length s0. A suitable reference temperature is needed to calculate the thermal expansion. Usually, an estimation of the spatial distribution of the temperatures, for example based on the approximation of the complex heat generation and transfer mechanisms using numerical and/or analytical methods, would enable a sound evaluation of the thermal expansion. However, this would have exceeded the scope of this work. Especially since the effects due to thermal expansion were expected to be rather small.

Previous research [6] on similar PA66-steel gear sets at the same load collective generated flank temperatures of 50 – 60 °C. Furthermore, literature, among others [23], has shown the tooth core temperature can be a good estimation for the average temperature of a tooth. Thus, the tooth core temperature was used to estimate thermal expansion. During the test, the tooth core temperature rose from 23°C to about 40 °C, giving a ΔT of about 17 K. Based on this data the thermal expansion Δs was estimated to be 1.2 µm.

A worst case calculation using α = 100 × 10–6/K, the full tooth thickness of s0 = 1.5 mm and ΔT = 20 K suggests an expansion of only 3 µm. Since the estimated thermal expansion is relatively small compared to the other measured deformations and the temperatures are relatively stable during the test runs, this factor was regarded as a negligible, reversible constant for all tests.

A hydraulic pulsator test rig built by LUVRA Hydraulik und Regeltechnik GmbH, Nuremberg, Germany, was used to determine quasi-static tooth deformation in dependence of the applied force. Three representative teeth on three specimens of the spline contour manufactured at TMould = 60 °C were tested. The force was measured using a load cell, type U2B, the displacement was recorded with a displacement transducer, type W1T3, both by Hottinger Baldwin Messtechnik GmbH, Darmstadt, Germany. A single metal tooth was used to apply an increasing force on the polymer gear, which was generated by a hydraulic cylinder of the type HS5132 by LUVRA Hydraulik und Regeltechnik GmbH.

In the gear test the load on a single tooth is applied in about 1,54 milliseconds, equalling a rate of about 32 500 N/s. Limitations in the measuring equipment do not allow for such high loading speeds or tests at elevated temperatures. Therefore, the force was increased by a rate of 100 N/s until break at room temperature. The high load setting of 1.0 Nm corresponds to a force of 50 N, the low setting equals a force of 15 N. Furthermore, the creep characteristic of the specimens was determined in a creep test. A constant force of 50 N was applied to the specimens for about 24 000 seconds, which corresponds to 400 000 load cycles. Longer testing times were not possible due to technical limitations. One representative tooth of three specimens was tested. The resulting creep curve was extrapolated to 106 load cycles using a Power Law approximation to estimate the creep during the in situ tests.

The ex situ tooth wear deformation was evaluated using a coordinate measuring machine, type Leitz PMM 654, by Hexagon Metrology GmbH, Wetzlar, Germany. The measurements were performed by the Institute of Manufacturing Technology, FAU Erlangen-Nürnberg, Germany. The coordinates were measured in scanning mode with a scanning speed of 0.2 mm/s and 30 measurements per 1 mm. The tip radius was 1.0 mm. The measured contours of the three specimens and the 39 teeth were averaged and compared to the untested contour. The wear was evaluated as the biggest normal distance between the two mean contours.

3.4. Influence of form and structural deviations

After validation, the in situ deformation testing method is used in combination with the analysis of the gear temperature and the spectral analysis of the torque fluctuations to determine the influence of form and structural deviations on the operating properties of the gear set.

3.4.1. Characterization of form and structural deviations

Two mould contours (line and spline contour) and two mould temperatures (60 °C and 100 °C) were used to create four sets of specimens with different combinations of structural and form deviations to examine their interactions.

To characterise the form deviations, a two-flank rolling test according to VDI/VDE 2608 was performed on five gears using a ZWP06, manufactured by Frenco GmbH, Altdorf, Germany. Results are the radial composite deviation Fi”, the tooth-to-tooth radial composite deviation fi”, and the runout by composite test Fr”. Fi” is a measure for the overall form deviations of the gear, whereas fi” correlates with the form deviations of the teeth and Fr” is a gauge for the out-of-roundness of the gear.

The differences in contour design are so miniscule that there is no influence on the morphology of the parts. Thus, the microstructure across the gear flank was analysed using Fourier Transform Infrared Spectrometry (FTIR) with a Nicolet 6700 FT-IR, Thermo Electron Corporation, Madison, WI, USA, on 10 µm thin cuts of exemplary parts for the two mould temperatures.

The degree of crystallinity was calculated from the band ratios of the wave numbers 1 199 cm-1 (crystalline phase) and 1 180 cm-1 (amorphous phase) measured in extinction, as described in [24, 25]:

3.4.2. Operating properties of the gear sets

In the future, the test rig will be fitted with additional sensor equipment and test modes to characterise a wider array of operating properties. Acoustic and structure-borne sound sensors are planned to measure the Noise-Vibration-Harshness (NVH) properties of polymer gear drives. A test chamber will be integrated to run tests at elevated temperatures and with lubricants. And lastly a test mode for temperature and frequency sweeps will allow the characterisation of geometric and material influences on the vibration properties over a wide spectrum of operating conditions.

