購買設(shè)計請充值后下載，，資源目錄下的文件所見即所得，都可以點開預(yù)覽，，資料完整，充值下載可得到資源目錄里的所有文件。。?！咀ⅰ浚篸wg后綴為CAD圖紙，doc,docx為WORD文檔，原稿無水印，可編輯。。。具體請見文件預(yù)覽，有不明白之處，可咨詢QQ:12401814
Numerical design of a new forging press drive incorporating non-circular gears
Abstract: Manufacturing processes as well as products have to be improved continually to meet all the requirements of international competition. Along with economic demands，changing consumer and environmental legislation lead to increased pressure for new and advanced products and processes. Consequently，the forging industry continually tries to improve hot forging processes. Precision hot forging technology，used for the production of connecting rods，bevel gears，straight planet gears，helical gears clutch gearing or constant velocity joints，has been improved constantly [1-3]. Precision forging is carried out with closed dies in order to guarantee the continuous quality of the workpiece and to avoid possible damage to the forged parts by clipping or piercing operations. Many variables influence the quality of the final product and the economics of the Process，especially the workpiece temperature，the die temperature and the pressure dwell time. High workpiece temperatures lead to high temperatures on the surface of the dies. Therefore，the temperature load depends directly on the pressure dwell time. Excessive temperature loads inevitably lead to damage of the dies [4]. This article presents a numerical study of a new press concept using non-circular gears in the drive mechanism. The new press kinematics result in a reduced pressure dwell time in comparison with a conventional press kinematics.
Keywords: metal forming; finite element simulation; thermal die loading; drive mechanism; non-circular gears .
NOTATION :
a
center distance
a,b
coefficients of Fourier series
A
surface area of the die
C
quality of the transmission function regarding kinematic demands
e
distance between the center and the pivot of an eccentrically mounted circular
transition ratio as a function of the driving angle
n
number of the cycle
flux
Q
quantity of heat
pitch curve radius of the driving fear as a function of the driving angle
pitch curve radius of the driven gear as a function f the driving angle
R
radius of a circular gear
s
ram stroke
Tdie
local temperature of the tool
Twp
local surface temperature of the workpirce
D
slide velocity
x
record of Fourier coefficients
αtr
heat transmission coefficient
Γ
cycle time
φ
angle of the driving gear
ψ
angle of the driven gear
1. PRECIDION FORGIN
Owing to its working principle and the higher accuracy of parts-die hot forging calls for higher requirements on process parameters and tool technology. Figure 1 shows the concept of the closed-die forging of a helical gear wheel. Closed-die forging is mostly used for the manufacturing of near net shape or additional closing elements close the die during the deformation, to operate the closing elements, multi-acting presses, spring assemblies or separate closing devices are needed to provide the necessary closing pressure.
Divided dies or additional closing elements are needed if the punch is not able to close the die because of radial form elements such as helical gearings. Horizontally divided dies have the advantage that the closing load can easily be provided by the ram movement combined with spring assemblies. Vertically divided dies, which are necessary for the ejection of parts with undercuts such as clutch gearings or constant velocity joints, need special devices for the transformation of vertical press loads into horizontal closing loads when used in s single-acting press .an alternative is the multicasting press, which is already used for thixoforming and hydroforming, although the ram velocity is often not fast enough for use in hot forging processes
The quality of the precision forged arts reaches the ISO standard IT 7-9. Typical forging temperatures are between 1100 and 1280 for steel materials.
2. NEW PRESS CONCEPT IN PRECISION FORGING
An increasing number of precision forging applications of conventional forging machines particularly for requirements such as reliable closing of the dies, short pressure dwell, constantly energy distribution, overload protection and process integrated quality control. New concepts in hot forging machines are being developed continually. Based on the technological requirements for economic precision hot forging processes, IFUM has developed an innovative press concept [5,6]. The concept is based on a mechanical press with non-circular fears in the drive mechanism to guarantee minimum pressure dwell time and, by this a lower thermal tool load.
2.1 Optimization of the ram kinematics for the precision forging press
Figure 2 shows the calculated optimized kinematics of a precision forging press in comparison with a conventional crank drive. The cycle time of both press drives is 1.0s, whereas every second stroke is an idle one in order to prolong the cooling time. With a forming section of 20mm, the resulting pressure dwell time of the conventional drive is 75ms. By using non-circular gears, it is decreased to 39ms.
