A direct pressure mold clamping mechanism, design method and die casting machine

Abstract

This application discloses a direct-pressure mold-closing mechanism, including a frame, a drive mechanism, and a moving mold plate. The end face of the moving mold plate facing away from the mold-closing direction has multiple drive points along the circumferential direction for drive connection with the drive mechanism. The distance from the drive point to the center of the moving mold plate is less than the distance from the sliding hole to the center of the moving mold plate. A design method for the direct-pressure mold-closing mechanism is also disclosed. A simulation model of the moving mold plate is established, and a set mold-closing force is applied to the simulation model based on the initially estimated extreme value of r, obtaining the deformation at the corresponding extreme point. The simulation results are compared and optimized to obtain the optimal r value. A die-casting machine, including the aforementioned direct-pressure mold-closing mechanism, is also disclosed. By shortening the distance from the drive point connecting the drive mechanism to the center of the moving mold plate, it is equivalent to shortening the lever arm of the bending moment generated by the mold-closing force during mold clamping, thereby effectively reducing the deformation of the moving mold plate and solving the problem of poor fit during mold clamping.

Description

Technical Field

[0001] This application relates to the field of metal die casting equipment technology, and in particular to a direct pressure mold closing mechanism, design method and die casting machine. Background Technology

[0002] A die-casting machine is a machine used for pressure casting, commonly used in the production and processing of automotive parts. For example, it is used in the unibody die-casting process of modern automobiles; die-casting machines can form car bodies under a mold clamping pressure of 13,000 tons.

[0003] The most widely used die-casting machine clamping mechanism is the toggle-type clamping and locking mechanism, also known as the three-plate mechanism. This clamping mechanism mainly relies on a hydraulic cylinder to drive the toggle to bend and extend to complete the mold movement and locking. The reliability of locking mainly depends on the rigidity of the toggle system. Precise positioning is required during locking. The pull rod is generally fixed by a locking nut, and the system structure is complex. Therefore, there are problems such as cumbersome removal of the pull rod when changing the mold, complicated mold adjustment, cumbersome adjustment of the clamping force balance in the pull rod, and long-term use leading to loosening of the locking nut and easy wear of the hinge, resulting in changes in the clamping force, ultimately affecting product quality.

[0004] The direct-pressure mold clamping mechanism eliminates the toggle mechanism, and the locking function is completed by the follow-up locking mechanism at the rear end of the moving mold plate. However, in the existing direct-pressure mold clamping mechanism, the clamping force is applied at the four corners of the moving mold plate, while the clamping position of the moving and fixed molds is located in the middle area of ​​the moving and fixed molds. Therefore, during the mold clamping process, the clamping force at the four corners needs to be transmitted to the mold surface through the mold plate, which requires high strength of the mold surface and results in large deformation of the mold plate during the mold clamping process, which can easily lead to poor fit between the moving and fixed mold plates. Summary of the Invention

[0005] One of the objectives of this application is to provide a direct pressure mold closing mechanism that can reduce the degree of template deformation during the mold closing process.

[0006] Another objective of this application is to provide a design method for a direct pressure mold closing mechanism that can reduce the degree of template deformation during the mold closing process.

[0007] Another objective of this application is to provide a die-casting machine that can reduce the degree of template deformation during the mold-closing process.

[0008] To achieve at least one of the above objectives, the technical solution adopted in this application is as follows: a direct pressure mold closing mechanism, including a driving mechanism and a moving mold plate, wherein the driving mechanism and the moving mold plate are slidably engaged with the frame through sliding holes provided at the four corners; the end face of the moving mold plate facing away from the mold locking direction is provided with a plurality of driving points along the circumferential direction for driving connection with the driving mechanism; the distance from the driving point to the center of the moving mold plate is less than the distance from the sliding hole to the center of the moving mold plate.

[0009] Preferably, if the distance from the sliding hole to the center of the moving template is R, and the distance from the driving point to the center of the moving template is r, then the value of r is 0.4R to 0.8R.

[0010] Preferably, the non-locking surface of the moving template is fixedly provided with an annular support rib; the driving mechanism forms the driving point by connecting with the top of the support rib.

[0011] Preferably, the cross-section of the support rib is circular or polygonal; the top of the support rib is connected to the drive mechanism through a support block to form the drive point.

[0012] Preferably, if the height of the supporting rib is H, then the value of H is 0.8r to 1.5r.

[0013] Preferably, the driving mechanism includes a driving seat that slides with the frame, and four telescopic devices correspondingly installed on the driving seat; the telescopic devices are respectively connected to the moving template to form four driving points, and the driving points are located between adjacent sliding holes.

[0014] A design method for a direct-pressure mold clamping mechanism includes the following steps:

[0015] S100: Establish a simulation model of the dynamic template in the simulation software, and preliminarily estimate the range of values ​​for r;

[0016] S200: Apply a set clamping force to the corresponding position of the simulation model according to the extreme value of the range of r values, and then obtain the deformation of the clamping surface of the moving template at the corresponding extreme point;

[0017] S300: Compare the simulation results of the current step S200 with the simulation results of the previous step S200;

[0018] S400: Based on the comparison results of step S300, optimize the range of r values ​​and incorporate it into step S200 until the optimal r value is obtained.