In this work, the influence of the part deviations on selected operating properties (in situ deformation, temperature development and vibration) were analysed using the new gear test rig. The tests were run with the test scheme used for the validation, i.e. three test runs per specimen group at an output speed of 1 000 min-1, a runtime of 106 load cycles, switching between 1.0 Nm for 200 meshing cycles and 0.3 Nm for 40 meshing cycles.

To exclude any effects due to pure shrinkage differences between the specimens, a compensation of the centre distance of the gears based on the process-induced shrinkage of the parts was applied. This compensation accounted for the difference between nominal and actual gear diameters.

For this work, three separate aspects of the operating properties were analysed. Firstly, the variations in torque due to vibrations caused by imperfections in the gears were analysed, since this is a measure of the influence of part deviations on additional dynamic loads which can lead to premature defects. To this end, the input torque signal sampled in one-second intervals with 5 kHz and then Fourier-transformed. There were no notable changes in the resulting frequency spectrum over time or between the specimens of the same group. Thus, a representative spectrum from the first “high” cycle is analysed.

Secondly, the influence of microstructure and form deviations on the gear temperature during operation was examined with a thermocouple embedded in the tooth root, since temperature greatly affects material strength and lifetime of polymer gears. Lastly, the influence of the deviations on the total plastic deformation (wear and creep) was investigated using the in situ method, since too high deformation and wear can cause the observed lifetime to be significantly shorter than expected.

3.5 Representation of the margin of error

The errors given in the results are the 90% confidence intervals (CI) for the mean and the difference of means, calculated based on a t-distribution, as follows:

Figure 4 shows the in situ deformation, calculated as described in section 3.2. Both, the “low” cycle and the “high” cycle curve of the in situ test exhibit a run-in phase, followed by a steady state of linear increase. This is consistent with the wear behaviour of polymer-metal systems [2]. The difference between the two curves is considered the additional elastic deformation as a result of the increase in load of 0.7 Nm between the “high” cycles and at the “low” cycles. Evaluating the in situ data results in an additional deformation of 58.6 ± 1.6 µm initially. This increases during the tests to 64.9 ± 11 µm after 106 load cycles, probably due to reduced stiffness caused by frictional heating of the material during the test.

The ex situ pulser test for the elastic material properties shows a roughly linear increase of deformation with increasing force, see figure 5 on the left. To validate the measurement of the additional elastic deformation, the pulser test is evaluated at the forces which correspond to the load on the pitch circle at the respective torque level.

In this setup 1.0 Nm torque corresponds to 50 N force in the pulser test and 15 N are equivalent to 0.3 Nm. This results in an elastic deformation of the tooth of from 12.2 ± 0.6 µm to 54.2 ± 2.0 µm for a difference of 42.0 ± 2.0 µm.

One explanation for this difference between in situ and ex situ measurements of the elastic deformation could be the torque differences in the meshing cycle due to dynamic loading of the teeth. The tested gear set has a nominal transverse contact ratio of 1.4. This means that on average 1.4 teeth are in mesh. At the beginning of the meshing cycle of the new tooth, the preceding tooth is still in contact. Both teeth share the applied load. This is followed by a phase in which only the current tooth transmits the load. Then the following tooth enters the engagement while the current tooth leaves the contact. A simplified schematic of this process is depicted in Figure 6.

Figure 6: Simplified schematic of load sharing during the meshing cycle

Using the calculation given below, it can be determined for the given gear set that there is one single tooth in mesh (= tsingle) for about 60 % of the meshing cycle. In the remaining 40 % two teeth (= tshared = 1 – tsingle) share the applied load.

While the mean torque during the test was 1.0 Nm, the actual force on the teeth varies due to load sharing in the meshing cycle. It can reasonably assumed that the torque shared between the two teeth during the concurrent meshing phase is half as high as the torque a single tooth transmits (Tsingle). Based on this assumption the highest effective load on a single tooth in this gear set can be estimated as 1.25 Nm, with following calculation:

If an effective single tooth load of 1.25 Nm (= 62.5 N) is assumed, the ex situ deformation is 74.1 ± 2.9 µm. Thus, the additional deformation in the ex situ test would be 61.9 ± 2.7 µm, agreeing with the in situ tests.

Another factor in the differences between the measurements of the elastic deformation could be the different testing conditions regarding temperature and strain rate, or loading speed respectively. Higher Temperatures result in a lower stiffness, increased loading speeds in increased stiffness. However, an exact analysis of these competing effects in the ex situ and in situ tests would require complex numerical modelling based on extensive thermo-mechanical material modelling, which is beyond the scope of this paper. Nevertheless, the effect of the increased temperature and loading speed on the material’s modulus shall be estimated based on the thermo-mechanical characterisation of the material.

