Improved Stiffness Modeling for An Exechon-Like Parallel Kinematic Machine (PKM) and Its Application

Hole drilling or contour milling for the large and complex workpieces such as automobile panels and aircraft fuselages makes a high combined demand on machining accuracy, stiffness and workspace of machining equipment. Therefore, a 5-DOF (degrees of freedom) parallel kinematic machine (PKM) with redundant constraints is proposed. Based on the kinematics analysis of the parallel mechanism using intermediate variables, the kinematics problems of the PKM are solved through equivalent kinematics model. The structural stiffness matrix method is adopted to model the stiffness of the parallel mechanism of the PKM, where the stiffness of each joint and branch component is obtained by stiffness formula and finite element analysis. And the stiffness model of the parallel mechanism is improved by correction coefficient matrix, each element of which is constructed as a polynomial function of three independent end variables of the parallel mechanism. The terminal stiffness matrices obtained by simulation result are used to determine the coefficients of polynomial function by least square fitting to describe the correction coefficient over the workspace of the parallel mechanism quantitatively. The experiment results prove that the modification method can greatly improve the stiffness model of the parallel mechanism. To enhance the machining accuracy of the PKM, the proposed kinematics model and the improved stiffness model are utilized to optimize the working stiffness of parallel machine by searching the best relative position of parallel machine and workpiece. A plate workpiece taken as example is examined in the case study section, which demonstrates the effectiveness of optimization method.


Introduction
The parallel kinematic machine (PKM) is composed of parallel mechanism and series mechanism, which have both the characteristics of these two types of mechanism. Therefore, compared with the conventional industrial robot, the PKM has more advantages in material removal applications, which require higher stiffness and precision of machining equipment in a relatively large workspace than other applications, such as feeding, welding and printing.
parallel mechanism with redundant actuation and found that v-SVM was the most efficient algorithm.
As an effective way to evaluate the performance of PKM, stiffness analysis is usually separated into the analysis on terminal stiffness of parallel mechanism and joint stiffness of series mechanism [10][11][12][13]. Bi et al. [14] used finite element method and structural stiffness matrix to solve the terminal stiffness of Exechon parallel mechanism. Dumas [15] introduced a general method for calculating the stiffness of any 6-DOF series robot by fining out its joint stiffness.
Based on the stiffness analysis, the stiffness model can be transferred into computer algorithms for applications on mechanical design and machining. Fan et al. [16] related to the design of PKM for optimal static stiffness using computer simulation. He et al. [17] proposed a new stiffness orientation method, which was used to optimize milling path and improve stability of the robotic milling system. Li et al. [18] used robot stiffness model and dynamic milling force model to optimize the cutter path and clamping position in robotic milling process.
In this paper, a new type of redundant constrained PKM is proposed, and its kinematics and stiffness are studied in detail. Section 2 analyzes the structure of the PKM. Section 3 introduces its kinematics solution. The improved stiffness model of the parallel mechanism is established in Section 4. The following section shows the effectiveness of the improved stiffness model and analysis on the stiffness of the parallel mechanism. Section 6 develops an application of the kinematics model and the improved stiffness model to improve the machining accuracy of the PKM. In Section 7, some findings of this research are concluded.

Structure of PKM
As shown in Figure 1, the PKM with redundant constraints is composed of a base, a fixed platform, three limbs, a moving platform, two rotary joints and a spindle. Limb1 and limb2 are two symmetrical linear motion chains, which are connected with the fixed platform at one end via a Hooke hinge, and with the moving platform at the other end via a rotary pair. The third linear motion chain limb3 is connected to the fixed platform in the form of a rotary pair and to the moving platform via a spherical pair. The two rotary joints are mounted in series on the moving platform of the parallel mechanism, the rotary axes of which are perpendicular to each other. The spindle is mounted on the end of the PKM via a flange, which serves as the end-effector to drive the milling cutter.
As an important feature of this new PKM, the parametric model of the parallel mechanism is shown in Figure 2, where B 1 , B 2 and B 3 are the junctions of limb1, limb2, limb3 and fixed platform, respectively; A 1 , A 2 and A 3 are the junctions of limb1, limb2, limb3 and moving platform, respectively. The joint variables q i (i=1, . . . , 3) of three branches represent the lengths of lines   where M is the number of DOF of the mechanism; n is the number of the rigid bodies in the mechanism, g is the number of joints; and f i is the number of DOF for joint i.
Without consideration of the redundancy of constraints in the proposed the parallel mechanism, its DOF is equal to 1 according to Eq. (1), which should be adjusted to 3 by analyzing the extra DOF caused by redundant constraints [6,7]. And then DOF of the whole PKM amounts to 5, counting 2 DOF of two rotary joints mounted on the end of the parallel mechanism.
There are only 6 passive pairs in the proposed PKM less than those in Tricept mechanism, which is beneficial to the decrease in motion error caused by passive pairs clearance and the practical application of PKM [19]. The kinematic pairs in Exechon mechanism which connect limb3 to the fixed platform and to the moving platform are interchanged in the proposed PKM, which makes it possible to use one-piece precision spherical pair instead of three rotation pairs and thus avoid the assembly error.