The varying transmission ratio, , of the non-circular gears [5] causes a non-uniform angular velocity, , of the crankshaft, a decreased ram velocity, within the upper stroke area and an increased one within the forming area. The variable pitch curve radii, and , of the non-circular gears are determined by the required course of the transmission ratio i and therefore the ram kinematics:
with a given constant center distance:
a = constant =
the transmission function describes the relation between the pitch curves of the non-circular gears.
In order to fulfill the requested demands on the ram kinematics, (Fig.2), the transmission function of the non-circular gears has to be suitably adapted. This function is determined as a Fourier series with a limited number, M, of harmonic waves:
In order to determine the Fourier coefficient record so that the resulting ram kinematics fits the demands, an iterative genetic algorithm has been realized(Fig.3) .
Firstly, an initial coefficient record is estimated from the given kinematics demands by regression of s fifth-degree polynomial over all demands and subsequent determination of its Fourier coefficients. By randomized change of single coefficients am and bm and interchange of coefficients, the next generation of N coefficient records ,n = 1,……N is generated. Then, the resulting ram stroke functions, , are determined by means of integration of and the following consideration of the crank drive.
The quality,, of the transmission functions generated by the records is determined by calculation of the difference to the predetermined kinematic demands and several other conditions such as minimization of the ram acceleration. The records with the best quality are selected in order to generate the next generation , of coefficient records by randomized modification. The iteration is stopped when the accuracy of the solution is sufficient, which is indicated by the quality,, of a solution falling below a predetermined value and a simultaneously slow rate of improvement in quality during a certain number of iteration steps.
Figure 4 shows the pair of non-circular gears calculated for the kinematic demands shown in Fig. 2. Since the angular velocity is variable owing to the changing transmission ratio. The course of the slide velocity as an important parameter for the wear of the gears is different for every pair of teeth. In order to obtain a sufficient load-carrying capacity, a module of 20m and a teeth number of 72 have been chosen.
2.2 Optimization of the shape of the non-circular gears
Since the shape of the driving gear is very similar to a circle, it is possible to obtain similar ram kinematics with an eccentrically mounted circular driving gear combined with a driven
gear with a non-circular pitch curve. Such a pair of gears may be more economically manufactured than two gears with non-circular shapes.
The radius, , of an eccentrically mounted circular gear is:
where , R is the radius and e is distance between the center and the pivot of the circle (Fig.5).
The transmission ratio is:
In order to achieve an average transmission ratio of 1 and therefore closed pitch curves with identical circumferences, the condition:
has to be fulfilled [8]. For a given ratio, the center distance has to be determined by solving this nonlinear equation.
Figure 5 shows a pair of gears with an eccentrically mounted driving gear, which realizes similar ram kinematics as the first pair of gears. The ram velocity as well as the acceleration only shows a negligible difference to the original course. Owing to the changed shape and therefore changed circumference of the gears, the center distance for an identical number of teeth and an identical module has changed to 1503.62mm.
In order to simplify the design of non-circular gears for press manufacturers, a PC program has been developed at IFUM. For a given set of kinematics it offers the possibility of calculating the shape of the pitch curves and teeth as well as other parameters including load-carrying capacity and slide velocity.
3 FINITE ELEMENT SINMULATION OF THE THERMAL DIE LOADING
After the design of the press drive, the effects the optimized kinematics on the thermal die loading should be examined. Therefore, finite element simulations have been performed in order to compare the different forming velocities and pressure dwells of a conventional crank drive and this newly proposed press drive.
A survey of the developments in metal forming simulation is given in the literature [9-11], for the prediction or optimization of the material flow; an FE simulation with rigid dies is often sufficient. For estimation of process safety, knowledge of the die loading is required. In this case meshing of the dies with finite elements is also necessary. Some FE packages allow the simulation of forming processes with deformable dies and workpiece. The contact processor couples the boundary and transient conditions between the die and the workpiece. The thermomechanical deformations of the dies and their influence on the material flow can then be considered in a coupled forming simulation. Today, a coupled FE simulation using deformable dies for complex three-Dimensional FE models needs substantially longer CPU (central processing unit) time than with rigid dies. Therefore, the IFUM has developed a software tool that uses an uncoupled calculation of the workpiece and dies with FORGE3 for the mechanical model and MSCMARC for the thermal analysis [12].