Supported by the literature [23], it is assumed that the core temperature of the tooth (23 °C for the ex situ and 40 °C for the in situ test) can be used as a suitable reference temperature for estimating the mechanical properties of a tooth. To estimate the relevant loading frequencies, the inverse of the loading speeds of the ex situ and in situ tests (0.5 s and 1.54 ms respectively) are used. The resulting loading frequencies in the in situ tests (650 Hz) are higher than those in the ex situ tests (2 Hz) by about three orders of magnitude. To determine the frequency-dependent modulus, Dynamic Mechanical Thermal Analysis (DMA) according to DIN EN ISO 6721 was performed using a rotational rheometer, type ARES-G2 by TA Instruments, New Castle, USA. Test specimen was an injection moulded tensile bar, size A1 made from Ultramid A3K according to DIN EN ISO 20753. In the DMA, temperature sweeps from 0 °C to 250 °C were carried out at 1, 10, 25 and 50 Hz. Based on the time-temperature superposition principle, frequency master curves for the storage modulus at 23 °C and 40 °C (and 50 °C for additional reference) were generated from these measurements.

Figure 7:  Tensile bar (left) and shear frequency dependent modulus (right)

Evaluated at the operating points of the ex situ and in situ tests, there is only an insignificant increase in the modulus from 862 MPa at 2 Hz and 23 °C to 867 MPa at 650 Hz and 40 °C, see figure 7. Based on these DMA measurements, only a negligible reduction of the deflection of might be expected as a result of the differences in loading speed and temperature for the chosen operating conditions. However, more research into the thermo-mechanical properties of polymer gears under typical operating conditions is certainly warranted.

In the validation tests the in situ plastic deformation after 106 load cycles was determined to be 32.4 ± 5.9 µm, see figure 4. This deformation consists of two main components, creep and wear. To determine the ex situ creep an extrapolated power law model was evaluated at one and at 60,000 seconds (= 106 load cycles). This gives a creep of 8.5 µm, see figure 5 on the right. The wear deformation was defined as the biggest difference between the mean tooth surfaces of the untested and the tested gears as determined by coordinate measurement. The wear was identified to be 25.5 ± 0.5 µm, see figure 8. Thus, the total deformation measured with ex situ methods was 34 ± 2.0 µm, matching the in situ measurement of 32.4 ± 5.9 µm.

Figure 8: Mean tooth contours determined by coordinate measurement

Thus, both the elastic and the plastic deformation measured by the in situ test rig are validated using ex situ measurements, promising a very helpful tool to examine the behaviour of gear sets more closely. However, as of now, this method is only validated for this operating point. A more comprehensive validation of the system is currently being performed. Furthermore, the development of testing strategies for automatic separation of creep and wear in the plastic deformation data is subject of ongoing research at the LKT. Nevertheless, the presented method can be employed to investigate the influence of form and structural deviations on the operating properties of a polyamide-steel gear set.

4.2. Influence of form and structural deviations

There is a clear connection between the contour description and the form deviations of the test specimens in the two flank rolling test. Due to an unfavourable geometry generation the gears with the line contour show high tooth-to-tooth deviations, see figure 9 left side. Especially notable are the five peaks in the two flank rolling deviation of the gears with the line contour, figure 9 right side, which imply five slightly larger teeth on the gear. These five thicker teeth could generate additional vibrations during operation.

In contrast, the spline contour shows drastically lower tooth-to-tooth deviations, probably due to a better approximation of the geometrically ideal involute form and generation of more equally sized teeth. However, there is no statistically significant difference in the runout Fr” between the different contour designs or processing conditions. Fr” is mainly influenced by the position and the clearance of the shaft the gear is moulded onto in the injection-moulding tool.

There is also an influence of the mould temperature on the form deviations and the resulting flank rolling deviations. This is clearly seen in the characteristic peaks of the two flank rolling deviations, figure 9 on the right side. A small peak can be seen for every individual tooth of the gears manufactured at 100 °C. For the gears with the line contour, the five characteristic peaks are also slightly higher than those of gears produced at 60 °C mould temperature. Thus, it can be concluded that an increase in mould temperature leads to an increase in tooth-to-tooth deviation fi” and radial composite deviation Fi”.

There could be two main reasons. On the one hand, a higher mould temperature could lead to the melt staying warmer for longer, thus increasing viscosity and allowing a better moulding of possible contour errors. On the other hand, a higher mould temperature leads to a higher degree of crystallinity and formation of bigger sperulitic structures in the edge layer, see figure 10. This would increase the stiffness of the contact, thus leading to a higher impact of existing errors in the measurement, since there would be less elastic deformation of the contact area compensating for slight errors. A more comprehensive study of the geometry of the moulds and the gears itself is needed to determine and separate the exact cause, which is not in the scope of this but future work.

02022022_Kunststofftechnikl.pdf

Beispielpaarung zweier Zahnräder für die Bestimmung elastischer, plastischer und Verschleißverformungsanteile

02022022_FIN-333 Schubert

Autoren Dominik Schubert, M.Sc., Christoph Herzog, M.Sc., Prof. Dr.-Ing. Dietmar Drummer, Lehrstuhl für Kunststofftechnik, FAU Erlangen-Nürnberg

Sprache Der Artikel liegt in englischer Sprache vor.

Erschienen in Zeitschrift Kunststofftechnik / Journal of Plastics Technology 18 (2022) 2, Seite 93 – 116 © Carl Hanser Verlag GmbH & Co. KG ISSN 1864 – 2217