Kinematics Modeling
In this paper, the kinematics analysis of the PKM is carried out by solving the equivalent kinematics model. Here, the parallel mechanism is regarded as a joint of the PKM and then it is equivalent to a 3-joint series mechanism. The first step of kinematics analysis is to establish DH model for the 3-joint series mechanism equivalent to the PKM. And then the kinematics analysis of the parallel mechanism of the PKM is discussed in detail to obtain the kinematics model of the PKM.

Kinematics Model of the PKM
The position and pose matrix T h and T p of the PKM and the parallel mechanism in coordinate system B-xyz are solved by xyz and zyx Euler angles respectively.
The position and pose variation matrices T s1i and T s2i (i = 1,2) of two series joints can be obtained by establishing standard DH model according to the parameters listed in Table 1, where β and α are the amounts of rotation around z and x axes, respectively; d and b are the amounts of movement along z and x axes, respectively [20].
And then position and pose matrix T h of the PKM can be calculated by Eq. (2) according to the principle of coordinate transformation: By multiplying the inverse matrix of T s22 and T s21 on both sides of Eq. (2), the joint variables of the series mechanism and the end variables of the parallel mechanism can be obtained by letting the corresponding elements of matrix on both sides of the equation equal to each other. According to the end variables of the parallel mechanism, the inverse kinematics of the parallel mechanism is analyzed. And thus, the inverse kinematics solution of the PKM is achieved.

Kinematics Model of the Parallel Mechanism
To solve the kinematics model of the PKM, the kinematics model of the parallel mechanism is solved by the method of intermediate variables to determine its position and pose matrix T p .
Through the analysis on the structure of the parallel mechanism, it can be known that the direction of u axis of coordinate system A-uvw is perpendicular to the directions of y axis of coordinate system B-xyz and vector A 1 B 1 ; the direction of y axis of coordinate system B-xyz is perpendicular to the direction of vector A 3 B 3 . According to these constraint conditions, Eq. (3) is shown as below, which indicates that the workspace of the parallel mechanism is a plane: As shown in Figure 3, three intermediate variables are designed here through the analysis of the parallel mechanism, which include distance L between points A and B,

Kinetostatic Modeling
The stiffness modeling of PKM includes the stiffness modeling of parallel mechanism and series mechanism. The paper focus on the stiffness modeling of parallel mechanism, because the stiffness of series mechanism has little impact on the stiffness of PKM [14]. And PKM has different forms of series mechanism for different applications, it is not meaningful to study the stiffness modeling of series mechanism [21]. As for the stiffness modeling of parallel mechanism, the stiffness modeling method for Exechon parallel mechanism is adopted to achieve the basic stiffness model [5,21,22]. In order to improve the accuracy of the basic stiffness model, correction coefficient matrix of the basic stiffness model is solved by regression analysis method to optimize the stiffness model and get the improved stiffness model.

