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Determining the Safest Anchoring Knot in a Fall Arrest System by Means of Static Tests

Building Sciences and Urbanism Department, University of Alicante, Carretera de San Vicente del Raspeig s/n, 03690 San Vicente del Raspeig, Alicante, Spain
Cresmes, Research Group for Testing, Simulation and Modelling Structures in Civil Engineering and Architecture, Civil Engineering Department, University of Alicante, Carretera de San Vicente del Raspeig s/n, 03690 San Vicente del Raspeig, Alicante, Spain
Civil Engineering Department, University of Alicante, Carretera de San Vicente del Raspeig s/n, 03690 San Vicente del Raspeig, Alicante, Spain
Department Statistics, Mathematics and Informatics, Universitas Miguel Hernández, Avenida Universidad s/n, 03202 Elche, Alicante, Spain
Authors to whom correspondence should be addressed.
Symmetry 2024, 16(2), 167;
Submission received: 2 January 2024 / Revised: 25 January 2024 / Accepted: 29 January 2024 / Published: 31 January 2024
(This article belongs to the Special Issue Symmetry in the Mechanical Behavior of Materials)


Today, rope access systems (RASs) and fall arrest systems (FASs) incorporate significant technological innovations. This research aims to determine the safest knot to be used in RASs. The most secure knots are those that leave the most resistance in the rope. Static laboratory tests, followed by an extensive statistical analysis of the obtained data, were carried out under controlled conditions. Five types of anchor knots were selected and studied using three rope models with similar diameters, and we analysed the symmetrical versions in the dextrorotational direction. Thirty break tests were performed for each rope model. The total number of breakage tests was 90. The double overhand knot proved to be the safest knot with an average efficiency of 61.82%. A better understanding of the behaviour of knots and their correct use in FASs will be key to accident prevention.

