Failure analysis and modernization of high-pressure hydraulic press for drilling tubes testing
Introduction
The hydrostatic pressure testing of tubes is an obligatory technological operation either after their production in metallurgical plants or field-tests before drilling operations on oil and gas sites. During the tests, the tube is closed by screw-threaded caps from both sides and filled with water by special pumps to the high pressure of up to 125 MPa. Tubes are kept at this pressure within about 5–10 s to check possible leaks and defects, then they release water and reinstall caps on the next tube. Such a sequential technological process is realized by the special mechanized hydrostatic presses, which may be damaged from the tube exploded due to a crack or a defect of screw-thread of caps in case if the machine and surrounding protective structure are improperly designed. The examples of the design of the existing hydraulic presses for testing tubes with a diameter of up to 1420 mm and a pressure of up to 70 MPa are shown in Fig. 1 and Fig. 2. In these designs for tubes of various lengths, the end thrusts are provided, adjustable by a screw electric drive, as well as locks fixing the tube along the length with a hydraulic drive. However, such variants of hydraulic presses do not provide high productivity for a wide assortment of tubes. The safety issues arising during operation of high-pressure machines in the restricted areas of workshops and satisfying controversial demands to productivity always need great efforts from the designers. Therefore, industrial customers install testing presses of their design. Such example of the investigated hydraulic press is represented in Fig. 3.
During one of the tube tests on this press, under the pressure of 20 MPa (even less than maximum value by design), one of the end caps has suddenly released due to the screw-thread defect and tube being moving by a water jet shocked into the protective structure of the machine causing deformations and penetration damages. Inspection of the structure after hitting the cap on the left thrust showed visually noticeable signs of deformation of the foundation bolts M36 (Fig. 4a) and the bolts M24 of the upper beam joining (Fig. 4b). The front plate with a thickness of 14 mm on the right thrust was punched by the impact of the mass composed of the tube with water and the right cap with a sharp end of the pressure line tip (Fig. 4c).
This incident forced to conduct a detailed analysis of strength capacity of the existing protective structure and to develop a modernization plan to restrain all possible static loads and dynamic impacts for safe operation under conditions of higher pressures 69–125 MPa. Multi-disciplinary research is required (fluid dynamics, mechanical shock and vibration, materials penetration) for the diverse impacts estimation on the structure and the multi-variant calculations for a wide variety of testing tubes depending on their specifications.
The content of this research paper is organized into several parts. Section 2 gives information on the steel grades of tubes, testing pressures and tubes fracture conditions. Section 3 contains methods and procedure of impacts calculations on different elements of a structure. Section 4 represents the calculated impacts on the structure from the water jet and damaged tube fragments. Finally, Section 5 gives recommendations on press modernization to satisfy the strength capacity limitations of structure and testing performance for all types of tested tubes.
Section snippets
The steel grades and fracture pressures
According to the API 5CT standard [4], the mechanical properties of the tube material are independent of the assortment of products. They depend only on the tube strength group (class), which all are given in this standard. Impact strength is not controlled on tubes, but only on blanks of caps. In the calculations of the tubes fracture the material reference information is used of ISO/TR 10400:2007 [5]. The tubes sizes and masses of end caps for calculating their dynamic effect on the axial
Methods of impacts calculation
In this section, the procedure is proposed for calculation of the dynamic impacts on the axial thrusts when the cap is failed, the high-pressure water jet flowing out and the possible movement of the tube parts with subsequent penetration into front plate of the thrust and protective casing.
Results of impacts calculations
In this section, tubes testing conditions of all possible strength groups (classes) are analysed with various values of material properties and sizes. The calculations were performed for the extreme case of tube fracture into two parts in different proportions along the length and with the formation of fragments along the perimeter of the tube with multiple fractures. The structural parts of the press are made of St3 steel, which physical characteristics are as follows: density 7850 kg/m3;
Recommendations on press modernization and increasing of productivity
In this section, an analysis of the timing of technological operations of tube tests is carried out and possible options for changing the design of the axial thrusts and the mechanized protective casing are given.
Discussion
Upon the burst, tube or its parts accelerate in opposite to the water jet direction and the shock impact energy is proportional to the speed square that the mass has time to gain. Hence, the general recommendation for reducing dynamic loads on a structure is to keep the tube as close as possible to the protective casing and axial thrusts. On the other hand, some clearance is necessary so that during the tube burst, excessive pressure is not created between the casing and the tube increasing the
Conclusions
Multi-disciplinary research is conducted including fluid dynamics, mechanical shock and vibration, materials penetration for the estimation of diverse impacts on the structure of high-pressure hydraulic press for tubes and screw-thread caps quality testing.
The dynamical impacts related to water jet driving effect and reactive tube motion are described by the analytical models under realistic assumptions. The penetrated whole thickness (14 mm) of the frontal plate on an axial trust by the tube
Declaration of Competing Interest
The authors declare that they have no known competing financial interests or personal relationships that could have appeared to influence the work reported in this paper.
Acknowledgement
This activity has received funding from the European Institute of Innovation and Technology (EIT), a body of the European Union, under the Horizon 2020, the EU Framework Programme for Research and Innovation. This work is supported by EIT Raw Materials GmbH under Framework Partnership Agreement No. 19036 (SAFEME4MINE. Preventive Maintenance System on Safety Devices of Mining Machinery).
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