Basic Stiffness Model of Parallel Mechanism
The terminal stiffness matrix of the parallel mechanism is affected by its three branches, each of which includes three parts. Limb1 and limb2 include Hooke hinge U, prismatic joint P and rotary joint R. Limb3 includes rotary joint R, prismatic joint P and spherical joint S. Therefore, it can be determined by analyzing the stiffness of three branches. As shown in Figure 4, the connecting joints in the parallel mechanism are replaced by the springs with equivalent stiffness. And the prismatic joint is regarded as a cantilever beam which is composed by a lead screw connected in parallel with a connecting rod. The fixed platform and the moving platform are regarded as rigid bodies. Thus, the terminal stiffness matrix of the parallel mechanism K p can be obtained without considering the influence of frictional force and damping force between the connecting members.  To solve the stiffness of the parallel mechanism, the stiffness of each joint is solved firstly by finite element analysis and structural stiffness analysis [21], which can be expressed as Eq. (7): where subscript l represents the link of each branch; subscript r represents the rotary joint R; subscript u represents the Hooke hinge U; subscript s represents the spherical joint S; subscript i represents the number of each branch.
And the values of k rui , k uui , k uvi , k su , k sv and k sw are zero.
Based on the above analysis of joint stiffness of each branch, the terminal stiffness matrix of the parallel mechanism can be obtained by the structural stiffness matrix. The parallel mechanism can be divided into four units, the nodes of which are points A 1 , A 2 , A 3 and A. Hence, the structural stiffness matrix K of the parallel mechanism can be expressed as Eq. (8): where K ii (i = 1, . . . , 4) is the stiffness of four nodes; K 4i (i = 1, . . . , 3) is the coupling stiffness relating the first three nodes to the fourth node; K i4 (i = 1, . . . , 3) is the coupling stiffness relating the fourth node to the first three nodes.
The elements K ii (i = 1, . . . , 4) in structural stiffness matrix K are acquired through the analysis on force relation and displacement relation between the first three nodes A 1 , A 2 , A 3 and the fourth node A, and the deformation compatibility conditions of the parallel mechanism. The specific steps for solving K ii is not listed here, which can be found by the stiffness modeling of Exechon PKM [5,21,22].
It can be found that structural stiffness matrix K is non-diagonal, which indicates that the terminal stiffness of the parallel mechanism is effected by the stiffnesses of three branches. The terminal stiffness matrix K p of the parallel mechanism in coordinate system A-uvw can be determined by flexibility matrix [21]: 6×6 represents the last 6 × 6 block of the inverse matrix of K.

Improved Stiffness Model of the Parallel Mechanism
In order to improve the stiffness model of the parallel mechanism, the correction coefficient matrix is introduced, each element of which is a function of three independent end variables of the parallel mechanism. Based on the stiffness data of simulation result, the polynomial function is constructed to fit the correction coefficient of stiffness calculated by stiffness model, which establishes the basis of the improved stiffness model. The construction method is presented in detail and verified by its good effect on improving the precision of stiffness model.
Because the diagonal elements in the stiffness matrix are the principle stiffness values, the non-diagonal elements are the coupled stiffness values, so we only analyze the principle stiffness values for content limitation [21]. The correction coefficient matrix C p is defined as a diagonal matrix shown in Eq. (10) accordingly. Then the improved stiffness matrix K m can be acquired by calculating the dot product of correction coefficient matrix C p and stiffness matrix K p obtained by stiffness model.
Each diagonal element c pii (i = 1, . . . , 6) of correction coefficient matrix C p can be expressed by a polynomial function of three independent end variables θ , σ and Z 0 of the parallel mechanism.
The terminal stiffness matrix K a of the parallel mechanism obtained by stiffness measurement experiment [23] or finite element analysis [24] is regarded as the improvement goal of stiffness model. In order to acquire the stiffness matrices of the parallel mechanism at a series of position and poses, an orthogonal experiment is conducted. The orthogonal experiment is designed by using the first three columns of L 49 (7 8 ) orthogonal experiment table to divide three variables θ , σ and Z 0 into seven levels, which can reduce the complexity of the experiment and also characterize the workspace of the parallel mechanism. To cover the workspace as much as possible, the levels of each variable can be distributed as Table 2.
According to the orthogonal experiment, the terminal stiffness matrix of the parallel mechanism K p and K a at each position and pose of orthogonal experiment can be acquired by stiffness model and finite element analysis, respectively. And then correction coefficient matrix C p at these position and poses can be acquired by dividing each element of matrix K a by the corresponding element of matrix K p , which can be used as the raw data of correction coefficient to be fitted. The relation between correct coefficients c pii and three independent end variables are discussed through the qualitative analysis of experimental results firstly, and then the mathematical expression of each correction coefficient c pii with respect to three independent end variables is acquired by using the least squares method to fit the raw data of correction coefficient.
Correction coefficient c p11 is taken as an example to analyze its functional relation with three independent end variables. The data of orthogonal experiment can be divided into 7 groups by the values of variable θ from − 15° to 15°. Figure 5(a) shows the mean of correction coefficient c p11 of each group, which indicates an approximate quadratic function relation between correction coefficient c p11 and variable θ . Similarly, a quadratic function relation between correction coefficient c p11 and variable σ and a linear function relation between correction coefficient c p11 and variable Z 0 are found through analyzing Figure 5(b) and (c).
Similarly, through the analysis on the rest main diagonal elements of correction coefficient matrix, it can be found that all the diagonal elements c pii have the quadratic function relation with variables θ and σ , and the linear relation with variable Z 0 . Therefore, the vector of correction coefficients c pii can be expressed by Eq. (11): In each group of orthogonal experiment, one variable keeps unchanged while the other two variables are assigned seven different combinations of values. When the combination of values of the rest two variables has an obvious effect on the relation between the correction coefficient and the first variable, the correction coefficient cannot change with the first variable in a certain regular pattern. Therefore, the combined items of any two variables in Eq. (11), which have less influence on the correction coefficient, can be ignored to simplify the fitting function.
The relation between correction coefficient c p11 and three independent end variables θ , σ , Z 0 are shown in Figure 6. The data with the same marker in each subFigure come from the experiments with the same value of the corresponding variable. It can be seen from Figure 6(a) and (c) that correction coefficient c p11 changes regularly with variables θ and Z 0 . But the relation between correction coefficient c p11 and variable σ shown in Figure 6(b) is irregular. Therefore, the combined items of variables θ and σ , variables σ and Z 0 play a very small role in the fitting function, which can be negligible by setting their coefficient to zero. The combined items of variables θ and Z 0 has such a marked impact on correction coefficient c p11 that it cannot be ignored in Eq. (11).
Similarly, through the analysis on the other main diagonal elements of the correction coefficient matrix, it can be found that the influence of combined items of variables θ and σ and variables θ and Z 0 are much smaller than that of variables σ and Z 0 on correction coefficients c p22 , c p33 and c p66 . And the combined item of variables θ and Z 0 plays a more important role on the fitting function of correction coefficient c p44 than that of variables θ and σ , and variables σ and Z 0 . The combined items of any two variables all have little impact on correction coefficient c p55 .
Therefore, the fitting functions of correction coefficients c pii (i = 1, · · · , 6) about three independent end variables can be expressed as Eq. (12): The coefficients e ij (i = 1, . . . , 6, j = 1, . . . , 9) in the above equation can be evaluated by least square fitting based on 49 sets data of orthogonal simulation experiments. Thus, the quantitative functional relations between six main diagonal elements of correction coefficient matrix and three end variables are obtained, which are used to correct the linear stiffnesses and torsional stiffnesses along x, y and z axes in coordinate system A-uvw of the end of the parallel mechanism at different position and poses.