1. Introduction

The continuous improvement of safety standards to prevent accidents is a legal and moral obligation. Accidents have socioeconomic impacts that affect business, commerce, education, and public policy [1,2]. Improving the elements of individual fall protection systems will have positive effects on the number of serious accidents. Falls from a height are one of the leading causes of fatalities. In the United States (US) construction industry, these accidents caused 5701 fatalities between 2003 and 2018, with 1102 fatalities in 2019, the highest value since 2011 [3]. According to the data acquired by the Center for Construction Research and Training in 2018, the US construction industry reported 633 fatalities and 51 hospitalizations [4,5]. Safe Work Australia compiles deaths due to work-related injuries, specifically those caused by falls from a height. In 2021, the organisation determined that such falls were the third highest cause of occupational mortality, with 22 deaths accounting for 11% of all fatalities [6]. For 2020, Spanish statistics reflect similar data to those of Australia, with 86 deaths due to falls, representing 11.39% of the total number of fatal accidents [7]. According to the Health and Safety Executive in Construction in Great Britain, falls from a height constitute the main cause of mortality and represent 50% of all fatal injuries [8].
Fall arrest systems (FASs) are included in the European Standard (EN) 363 [9]. Rope access systems (RASs) are FASs in which the worker is positioned by ropes at the operation point. Ropes are the main element of an RAS. Figure 1 represents the main RAS components. Using a carabiner (1 in Figure 1), the knots connect the rope to the structure (2 in Figure 1) [10,11,12,13,14,15,16,17].
There are more than 3800 types of knots [18]. Some knots have been studied by other authors, but these previous works have serious shortcomings in terms of the methodology used and the treatment of the obtained data. Moreover, previously analysed knots are those used in sports. As a result, some knots that could be used as anchor knots, such as the double overhand knot, have not yet been studied [19,20]. Advances in technology and the use of new materials in rope manufacturing mean that the effects of knot selection on these new types of rope need to be re-examined [21,22,23,24]. The overhand sling, figure eight sling, figure nine sling, clove hitch, and double overhand sling are anchoring knots. These knots are used in rope access systems in the construction sector for the maintenance of skyscrapers, power pylons, dams, and unique high-rise projects [10,11,12,25,26,27,28,29].
Knots reduce the static breaking strain of ropes [18,19,29,30,31,32,33] by 35–50%, depending on the diameter and type of rope and knot. A summary of the wide range of results in this field [34,35,36,37] is shown in Figure 2. This lack of homogeneity in the results can be explained by the fact that some authors did not consider important test parameters such as the loading rate, the acclimatisation of the specimens, the need for loading cycles prior to failure, or the minimum number of tests.
Authors such as Boron, Drohan, Merchant, Diamond, and Gómez [25,34,38,39,40] used the manufacturer’s breaking strength data in their studies. Manufacturers provide a minimum knotless tensile strength of the rope. However, the data provided by manufacturers are usually much lower than the real breaking strength. Brown, Milne, Aldazábal, and Simon [26,35,36,41] have determined this value experimentally using tests in which the real value of the break is obtained.
To obtain reliable results in static tests, it is important to establish a low loading speed close to the equilibrium, since in quasistatic and dynamic tests, it cannot be assumed that the ropes exhibit a homogeneous regular behaviour. It is necessary to perform the previous loading cycles in tests with new ropes to simulate their use and achieve more homogeneous mechanical response behaviours in both the core and sheath assembly.
To evaluate the loss of static rope strength due to the presence of knots, the efficiency term (η) of a knot is used. This term is defined as the quotient of the breaking load of the rope with a knot (x) and the breaking load of the rope without a knot (y), the magnitude of which is usually expressed as a percentage via Equation (1):
η = x y   100 %
Measuring the efficiency as a function of knotless rope strength stems from work by Šimon [41] (p. 404), who, for the first time, proposed the following concept: “Loop knot efficiency is not a constant, but depends at least on the static breaking strength of a rope”. In addition, manufacturers indicate a minimum knotless tensile strength for their ropes, but the provided data are usually much lower than the actual breaking strength. Manufacturers also do not provide static breaking strength values for ropes with different knots. Consequently, the efficiency value must be obtained in the laboratory for each rope and knot assembly. Figure 2 shows the average efficiency values of the main anchoring knots obtained from the studies carried out in the last two decades. The technological progress of these materials remains rapid and constant.
Figure 2. Efficiencies ( η ) of various knots obtained by authors in previous research [25,26,29,34,35,38,39,40,41,42].
Figure 2. Efficiencies ( η ) of various knots obtained by authors in previous research [25,26,29,34,35,38,39,40,41,42].
Symmetry 16 00167 g002
Table 1 provides a schematic overview of the main characteristics of previous investigations, including the type of rope, the standard used, the experimental procedure, and the source of the knotless breaking load.
From a strictly statistical perspective, several authors stated that tests should be repeated at least five times for each specimen, especially for systems that affect employee safety and life [35,41]. These recommendations are in line with the American NFPA 1 [49]. Drohan [34] stressed the importance of conditioning samples 72 h prior to testing and performed an atmospheric control test at 20 °C under 65% humidity, as specified in ISO 139:2005/A1 [29,42,53]. Some authors consider the number of cycles before the breaking load to have a significant effect on the obtained results. Baszczyński [54] observed significant differences between the load-elongation characteristics obtained in the first load cycle and those obtained in subsequent cycles and concluded that the organisation of the textile structure was more strongly affected during the first load. After working with new ropes, Gómez [40] concluded that ropes break at lower loads when new.
In short, the required information to assess the most appropriate knot for use in RASs is lacking. The aim of this research was to carry out rigorous laboratory tests considering the variables that affect the test: humidity, temperature, speed, load cycles, and sample conditioning. Complemented by a rigorous statistical study of five breaks per configuration, including knotless breaks, reliable data were obtained to determine which knot is the safest anchor knot for FASs and RASs. Selecting the correct anchorage knot significantly contributes to safety when working at a height and reduces the probability of a fall-from-height accident.

2. Materials and Methods

2.1. Ropes and Test Samples

The regulations applicable to ropes used in RASs in Europe are Directive 2001/45/EC of the European Parliament and of the Council of the European Union [55]. As personal protective equipment (PPE), ropes are also affected by EU Regulation 2016/425 of the Official Journal of the European Union [56]. RAS ropes are products with an international standard certification. European regulations for low-stretch kernmantle ropes and dynamic ropes establish technical specifications that provide a presumption of conformity for applying the CE mark according to EU Regulation 2016/425 on PPE [56]. Compliance with the technical requirements of this regulation presupposes compliance with the essential safety requirements of Directive 2001/45/EC [55].
Three types of rope were selected from different manufacturers with international reputations in the RAS sector. Table 2 shows the main technical characteristics of the tested ropes. All ropes were new, low-elongation kernmantle type A ropes in accordance with EN 1891 [43]. All ropes were made from synthetic textile fibres and consisted of a braided core and sheath with a low elongation coefficient. These are the types of ropes used in RASs [10,12,25,26,27,29,41,57]. The range of diameters was between 10.5 and 11 mm, which is the range commonly used in RASs and allows for a reliable comparison of results. The textile materials used for these ropes were polyamide (PA) and polyester (PES) with low-stretch core sheathing [53]. Notably, the λ rope has double normative certification and complies with the requirements of EN 1891 [43] for low-stretch core ropes and EN 892 [46] for dynamic ropes. A study on this type of rope with double certification is, therefore, a milestone. Types A and Ψ are certified by the National Fire Protection Association (NFPA), the Eurasian Economic Union (EAC), and the International Mountaineering and Climbing Association (UIAA) [49,58,59].
The tested specimens (Figure 3) were made using sections of the three rope models. Six specimens were taken from the same rope sample, with five for knot tests and one for knotless tests. The lengths of the five samples with knots ranged from a minimum of 2.5 m to a maximum of 4 m, depending on the type of knot. In this way, the rope could be wound around the test bollard three times. The knot was tied at one end of the rope, while the other end of the rope was left untied. In the test specimen reserved for evaluating the resistance of the rope, no end or knot type was made. Instead, the rope was simply coiled around the two bollards.

