International Journal of Manufacturing Engineering

Volume 2016, Article ID 6198278, 6 pages

http://dx.doi.org/10.1155/2016/6198278

## Pervasive Investigations of Critical Speed over Weight and Deflection Factors of Shaft Assembly in CNC Ball Screw System

PEC University of Technology, Chandigarh 160012, India

Received 3 April 2016; Revised 22 May 2016; Accepted 2 June 2016

Academic Editor: René J. Romero-Troncoso

Copyright © 2016 Kuldeep Verma and R. M. Belokar. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

#### Abstract

The demand for higher productivity requires machine tools to work on the adequate critical speed to have faster and more accurate ball screw system. Ball screw affects severely over the higher rotation speed of the shaft in computer numeric control (CNC) machining centers. This paper deals with an approach to calculate the initial critical speed of the shaft. Critical speed requires significant attention due to its major use in the manufacturing sectors. The impacts of weight on the critical speed of shaft assembly have been analyzed from theoretical as well as analytical investigations. Additionally, we evaluated the impact of weight on the deflection of the shafts along with failure analysis of shafts with respect to critical speed. Further, we computed the results for critical speed based factor to enhance the accuracy of CNC machining centers. Finally, the analytical estimations have been carried out to prove the validity of our proposal.

#### 1. Introduction

Research on the CNC machine tools is gaining considerable momentum in the recent years. There are many research efforts reported by different researchers to enhance the accuracy of CNC machining centers. A majority of CNC machining systems are using ball screw drive system. The effect of ball screw feed drive system must be addressed to improve the efficiency of CNC matching centers. Nevertheless, few researchers have focused on the critical speed of the shaft used in the ball screw system. Some of the initiatives in the field of CNC machine tools are as follows. Xu et al. [1] presented thermal error forecast and performance evaluation for an air cooled ball screw system. Kim et al. [2] reported damage prediction in the multistep forging process of subminiature screws. A study in precision grinding of screw rotors using CBN wheel was proposed by Wei et al. [3]. A relation establishing the correlation between feed velocity and preloading in ball screw drives was presented in [4]. An effort towards thermal error optimization modeling and real-time compensation on a CNC center was proposed by Hao et al. [5]. Robust compensation of elastic deformation in ball screw drives in the machine was reported by Kamalzadeh et al. [6]. An effort towards the thermal issues on CNC machine tools was suggested in [7]. Yang et al. [8] proposed thermal error modeling and compensation for high motorized spindle in CNC machines. A new method based on homogeneous method was described in [9]. Fuzzy based clustering method for thermal error modeling using a thermal sensor was reported by Wang et al. [10]. Thermal displacement and decomposition method for optimization of an ultraprecision machine tool were shown in [11]. A thermal model of a ball screw feed drive system for a machine tool was presented by Min and Jiang [12]. An investigation based on Newton interpolation method for calculation of geometric and thermal error compensation for CNC milling machines was suggested by Wang et al. [13]. A study on heat generation based method for precision ball screw drive system was conducted by Xu et al. [14]. An initiative based on thermal deformation estimation for a hollow ball screw feed drive system was reported by Yang et al. [15]. Design and simulation of the gas-liquid binary cooling system for high-speed ball screw units were proposed by Liu et al. [16]. In the direction of stiffness, Olvera et al. [17] presented an analysis on the tool tip radial stiffness of turn-milling centers and proved its validity. Brecher and Witt [18] reported an interactive analysis of structure mechanic behavior of machine tools. Li et al. [19] studied reliability evaluation of NC machine tools considering working conditions. Sued and Pons [20] highlighted the dynamic interaction between machine, tool, and substrate in bobbin friction stir welding for CNC machines. For the heavy CNC machines, rotation through the idea of rack and pinion is avoided and ball screw system is used instead. This is due to the lower speed in rack and pinion mechanism as compared to ball screw systems. We focused on the critical speed parameter for our investigations. The critical speed of the shaft may be referred to as the maximum speed of shaft over and above which failure of the shaft could be occurred. Critical speed of the shaft remains different and depends on the calculation method. There are four major methods for supporting assembled shafts, namely, (i) fixed-fixed, (ii) fixed-free, (iii) fixed-supported, and (iv) supported-supported. We used the fourth method (i.e., supported-supported method) for our analytical investigations. The motivation behind the research work initiates from the frequent failure of the shafts at higher revolutions. The accurate critical speed of shafts remains the top priority for the performance assessment of CNC machines. An optimal speed of the shafts enhances the performance of the overall system whereas the strength of CNC machining system may be dependent on the same. Specific speed of a shaft may give the best result for a single instance, but we have to deploy such an efficient critical speed that provides optimal results in speed evaluations. The improper speeding strategy may change the behavior of shafts resulting in an overload of the entire system. This strategy can consume more resources in terms of both energy and computation resulting in the entire system performance degradation. There always remains dire influence of critical speed assessment on the entire operating environment when evaluating a specific speed of shafts of CNC systems. The goal remains there is to carefully choose and examine the speed for shafts and present an optimal result without compromising any constraints than expected outcome. Therefore, a typical investigation should be required to access the critical speed of shafts for CNC machines. In this paper, a well-defined approach is suggested to calculate the initial critical speed of the shaft which serves as an integral component of the ball screw system.