Verification and Analysis on Stiffness of the Parallel Mechanism
As an important performance of PKM, stiffness should be fixed attention on especially in mechanical machining. In order to further apply the improved stiffness model, it is necessary to verify the accuracy and also study the stiffness distribution of parallel mechanism in the workspace.

Verification of Improved Stiffness Model
The verification of improved stiffness model includes two parts: the effectiveness of fitting correction coefficient in improving the accuracy of basic stiffness model; the accuracy of improved stiffness model by comparing with the stiffness obtained by ANSYS finite element simulation.
To evaluate the effect of correction coefficient matrix on the improvement of basic stiffness model of the parallel mechanism, verification experiment is conducted at more position and poses to achieve richer experiment data for regression analysis. Besides the 49 position and  poses of orthogonal experiment, the additional 25 position and poses of the parallel mechanism which cover its workspace as widely as possible are selected to calculate the end stiffness matrices K p , K m and K a by the basic stiffness model, the improved stiffness model and finite element analysis, respectively. Correction effect matrix ME, defined as Eq. (13), is introduced to evaluate the correction effect of correction coefficients c pii (i = 1, . . . , 6) quantitatively. If the values of me ii are positive, it indicates that the stiffness from improved stiffness model is closer to the stiffness obtained by ANSYS finite simulation than the one from basic stiffness model. The larger the value of me ii is, the better the correction effect of correction coefficient.
where k ii p , k ii m , k ii a are the main diagonal elements of stiffness matrices obtained by basic stiffness model, improved stiffness model and finite element analysis, respectively.
As listed in Table 3, if correction effect me ii ranges from 0.9 to 1, the correction effect of correction coefficients c pii is satisfactory; if correction effect me ii ranges from 0.6 to 0.9, the correction effect is acceptable; if correction effect me ii ranges from 0 to 0.6, the correction effect is poor.
According to Table 3, the minimum of correction effect me ii is equal to 0.32, which proves that the modification method can effectively decrease the differnce between the stiffness obtained by basic stiffness model and finite element analysis. By comparing the mean and distribution of correction effect me ii in orthogonal experiment and verification experiment, it can be seen that the correction effect in verification experiment is not as good as that in orthogonal experiment. It is due to the relatively small number of (13) ME = diag[me 11 , me 22 , me 33 , me 44 , me 55 , me 66 ], position and poses selected in orthogonal experiment to characterize the entire workspace of the parallel mechanism resulting in the relatively poor fitting precision of correction coefficient at the position and poses in verification experiment. Therefore, the correction effect can be obviously enhanced by appropriately increasing the number of level in orthogonal experiment to obtain the high-precision fitting correction coefficient. In order to verify the accuracy of improved stiffness model, the relative errors of main diagonal elements of improved stiffness model re ii (i = 1, . . . , 6) are defined as Eq. (14). The closer to zero the values of re ii is, the more accurate the improved stiffness model.
The values of re ii can be solved through the analysis on experimental data obtained by orthogonal experiment and verification experiment, which are shown in Table 4. The means of relative errors are all smaller than (14)   10%, which indicates that the improved stiffness model is accurate enough to describe the stiffness of the parallel mechanism in the mass. Through the analysis on standard deviation, maximum and minimum of re ii , the deviation of re 22 is relatively large. It indicates that the improved stiffness model doesn't describe the liner stiffness along y axis in coordinate system A-uvw as effectively as others.