2.2. Knots

Based on the available documentation, we tested five of the most commonly used loading knots (Figure 4) in RASs [11,38]: the figure nine loop, figure eight loop, double overhand noose, clove hitch, and overhand loop. All knots were configured using the symmetrical dextrorotatory versions (see Figure 5).
The knots in this paper were studied by applying a load longitudinally to the rope axis (standard load), as this is how knots are loaded when used in RASs. From a geometrical perspective, each knot has two symmetrical versions in its construction. In this study, we examine the I-geometry (see Figure 5, red centre); i.e., a symmetrical version of knot construction with the loops in a dextrorotational direction. A well-made knot is particularly important to ensure the homogeneity of the results and draw the correct conclusions. To this end, all knots in this work were made by the same person who is an expert in fall protection systems, a specialist in RASs, a firefighter, and a rescuer with more than 30 years of experience.

2.3. Experiment Setup and Procedure

The rupture tests described in this paper were carried out at the Geotextiles and Geosynthetics Laboratory of the AITEX/Research and Innovation Centre. An INSTRON model 5984HK8242 dynamometer with a maximum capacity of 150 kN was used. This machine allows both the force and displacement to be controlled (Figure 6). The force was recorded with an INSTRON load cell, using a full scale of 150 kN and a measurement frequency of 50 Hz. Data management was carried out using Bluehill software (Bluehill version: Universal V4.15), also from INSTRON (INSTRON version: 5984). The knotless rope tests were carried out using a Zwick Roell Z600E (Manufacturer: Instron, City: Barcelona, Country: Spain) maximum-capacity dynamometer with an integrated cell. A bollard (13 cm in diameter) was used to hold the free end (without a knot or sewn end). The free end was wrapped around the bollard at least three times to ensure sufficient friction between the rope and the bollard to prevent the rope from slipping (Figure 6a,b). The last section of rope was secured with a clamp stopper to prevent slippage. The testing machine and a croquis of the bollard used are shown in Figure 6. The smaller the diameter, the higher the stress concentration; thus, a smaller diameter may cause a breaking point to contact the bollard. To measure the tensile breakage correctly, the rope should theoretically break when the first loaded knot becomes strangulated [11,26,32,50]. If the knot breaks on contact with the bollard, the test method is incorrect, and the true tensile break is not obtained. Once the specimen has been conditioned, the knot is installed in the loading gantry. Then, the cylinder is inserted through the core of the knot and secured with a locking mechanism. The setup and procedure of the experiment are shown in the flow chart in Figure 6c.
The test procedure consisted of placing a specimen in the test gantry and breaking it. Five breaks were made for each knot type and rope model selected. To acclimatise them, the samples were placed in a conditioning chamber for 72 h prior to testing. A temperature of 20.0 °C (±2.0 °C) and relative humidity of 65% (±4.0%) were maintained in the room in which the tests were carried out, as specified in ISO 139:2005/A1 [53]. In all tests carried out, the load was applied at a speed of 1 mm/s, which is the maximum speed allowed by the EN 364 [60]. The test specimens were 40 cm in length between the bollards.
Although the EN 364 standard [60] specifies a few tests (between two and four) for each set of samples, the most restrictive criterion established by the NFPA 1 standard [49] was used in this research. This standard states that at least five tests must be carried out whenever the lives of workers are at stake. The requirements of ISO 7500-1 [61] were also considered. Two bollards with identical characteristics were used to determine the knotless rope strength. Each end of the rope was wound onto the bollards. The sample was placed in the tester (Figure 6). The diameter of the bollard holding the knotless rope was 13 cm. A smaller diameter can cause the rope to break when it encounters the bollard, because the smaller the diameter, the higher the stress concentration. To measure the tensile breakage correctly, the rope should theoretically break when the loaded knot becomes strangulated for the first time [11,26,32,50]. After conditioning the sample, the knot was placed on the loading gantry. Then, the cylinder was inserted through the coke of the knot and secured with a pin. The terminal was wrapped around the bollard three times. The terminal stop was secured to prevent any slippage (Figure 6). Each specimen was subjected to three cycles: two previous loading/unloading cycles up to 5 kN and a final cycle until breaking. Figure 7 shows the cycles each specimen was subjected to. Previous authors, such as Boron, Martin, Drohan, and Aldazabal [25,29,34,36] did not carry out preloading cycles in their tests. However, these preload cycles were performed by Milne [35]. Šimon [41] explains that this omission was due to using testing ropes that were not new. In the present research, these prestress cycles were essential, as new ropes were used.
Overall, three different rope models were used: five sets of knotted tests and a final set of knotless tests. Each test series consisted of five breaks. In total, 25 knotted breaks and five knotless breaks were carried out.