3.1 Strategy of an uncoupled FE simulation
At LFUM, helical gear wheels have been formed in s precision forging process. Characteristics for this process are the high local stresses in the die. For this reason, the thermal die loading due to the forging process was investigated by the uncoupled method (fig.6). Firstly, an FE simulation of the forging process was performed with rigid dies. This simulation was performed with the commercial FE package FORGE3. The thermal fluxes into the rigid dies were then determined during this simulation. Subsequent calculation of the thermal die loading was performed with the previously determined external fluxes. The split nodal fluxes are brought on to the meshed dies as boundary conditions. This strategy leads to short CPU times. A previous investigation of a three-dimensional FE simulation of an orbital forging process resulted in s reduction in CPU time of about 50 per cent in comparison with the coupled method [12.].
3.2 FE simulation of the forging process and the thermal die loading
To collect information about the thermal die loading as a result of the hot forging process for both press kinematics, uncoupled FE simulations were executed for the example of a helical gear wheel. In the first step, simulations with rigid dies were performed with FORGE3 for the non-circular and the conventional press kinematics (see fig.2). For both cases, the billet temperature was 1200. The heat transfer coefficient for contact between the two surfaces was constant .
To reduce the CPU time further, only a segment of the helical gear was modeled. Figure 7 shows the material flow and the temperature distribution of the thermomechanical simulation with OFRGE3. Significant differences in temperature can be seen at the top of the tools and at the reliefs. The surface temperature of the conventionally forged part at the end of the forging process is 100-150K lower than for the part that is forged with a non-circular gear drive unit. This effect becomes important when a heat treatment is to be integrated directly after the forging process to make use of the forging temperature. The flux is determined as follows:
where
Q = quantity of heat ;
A = surface area of the die;
During the FE simulation with rigid tools, the fluxes, have to be determined at the surface. In the second step, the calculated heat flow into the lower die is transferred to an FE model with meshed dies. To determine the evolution of heat into the die of more than one forging:
where
;
= local surface temperature of the workpirce;
= local temperature of the tool;
= heat transission coeffient;
= cycle time;
n = number;
In this manner it is possible to simulate the temperature field and include the thermal dilatation of the dies for many forging cycles.
The heat flow into the upper and lower die and from there into the matrix was neglected. The different pressure dwell times of both drive units wee taken into account. The calculated heat flow from the forging simulation was transferred for a total of 36 strokes on to the die.
The simulations were accomplished using the commercial FE package MSC.MARD. The starting temperature pf the die was 100C. Figure 8 shows the simulated temperature distribution of both drive units. Already after 18 forging strokes (36 strokes). Significant differences can be seen between the drive units. In the case of the non-circular gear drive unit, the maximum temperature reached approximately 460C.
The highest temperature for the conventional drive unit was 780C. owing to the shorter pressure dwell time of the non-circular gear drive unit, the amount of heat flow during the forging process was significantly lower than for the conventional drive unit. Further more , heat was conducted away more efficiently as a result of the longer cooling time.
4. CONCLUSION
This article describes how to optimize the design of non-circular gears used in press drives. The required symmetrical ram kinematics means that an eccentrically mounted circular driving gear can be used. Since this gear may be manufactured conventionally, a reduction in manufacturing costs may be possible in comparison with two non-circular gears.
The evolution of the temperature of the workpiece during the forging time can be simulated very easily with the uncoupled simulation tool described. This simulation tool is optimized to reduce the FE simulation time of complex three –dimensional that the workpiece is hotter after the forging process using a press with non-circular gears. This can be very important for the integrated heat treatment. Nevertheless, the thermal die loading of this press is much lower than for the conventional press. Therefore, the thermal damage to the dies is smaller.
In contrast to the conventional press drive unit, the non-circular gear drive4 unit has the following advantages:
（1）The pressure dwell time is reduced significantly;
（2）The time for cooling and handling is longer;
（3）The thermal die loading is lower;
（4）The heat transfer from the workpiece into the dies is lower.