Analysis on the Stiffness of the Parallel Mechanism
To visualize the stiffness of the parallel mechanism, the distribution of stiffness over its workspace is calculated based on the improved stiffness model and then plotted. It can be seen from the kinematics analysis that the workspace of the parallel mechanism is a plane Y 0 =0, which is xz plane of coordinate system B-xyz. The distribution of the main diagonal elements of stiffness matrix over the workspace is shown in Figure 7.
By comparing the distribution of stiffness k m 11 , k m 22 and k m 33 , it can be seen that the linear stiffness of the parallel mechanism is relatively large in area X 0 ∈ [− 400, − 200], which is located at the extreme position and pose of workspace. When X 0 keeps fixed, the linear stiffness of the parallel mechanism decreases with the increment of Z 0 . The value of k m 33 is about one order of magnitude higher than that of k m 22 and k m 33 , which indicates that the linear stiffness along z axis of coordinate system A-uvw of the parallel mechanism is the highest and the linear stiffnesses along x and y axes are similar in value.
By  Figure 7, the linear stiffnesses of the parallel mechanism is much better than its rotational stiffnesses so that the parallel mechanism can sustain greater forces in the directions of x, y and z axes of coordinate system A-uvw rather than moments around x, y and z axes.
In the application of PKM in machining, the working stiffness in which the stiffness of parallel mechanism plays a key role is usually taken into account for the good machining quality. Therefore, according to the characteristics of stiffness distribution, the working stiffness of PKM in its application can be improved by optimizing its working position and pose. For example, in the robotic machining, the flange or fixture used to install the motorized spindle into the end of robot can be designed to ensure that the main force is applied along z axis of parallel mechanism, which can reduce the influence of deformation on the machining precision [25]. Moreover, the external axis also can help to optimize the machining position and pose of PKM for higher working stiffness. The following section presents the application of improved stiffness model to optimize the relative position of the workpiece and the PKM via external axis for the improvement of working stiffness of the PKM.

Application of Improved Stiffness Model
In order to expand the workspace of PKM for the machining of large-scale workpieces, the additional machinery are usually integrated into the machining system as the external axes of PKM [26][27][28][29][30][31]. However, there are few researches on the control and planning of movement of additional machinery which is generally determined by manual work according to the on-site teaching. Therefore, based on the improved stiffness model and the kinematics model, a way to find the most appropriate position of the additional machinery which makes the best working stiffness of the PKM is proposed.