3. Results and Discussion

3.1. Statistical Analysis

The Kolmogorov–Smirnov and Shapiro tests were used to validate the normality assumption. The quantitative parametric data were presented as the mean ± standard deviation. To study the influence of the two categorical variables (rope and knot) on the resistance, a two-way analysis of variance (ANOVA) test was carried out. To build a predictive model and analyse the influence of the rope breaking force on the knot efficiency, a linear regression was performed. An estimation of the measured values using the solid approximation of the knot efficiency probability distribution function (PDF) was performed following the results presented in Šimon [62]. The R software package version 4.2.3 was used for the analyses.

3.2. Knotless Rope Breaks: Efficiency

As defined in Equation (1), to obtain the knot efficiency (η), it was essential to measure the resistance of the ropes without knots, since the resistances given by the manufacturers were unreliable (Table 3).
The effect of each rope and knot on the efficiency was analysed using the ANOVA after obtaining the efficiency values for each rope and knot. Table 4 shows the estimated effects of the knot and rope on the efficiency when no interaction was included in the model [63].
Including an additive model in the ANOVA yielded results like those obtained when interactions were considered. In this case, the R2 was 0.8814. The hypothesis of the normality of the residuals was satisfied with a p-value of 0.70 after applying the Shapiro test. The interaction present in the model was not significant at a 0.01 level, which was also the case for the static breaking strength.
An interaction graph (Figure 8) was created to assess the presence of any interactions between the rope and knot varieties. As shown in the graph, the behaviours of different ropes were the same for different knot types. The knot type and rope type had a significant effect on the efficiency and breaking strength. Table 5 shows the estimated effects of each factor (knot and rope).
The results in Figure 9a,b show that the greatest efficiency was obtained for the knots with a larger volume, specifically, the double overhand knot and the figure nine loop. Marturello and Muffly [64,65] presented similar results and suggested increasing the number of turns (i.e., knot size) to improve the knot efficiency. The observed effect of the number of turns of the knot on the loss of strength in the rope can be explained by the process that the rope experiences during the breaking process. Tension forces are transferred along the whole length of the rope. In the area of the knot, this traction causes the knot to tighten. At the entrance of the knot, the rope is then constricted. As the tension in the rope is inversely proportional to the cross-sectional area, reducing the cross-sectional area at the entrance of the knot greatly increases the tension in this area. Breaks always occur at the knot entrance in knotted ropes. Notably, the rope with the smallest diameter ψ was the rope with the highest efficiency among the tested rope models shown in Figure 9c,d. To estimate the efficiency of each rope/knot separately, the scheme presented by Šimon [62] was considered due to the lack of symmetry in the PDF of efficiency. Two knots had an average efficiency above 60%: the double overhand knot and the figure nine loop. The figure eight loop and the overhand loop yielded average efficiency results between 48% and 60%, respectively. The clove hitch had the lowest efficiency, with less than 45%. The least-squares approximation of these two parameters was used to determine if there was a trend in the knot efficiency as a function of the breaking load of the rope on which the knot was tied.
The results presented the efficiency of each knot as a linear decreasing function dependent on the static breaking load of the rope (Figure 10). The graph shows two types of lines with slopes that are clearly distinguishable from each other: (1) knots of the figure eight and figure nine families and (2) all other knots. Among previous authors, only Marturello [64] and, in particular, Šimon [62], carried out valuable, rigorous statistical analyses. We compared the results of the slopes published by these two authors with those presented in this work.
The double overhand knot had a mean efficiency of 61.82%. The confidence intervals were 1σ (56.45, 67.76) and 2σ (51.55, 74.41). In Figure 11a, the efficiency of this knot is plotted as a linear decreasing function of the knotless breaking strength: η (y) = −0.78 (y − 34.996) + 44.202%. The best efficiency was observed when using this knot.
A mean efficiency of 60.05% with confidence intervals of 1σ (55.11, 65.54) and 2σ (50.62, 71.72) was obtained for the figure nine loop (see Figure 11b). The decreasing function obtained was η (y) = −2.19 (y − 34.996) + 60.375%. The efficiency (74%) was almost identical to that observed by Šimon [62] on a single rope. However, the range used by Šimon, with 2σ (71.19–76.81) obtained using a single rope, was more focused. The range of values obtained in this paper was much broader, using three ropes with different diameters and manufacturers. The following data were reported by other authors using less detailed experimental procedures and less statistical rigour: Merchant [38]: 85% efficiency for used ropes and breaking strength obtained from the manufacturer; Núñez [42]: 83% efficiency; and Gómez [40]: 75% efficiency using new/used ropes and breaking strength obtained from manufacturer.