[0019] Preferably, let the deformations corresponding to the two extreme points obtained from the first simulation in step S200, from largest to smallest, be A1 and A2, respectively, and let the deformation of the traditional moving template during mold locking be A0; then in step S400, if A0 > A1 > A2, the optimal value of r is located at the position where the extreme point corresponding to A2 decreases, or the optimal value of r is located between the extreme points corresponding to deformations A1 and A2; if A0 > A2 > A1, the optimal value of r is located between the extreme points corresponding to deformations A1 and A2, or the optimal value of r is located at the position where the extreme point corresponding to deformation A1 increases.

[0020] Preferably, when A0 > A1 > A2, the extreme point corresponding to deformation A2 is first reduced to obtain a new extreme point r* and substituted into step S200; if the deformation A3 corresponding to the extreme point r* is < A2, it means that the optimal value of r is close to the extreme point r*; otherwise, the optimal value of r is located between the extreme points corresponding to deformation A1 and A2; when A0 > A2 > A1, the extreme point corresponding to deformation A1 is first increased to obtain a new extreme point r** and substituted into step S200; if the deformation A4 corresponding to the extreme point r** is > A1, it means that the optimal value of r is located between the extreme points corresponding to deformation A1 and A2; otherwise, the optimal value of r is close to the extreme point r**; where, let the extreme points corresponding to deformation A1 and A2 be r max1 and r min1 Then the value of the extreme point r* is r. min1 -(0.01~0.05)(r max1 -r min1 The value of the extreme point r** is r. max1 +(0.01~0.05)(r max1 -r min1 ).

[0021] A die-casting machine includes the aforementioned direct-pressure mold-closing mechanism, a frame, and a pair of support components; the lower ends of the drive mechanism and the moving mold plate are respectively engaged with the frame through corresponding support components; when the direct-pressure mold-closing mechanism moves horizontally, the support components are adapted to move synchronously along the frame, thereby providing vertical support for the direct-pressure mold-closing mechanism; when the direct-pressure mold-closing mechanism vibrates, the support components are adapted to elastically extend and retract in the vertical direction.

[0022] Preferably, the support assembly includes, from top to bottom, an upper sliding foot, a lower sliding foot, and a roller assembly; the upper sliding foot is fixedly installed at the lower end of the direct pressure mold closing mechanism, and the roller assembly is installed at the lower end of the lower sliding foot for rolling engagement with the frame; the upper sliding foot and the lower sliding foot are elastically connected by a deformation assembly.

[0023] Compared with the prior art, the beneficial effects of this application are as follows:

[0024] Compared to traditional mold clamping mechanisms, this application shortens the distance from the drive point connecting the drive mechanism to the center of the moving mold plate. This effectively shortens the lever arm of the bending moment generated by the clamping force on the moving mold plate during clamping, thereby effectively reducing the deformation of the moving mold plate and solving the problem of poor fit during clamping. Simultaneously, while ensuring the strength of the moving mold plate, the required material thickness of the moving mold plate can also be effectively reduced. Attached Figure Description

[0025] Figure 1 This is a partial structural schematic diagram of the direct pressure mold closing mechanism in this invention.

[0026] Figure 2 This is a schematic diagram of the drive mechanism in this invention.

[0027] Figure 3 This is a schematic diagram of the axial side structure of the moving template in this invention.

[0028] Figure 4 This is a schematic diagram of the structure of the moving template in the present invention from a top view.

[0029] Figure 5 This is a schematic diagram of the structure of the moving template in the present invention from the front view.

[0030] Figure 6 This is a schematic diagram of the fitting curve of the mold-locking surface deformation of the moving template corresponding to the extreme point in this invention. Figure 1 .

[0031] Figure 7 This is a schematic diagram of the fitting curve of the mold-locking surface deformation of the moving template corresponding to the extreme point in this invention. Figure 2 .

[0032] Figure 8 This is a partial structural diagram of the die-casting machine in this invention.

[0033] Figure 9 This is a schematic diagram of the support component in this invention.

[0034] Figure 10 This is a cross-sectional view of the sliding foot in this invention.

[0035] Figure 11 This is a schematic cross-sectional view of the support component in this invention.

[0036] In the figure: frame 100, guide column 110, tail plate 120, base 130, drive mechanism 200, drive seat 210, first sliding hole 211, telescopic device 220, moving template 300, second sliding hole 310, support rib 320, weight reduction hole 321, support block 322, support assembly 4, roller assembly 41, rotating shaft 411, roller 412, lower sliding foot 42, upper sliding foot 43, deformation assembly 44, connecting pin 441, disc spring assembly 442. Detailed Implementation

[0037] The present application will be further described below with reference to specific embodiments. It should be noted that, without conflict, the various embodiments or technical features described below can be arbitrarily combined to form new embodiments.