The rest of the paper is organized in the following sections. Section 2 reported the critical speed based computation method for ball screw systems. Section 3 presented the problem definition and system model. Section 4 describes the detailed design of our experimental setup. Analytical results and validations are presented and discussed in Section 5. Finally, conclusions are made in Section 6.

#### 2. Proposed Model for Critical Speed Calculation

This section represents the motivations along with mathematical equations for critical speed calculation. We used the following notions to calculate the critical speed of the shaft. The methods given in our proposal are applicable for shaft supporting at two points only and for the first critical speed. The higher critical speeds and the critical speeds of shafts supported at more than two points are generally high to exclude them from consideration. Let Ma denote the moment of area of cross section in bending (mm^{4}); SL represents the length of shaft (mm), CS shows the critical speed (rpm), Wt depicts the weight of shaft per unit length (kg/mm), and exhibits deflection of the shaft (mm). Practically, the following two cases may arise.

##### 2.1. First Case

For a shaft of the almost uniform cross section and the gears mounted on it are of negligible weight compared to the weights of shafts [21], then the first critical speed (CS) is given bywhere denotes constant for different shaft supports, namely, cantilever, simple supported and fixed, and so forth. We assumed the steel shaft with parameter as = 21 × 10^{3} kg/mm^{2} and = 9810 mm/sec^{2}. Ma for a different shaft cross section can be obtained from shaft calculation standard.

##### 2.2. Second Case

For a shaft of negligible mass and having weights on it, the first critical speed [21] is given bywhere are the static deflections of the shafts at the weights. If the weight of the shaft is considerable, then it is divided into several parts (a number of which are dependent on designer discretion). The weight of each part is lumped at a point and added to the external weights. Then, as before the static deflections of the shaft at the points of action of the lumped weights can be found out and the critical speed can be determined from the above said formula. The same procedure can be adopted to find out the critical speed of a shaft with varying cross section under its own weight.

##### 2.3. Critical Speed Calculation

The critical speed of the shaft under its own weight and the gears weight is found as follows [21]. We assumed that the shaft is simply supported and gear hubs do not add flexural rigidity to the shaft. We followed the following steps to calculate the critical speed of the shaft. (i) The weights of the gears and different portions of the shaft are found out. (ii) The bending moment due to the weights and the second moment of area in bending are calculated at different sections and the M/EI diagram for the shaft is constructed.With the help of the above two steps on the ME/I diagram, the funicular polygon is constructed. The pole distance H1 is arbitrary. By drawing lines parallel to those in the funicular polygon, the slope diagram is constructed. A second funicular polygon is constructed from the slope diagram taking an arbitrary pole distance H2. By drawing lines parallel to those in the second funicular polygon, the deflection diagram is constructed. The line joining the intersections of the deflection curve with the bearing centerlines gives the zero-deflection line. Parallel to this zero-deflection line, a line is drawn in the second funicular polygon. The line corresponding to this in the slope diagram gives the zero-slope line. The scales of the slope and deflection diagrams are obtained and shown in Section 6.

#### 3. Problem Definition and System Model

When the speed of rotation approached high level the shaft may resonate and eventually become unable to operate due to the natural frequency of the shaft. Therefore, it becomes necessary to strengthen shaft speed limit or run the shaft up to specified critical speed. Over and above this limit, the shaft may be unable to operate. In our analysis, a shaft simply supported at both ends with gears mounted over has been taken. Accordingly, for a given feed drive system, we are interested in finding the following two problems: (i) what is the influence of weight and deflection cycle on the performance of the feed drive system and (ii) how to calculate the critical speed of shaft in a feed drive system with comparative analysis of weight versus deflection cycles. We used the mathematical model based on the above-mentioned equations (1) and (2) for our investigations.

#### 4. Detailed Setup

The following assumptions have been incorporated in our evaluation model. We have taken ball screw system with shaft length 500 mm supported at eight points. The shaft support points are at 50 mm, 100 mm, 170 mm, 240 mm, 310 mm, 380 mm, 440 mm, and 500 mm, respectively. We applied load (kg) ranging from 0.6 to 1.0 at point 50 mm, from 6.1 to 10.5 at point 100 mm, from 4.2 to 5.7 at point 170 mm, from 4.25 to 5.75 mm at point 240 mm, from 4.2 to 5.7 mm at point 300 mm, from 4.25 to 5.75 mm at point 380 mm, from 13.2 to 21.59 mm at point 440 mm, and from 3.00 to 3.71 mm at point 500 mm. The summarization of the parameters of our proposed model is given in Table 1.