Figure 12a shows the data for the figure eight knot, with a mean efficiency of 54.84% and confidence intervals of 1σ (50.07, 60.11) and 2σ (45.72, 66.02). This is undoubtedly the most commonly studied knot and that with the largest number of results available from previous studies. Higher efficiency values have been obtained by many authors. For example, Diamond [39] reported an average efficiency of 70%. However, he did not report important aspects of the test methodology, such as whether the rope was used or new, the test speed, or whether the samples were acclimatised. Šimon [41] found a mean efficiency of 64.42%. The resulting confidence interval was considerably lower than that obtained here, because Šimon used only one type of rope, whereas this study used three different rope models. Merchant [38] obtained a 75% efficiency for used ropes. However, he did not clearly define the experimental procedure or the manufacturer’s breaking strength. Milne [35] found an efficiency of 76% for new ropes and used his own tests to assess the ropes’ breaking strengths. Boron [25] reported an efficiency of 77% for new ropes using a well-defined methodology but used the manufacturer’s breaking load as a reference.
Finally, the highest average efficiency value obtained prior to the present work was that of Brown [26] at 87.29%. However, this study did not define whether the rope was new or used, nor did it provide relevant details on the experimental procedure. Nevertheless, the reported efficiencies were derived from the tested data.
Efficiency values like those obtained in the present study were achieved by the analysed authors. Martin [29] did not indicate where the breaking strength of the rope was obtained but reported an efficiency of 55.49% for new ropes. Gómez [40] reported a 60% efficiency with new and used ropes, but the experimental procedure was too undefined, and the breaking strength values were those of the manufacturers. In addition, no confidence intervals were provided. Drohan [34] reported an efficiency of 48% for used ropes. The breaking strength values of the ropes were those given by the manufacturers. Some previous studies stated that the figure eight is one of the best knots [26,35]. A number of these studies did not include other very important knots, including the figure nine loop and the double overhand knot. The efficiency results obtained in this research contradict the claims of Milne [35], who obtained an average efficiency of 61.82% for the double overhand noose knot. A detailed study of the results showed that efficiency was a decreasing function of knotless rope resistance, which was satisfied as follows: η(y)= −1.98 (y − 34.996) + 55.138%. Compared to the function obtained by Šimon [41], η(y) ≅ −0.77 (y − 32.79) + 66.4%, the obtained function decreased with a greater slope.
The clove hitch shown in Figure 12b had the lowest efficiency data of all the knots tested, with a mean efficiency of 44.08% and confidence intervals of 1σ (39.80, 48.78) and 2σ (35.84, 53.98). The decreasing function obtained corresponds to η(y) = −0.64 (y − 34.996) + 61.91%. Nuñez [42] and Merchant [38] gave efficiency results of 62% and 55%, respectively, for the efficiency of this knot. Nuñez [42] performed laboratory tests according to the EN 919 [44]. However, he did not give details on important experimental procedures such as the test speed or sample conditioning. Merchant [38] carried out tests on new ropes (11 mm in diameter) but did not adequately describe the test methodology.
The average efficiency for the overhand loop was 53.60%, while the confidence intervals were 1σ (48.70, 59.00) and 2σ (44.19, 65.02). The regression gave the following expression: η(y)= −0.78 (y – 34.996) + 53.717% (Figure 13). Šimon [41] reported a result similar to that obtained in this study for this type of knot, using five ropes and 108 trials (η (y)= −0.62 (y − 32.79) + 60.67%). Šimon reported a mean efficiency of 56.92% when testing only one type of rope. The confidence interval was slightly lower but remained within the expected values. Drohan [34] reported an average efficiency of 65% with an 11 mm low-stretch kernmantle rope. Drohan ran six tests on samples that were preconditioned at 20 °C and 65% humidity but did not perform any preload cycles. The breaking strength value was that which was provided by the manufacturer. Similar to Drohan [34], Brown [26] reported an efficiency of 65.28% and used 10 mm dynamic ropes. Brown also included the results of tests using a knot tied around a metal tube, increasing the efficiency by reducing the rope curvature at the knot [63]. Considering past studies, the present results seem reasonable, as previously reported efficiencies tend to cluster around the values in the present study.