Optimization Algorithm on Position of Additional Machinery
The external axes of PKM can be the linear axis along x, y or z axis of world coordinate system, the rotation axis around x, y or z axis of world coordinate system or any combination of them. However, too many external axes will increase the cost and difficulties in control of machining application. Therefore, the common additional machinery used to expand the workspace of PKM include: the cross slide table [26][27][28] providing two external linear axes; both the positioner [29,30] and the slewing platform [31] providing an external rotation axis. Taking the cross slide as an example, the most appropriate position of the additional machinery which makes the best working stiffness of the PKM can be determined by the following steps. (1) Establish four coordinate systems.  where i is the number of machining position and poses; T W B is the transformation matrix of coordinate system B-xyz relative to the world coordinate system W-xyz; T W U (dx, dy) is the transformation matrix of the worktable coordinate system U-xyz relative to the world coordinate system W-xyz.
Min(C(dx, dy)) =  To facilitate the motion control of cross slide table, it is necessary to convert the optimal position (dx, dy) of worktable in world coordinate system W-xyz into that in cross slide table coordinate system C-xyz by coordinate transformation.

Case Study
To verify the optimization method mentioned above, the plate workpiece shown in Figure 8 is taken as an example where there are two series of holes distributed in areas A and B respectively. The cross slide table drives the workpiece to let every series of holes to be machined enter the workspace of the PKM one after another. Thus, the movement of cross slide table is optimized to determine the relative position of the workpiece and the PKM which always makes the best working stiffness.
In the optimization, the values of objective function C (dx, dy) for areas A and B keep decreasing, which indicates the growing working stiffness for machining two series of holes. The improvement of working stiffness is described by the ratio Q of the difference between the optimized stiffness and the maximum stiffness to the difference between the lowest stiffness recorded during the optimization and the maximum stiffness. If the value of ratio Q is less than 1, the working stiffness is improved.
The smaller the value of ratio Q, the better the optimization efficiency. The average value of ratio Q of six stiffnesses of machining trajectory in area A is 0.73 and that in area B is 0.74, which indicates that the optimized working stiffness comes much closer to the maximum stiffness. The best positions (dx, dy) of the worktable for machining two series of holes in areas A and B are (− 176, 300) and (− 152, − 136), respectively. The great difference between two best positions demonstrates the significance of the proposed optimization method in enhancing the working stiffness of the PKM. By comparing the data listed in Table 5 with the distribution of stiffness over the workspace of the parallel mechanism shown in Figure 7, it can be seen that all the values of stiffness k m 11 , k m 22 , k m 33 , k m 44 and k m 66 after optimizing the position of worktable concentrate near their maximal values except the values of stiffness k m 55 . When the worktable locates at position (− 176, 300) in W-xyz, the PKM drills holes 1 to 4 with the position variable X 0 of the parallel mechanism ranging from − 400 to − 200, where other than stiffness k m 55 almost any other stiffness is relatively high. It conforms with the finding discussed in Section 5.2. When the worktable locates at position (− 152, − 136) in W-xyz, the PKM drills holes 5 to 7 with the position variable X 0 of the parallel mechanism ranging from − 210 to − 150, where the stiffness is a little poorer. It is because the disturbed holes 5 to 7 cannot be drilled together by the PKM with the position variable X 0 of the parallel mechanism ranging from − 400 to − 200. Therefore, a series of suboptimal positions of the parallel mechanism is found, which ensures the best working stiffness of the PKM when the series of holes in area B is machined without moving the worktable. This case proves that the proposed optimization method can solve the best position of worktable to obtain the highest working stiffness of the parallel mechanism and also ensure the machining trajectory in the workspace of the PKM.

Conclusions
The studies on kinematics modeling and stiffness modeling of a novel 5-DOF PKM with redundant constraints are conducted, which promote the theoretical research method of the PKM and improve its application in the field of machining.
(1) To facilitate the study on kinematics, the parallel mechanism of the PKM is transformed into a joint of the PKM, which is equivalent to a 3-joint series mechanism. The kinematics analysis is firstly carried out on the equivalent series mechanism of the PKM and then on the parallel mechanism. (2) Correction coefficient matrix is introduced to improve the basic stiffness model of the parallel mechanism. Based on the data from orthogonal simulation experiment, the qualitative relation between correction coefficients and three independent end variables of the parallel mechanism is described by polynomial fitting function. The results of verification experiment prove the effectiveness of the modification method on improving the precision of main diagonal elements of stiffness matrix over the workspace of the parallel mechanism. (3) Through the research on the application of kinematic model and improved stiffness model of the parallel mechanism in the field of machining, the working stiffness of the PKM is optimized by searching the best relative position of the PKM and workpiece to be machined for improving the machining accuracy.

Table 5 Stiffness and position variables of the parallel mechanism for drilling each hole when the worktable locates at the optimal position
No. of holes k m