4. Conclusions and Contributions

This research offers relevant data to determine knot efficiency more accurately in fall arrest systems, ultimately improving worker safety. Every knot reduces the tensile strength of a rope, but not all knots cause the same reduction in strength. The rope strength can vary by more than 6 kN depending on the type of knot chosen. The results obtained in this article are valid for a low-elongation core sheath rope of type A, EN 1891 [43], with a diameter of 10.7 ± 0.3 mm and a breaking load of 30–35 kN. The knots were tested in a standard load configuration, with the I-geometry knot construction already described in detail by other authors such as García and Castaño [11], Šimon [41], and Gómez [40]. The symmetry of the dextrorotational version was used for all knots. We observed the breaking point of the rope to be located at the knot. Indeed, the breaking point occurred at exactly the first strangulation point of the loaded rope. Knots with a greatest resistance to breakage are those with a greater volume, more loops, and a greater turning radius in the rope section where the breaking occurs, such as the figure eight loop and the double overhand knot. These knots behave much more efficiently than knot types with a smaller volume and less rope consumption, such as the clove hitch.
The resistance values obtained in the tests showed that each of the analysed knots, regardless of the type of rope, could resist a slow traction force above the injury threshold (12 kN). The minimum resistance values obtained with each of the knots and ropes tested were within the relevant safety limits, making such knots suitable for static rope access and positioning work. The most efficient results were obtained using the combination of an overhand knot and ψ rope with a smaller diameter and, theoretically, a lower resistance. The α rope has a larger diameter and is the strongest without a knot. However, this rope type yielded the poorest efficiency. From the results obtained, it is possible to establish a taxonomy from the most to least efficient: the double overhand knot, figure nine loop, figure eight loop, overhand knot, and carnation knot.
The obtained knot efficiency can be empirically represented as a decreasing line depending on the static breaking load of the rope. In the same way, a decrease in the knot efficiency can be observed as the rope diameter increases. The interaction data showed that a favourable or unfavourable knot behaviour occurred independently of the type of rope used from the perspectives of strength and efficiency. There was also a large variation in tensile strength depending on the choice of knot type. The rope type selection had no such significant influence. The figure eight- and figure nine-family knots were affected by a much more rapid loss of efficiency as the breaking strength of the rope increased. For the other knots, this phenomenon was less pronounced.
After analysing the results, we concluded that the best anchorage knot to use in RASs is the double overhand knot, in terms of efficiency and strength. The main contribution of this research, and its greatest novelty, is its identification of the double overhand knot as the safest knot to use in fall arrest systems.
These findings will have important implications in both sports and the workplace, particularly in construction, wind turbines, industry, rescue, climbing, canyoning, and caving. Indeed, the present results could have implications in any activity where rope access systems are used.
It is highly advisable for future authors to include technical specifications relating to knot efficiency in applicable regulations so that the knot behaviour against loads can be known. Establishing a good classification system for safe knots could help establish safety criteria for the elements and components of FASs.
In future work, it will be necessary to improve the knowledge of knots by analysing other characteristics such as the knot behaviour during dynamic tests. Future work could also explore hypotheses related to the relevance of knot construction and geometry (with levorotatory symmetry), as well as knot functionality and the complexity of untying after loading.

Author Contributions

Conceptualization, P.I.S. and E.Á.C.; methodology, P.I.S., E.Á.C., B.F. and J.F.M.; validation, P.I.S., E.Á.C., B.F., E.G. and J.F.M.; formal analysis, E.Á.C. and J.F.M.; investigation, P.I.S., E.Á.C., B.F. and E.G.; writing—original draft preparation, P.I.S., E.Á.C. and J.F.M.; writing—review and editing, P.I.S., E.Á.C., B.F., E.G. and J.F.M.; supervision, P.I.S., E.Á.C., B.F. and E.G.; project administration, B.F. and E.G.; funding acquisition, P.I.S., E.Á.C., B.F. and E.G. This article is part of the doctoral thesis of P.I.S. All authors have read and agreed to the published version of the manuscript.


This research was funded by the University of Alicante and Centro de Innovación Vertical S.A.C., grant numbers PC20-01A and GRE 20-07-A.

Data Availability Statement

The data presented in this study are available upon request to the corresponding author. The data are not publicly available because possible misinterpretation of the data could cause fall from height accidents.


The authors are particularly grateful to the CIV Vertical Innovation Centre of Perú and the University of Alicante.

Conflicts of Interest

The authors declare no conflicts of interest.


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Figure 1. Example of an RAS. Figure according to the standard in [9].
Figure 1. Example of an RAS. Figure according to the standard in [9].
Symmetry 16 00167 g001
Figure 3. Rope models used during the tests.
Figure 3. Rope models used during the tests.
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Figure 4. Tested knots.
Figure 4. Tested knots.
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Figure 5. Possible loading of a knot, and the symmetrical realisation of a loop knot.
Figure 5. Possible loading of a knot, and the symmetrical realisation of a loop knot.
Symmetry 16 00167 g005
Figure 6. Encounter between the terminals and a bollard (a). Detail of the test machine (b). Test sequence (c).
Figure 6. Encounter between the terminals and a bollard (a). Detail of the test machine (b). Test sequence (c).
Symmetry 16 00167 g006
Figure 7. Results obtained for the knot overland loop with rope α.
Figure 7. Results obtained for the knot overland loop with rope α.
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Figure 8. Efficiency: interactions between the rope model and knot type.
Figure 8. Efficiency: interactions between the rope model and knot type.
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Figure 9. Efficiencies for each knot type and rope model: (ad).
Figure 9. Efficiencies for each knot type and rope model: (ad).
Symmetry 16 00167 g009aSymmetry 16 00167 g009b
Figure 10. Efficiency of the knot as a function of the breaking load of the rope.
Figure 10. Efficiency of the knot as a function of the breaking load of the rope.
Symmetry 16 00167 g010
Figure 11. Presentation of efficiency: (a) double overhand noose; (b) figure nine loop.
Figure 11. Presentation of efficiency: (a) double overhand noose; (b) figure nine loop.
Symmetry 16 00167 g011
Figure 12. Presentation of efficiency: (a) figure eight loop; (b) clove hitch.
Figure 12. Presentation of efficiency: (a) figure eight loop; (b) clove hitch.
Symmetry 16 00167 g012
Figure 13. Presentation of efficiency: overhand loop.
Figure 13. Presentation of efficiency: overhand loop.
Symmetry 16 00167 g013
Table 1. Main methodologies and experimental procedures used with knots.
Table 1. Main methodologies and experimental procedures used with knots.
AuthorRope TypeStandardsExperimental ProcedureBreaking Load without Knot
(1999) [42]
New low-stretch kernmantle rope
Polyamides and polyester
EN 1891:1999
Number of tests: 153
Sample conditioning according to the standard EN 919 [44]
No record
(2001) [34]
Canyoning 11 mm
Used rope
AS 4142.3 (1993) [45]Number of trials: 48
Number of tests per knot type: 6
Speed = 0.67 mm/s
Sample conditioning: 20 °C /65% humidity
Minimum breaking strength (MBS) = mean − 2sd
Prebreak load cycles: no
Obtained from manufacturer’s data
(2007) [38]
11 mm ropes for caving Used kernmantle rope
Nylon-6,6 polyamides
EN 1891:1999 [43]Distinguish between different knot configurations
Not stated: number of tests, speed, specimen conditioning, and applied load cycles
Obtained from manufacturer’s data
(2006) [35]
New ropes
EN 892 with adaptations [46]Number of trials: 180 (3 trials with no knot)
Number of trials per scenario: 5
Speed = 1 mm/s
Sample conditioning: no
Load cycles prior to breakage: 3 cycles at a 10% breaking load
Knots tied by three different people (to simulate the human factor in knot tying)
Obtained from our own tests
Aldazabal (2007) [36]Beal cord, 5 mm
New rope
EN 1891:1999
Number of trials: 45
Number of rehearsals per stage: 5
Speed = 1 mm/s
Sample conditioning: no
Prebreak load cycles: no
Data logging at frequency = 0.5 Hz
Obtained from our own tests
Diamond (2007) [39]Sailing Polyester Ø, 8 and 10 mm; Dyneema 8 mm
It is not stated whether the rope was new or used.
Number of tests: 158
No cycles
Steel bollard ropes with three turns of a drum (for holding ropes without a knot)
Test tubes of 2.3 m (knotless), 1.64 m (bowline knot), and 1.75 m (figure eight knot)
Not stated: test speed, acclimatisation samples
Obtained from manufacturer’s data
Brown (2008) [26]Dynamic climbing10 mm Beal Tiger
It is not stated whether the rope is new or used.
BS 3104 [47]
BS 892 [48]
Number of tests: 60
All labelled test tubes are 2 m
No load cycles
Not stated: test speed, sample acclimatisation, new or used rope
Obtained from our own tests
(2013) [25]
Escape rope
New ropes
NFPA 1983 CI 1801 [49]Number of tests: not determined
Number of rehearsals per stage: 5
Speed = 5.4 mm/s
Sample conditioning: room temperature [50,51,52]
Minimum breaking strength (MBS) = mean − 3sd
Prebreak load cycles: two preload cycles, the first of 130 N and the second of 830 N.
Obtained from manufacturer’s data
Martin (2015) [29]Escape rope
New ropes
NFPA 1983
CI 1801 [49]
Number of tests: 27
Number of rehearsals per scenario: 3
Speed = 5.4 mm/s
Sample conditioning: at room temperature and humidity
Minimum breaking strength (MBS) = mean − 3sd
Prebreak load cycles: no
Data logging at frequency = 10 Hz
Not provided
Gomez (2016) [40]Low-stretch kernmantle rope
Polyamide (PA) polyester (PES)
Ø 10 mm
New and used ropes
EN 1891:1999 [43]Distinguish between different configurations of symmetrical knots (levorotatory and dextrorotatory)
Number of tests: 216
Speed > 5 mm/s
3 tests each per scenario (sample set) knots
Long = not defined
0 cycles
Knots made by cavers
No sample acclimatisation
Obtained from manufacturer’s data
Šimon (2020) [41]Low-stretch kernmantle rope
New and used ropes
EN 1891:1999 [43]Number of trials: 81 (figure light, ABOK 1047) + 66 (double figure eight loop, ABOK 1085) + 19 (figure nine loop, ABOK 521) + 180 (overhand, ABOK 1009) + 153 (bowline, ABOK 1010) + 50 (alpine butterfly, ABOK 1053)
Minimum number of rehearsals per scenario: 12
Speed = 3 mm/s
Sample conditioning: tests carried out at ambient laboratory temperature
Prebreak load cycles: no
Obtained from our own tests
Table 2. Technical specifications in accordance with the manufacturer’s user manual.
Table 2. Technical specifications in accordance with the manufacturer’s user manual.
Model Axis (PETZL)
Model Lluisa (KORDA’S)
Model Parallel (PETZL)
StandardsEN 1891 type A [43]
NFPA 1983 [49]
UIAA 107 [59]
EN 1891 type A [43]
EN892 + A12016 [46] simple dynamic rope
EN 1891 type A [43]
NFPA 1983 [49]
UIAA 107 [59]
Diameter (mm)1110.610.5
Sheath slippage (%)1.301
Elongation between
50 and 150 daN (%)
Mass of the sheath (%)/mass of the core (%)41/5937.5/62.545/55
Mass per unit length (g/m)827775
Static strength without knots (kN)3032.327
Static strength with figure eight loop knots at ends (kN)19complies15
Static strength with sewn termination22complies22
Shrinkage (%)2−0.22
Numbers of carriers32 32
Number of falls with an FF = 120>510
Table 3. Knotless static strength. Manufacturer data vs. experimentally obtained data.
Table 3. Knotless static strength. Manufacturer data vs. experimentally obtained data.
Rope Modelα (11 mm) kpλ (10.6 mm) kpψ (10.5 mm) kp
Maximum and minimum breaking values obtained during tests3830–36053264–3068.303376.67–3362
Value provided by the manufacturer (knotless)3059.153293.682753.23
Terminal TypeBreaking Values Obtained during Tests (kp)
Figure eight loop (Abok 1047)
Symmetry 16 00167 i001
Figure nine loop (Abok 521)
Symmetry 16 00167 i002
Double overhand noose (Abok 409)
Symmetry 16 00167 i003
Overhand loop (Abook 1009)
Symmetry 16 00167 i004
Clove hitch (Abok 1245)1549.811464.261570.99
Symmetry 16 00167 i0051549.231352.741676.28
Knotless rope
Symmetry 16 00167 i006
Table 4. ANOVA results for efficiencies.
Table 4. ANOVA results for efficiencies.
ANOVAdfSSMSF Valuep-Value
Knot × Rope8191.523.92.750.0118
R2 = 0.8814
Table 5. Estimation of the knot effect and rope effect on efficiency.
Table 5. Estimation of the knot effect and rope effect on efficiency.
Differences between KnotsEffects (%)
Figure nine loop–figure eight loop+5.24%
Clove hitch–figure eight loop−10.93%
Double overhand noose–figure eight loop+6.78%
Overhand loop–figure eight loop−1.42%
Differences between RopesEffects (%)
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Sáez, P.I.; Carrión, E.Á.; Ferrer, B.; García, E.; Monge, J.F. Determining the Safest Anchoring Knot in a Fall Arrest System by Means of Static Tests. Symmetry 2024, 16, 167.

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Sáez PI, Carrión EÁ, Ferrer B, García E, Monge JF. Determining the Safest Anchoring Knot in a Fall Arrest System by Means of Static Tests. Symmetry. 2024; 16(2):167.

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Sáez, Pedro Ignacio, Elena Ángela Carrión, Belén Ferrer, Encarnación García, and Juan Francisco Monge. 2024. "Determining the Safest Anchoring Knot in a Fall Arrest System by Means of Static Tests" Symmetry 16, no. 2: 167.

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