[0038] In the description of this application, it should be noted that the directional terms such as "center", "lateral", "longitudinal", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", and "counterclockwise" indicate the orientation and positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. They should not be construed as limiting the specific protection scope of this application.

[0039] It should be noted that the terms "first," "second," etc., in the specification and claims of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence.

[0040] One aspect of this application provides a direct pressure mold clamping mechanism, such as Figures 1 to 3 As shown, one preferred embodiment includes a frame 100, a drive mechanism 200, and a moving template 300. Both the drive mechanism 200 and the moving template 300 are slidably engaged with the frame 100 via sliding holes at their four corners. The end face of the moving template 300 facing away from the mold-closing direction has multiple drive points along the circumferential direction for driving connection with the drive mechanism 200. The distance from the drive point to the center of the moving template 300 is less than the distance from the sliding hole to the center of the moving template 300. Therefore, the drive mechanism 200 applies a mold-closing force to the drive point to drive the moving template 300 to perform mold-closing. Compared to traditional mold-closing mechanisms, by shortening the distance from the drive point connecting the drive mechanism 200 and the moving template 300 to the center of the moving template 300, the lever arm of the bending moment generated by the mold-closing force on the moving template 300 during mold-closing can be effectively shortened, thereby effectively reducing the deformation of the moving template 300 and solving the problem of poor fit during mold-closing.

[0041] Understandably, in traditional direct-pressure mold clamping mechanisms, during mold clamping, the drive mechanism 200 applies clamping force to the moving template 300 through sliding holes along the frame 100. However, during mold clamping, the contact area between the moving template 300 and the mold is smaller than the area formed by the interconnected sliding holes at the four corners of the moving template 300. Therefore, the extremely high clamping force (13,000 tons) applied by the drive mechanism 200 can create a bending moment on the moving template 300 along the edge where the mold and moving template 300 are in contact. This easily leads to an arching of the area where the moving template 300 and the mold are in contact, away from the mold, resulting in gaps between them. This means the mold experiences uneven stress, affecting product quality.

[0042] In traditional direct-pressure mold clamping mechanisms, the moving mold plate 300 is typically thickened to resist deformation. Increasing the thickness of the moving mold plate 300 can improve its bending section modulus. However, increasing the thickness of the moving mold plate 300 will increase production costs and may also lead to an increase in the axial dimension of the mold clamping mechanism.

[0043] In this embodiment, by contracting the force applied by the drive mechanism 200 to the moving template 300 towards the center of the moving template 300, the deformation of the moving template 300 due to the ultra-high clamping force can be effectively reduced. In other words, by keeping the moving template 300 within a specified deformation range, the required thickness of the moving template 300 can be effectively reduced.

[0044] For ease of understanding, such as Figure 4 As shown, the distance from the sliding hole to the center of the moving template 300 can be set as R, and the distance from the driving point to the center of the moving template 300 can be set as r. Then the value of r is 0.4R to 0.8R.

[0045] Understandably, the value of r cannot be too small. A small r value means that the drive mechanism 200 applies a clamping force to the moving template 300 near the center of the moving template 300. This can easily lead to an overly concentrated clamping force applied by the moving template 300 to the mold, which can cause a tendency to lift at the sliding hole where the moving template 300 connects to the frame 100, thus affecting the production quality of the product. Therefore, the lower limit of r is generally preferably 0.4R. The upper limit of r can generally be determined based on the edge of the contact position between the moving template 300 and the mold when they are clamped. That is, when the moving template 300 is in contact with the mold, the distance from the edge of the mold to the center of the moving template 300 is generally between 0.8R and 0.9R. Therefore, the upper limit of r is preferably 0.8R.

[0046] In this embodiment, as Figures 1 to 3 As shown, guide posts 110 are installed at all four corners of the frame 100, and the drive mechanism 200 and the moving template 300 slide with the guide posts 110 through the sliding holes provided at the four corners.

[0047] In this embodiment, as Figure 1 and Figure 2As shown, the drive mechanism 200 includes a drive base 210 and multiple telescopic devices 220. The drive base 210 has first sliding holes 211 at its four corners, allowing it to slide against guide posts 110 on the frame 100. The telescopic devices 220 are evenly spaced along the circumference of the drive base 210. Each telescopic device 220 is connected to the moving template 300 via its output end, and the connection point between the output end of the telescopic device 220 and the moving template 300 is the drive point. Therefore, during mold clamping, each telescopic device 220 can synchronously drive the moving template 300 to slide along the guide posts 110 via its output end to achieve mold clamping. By evenly spaced the telescopic devices 220, the clamping force on the moving template 300 can be ensured to be uniform.

[0048] Understandably, the specific number of telescopic devices 220 can be selected based on the mold clamping force requirements and the installation space of the drive base 210; for example... Figure 2 As shown, the number of telescopic devices 220 is preferably four, so that the driving force applied by a single telescopic device 220 to the moving template 300 is one-quarter of the total mold closing force.

[0049] Specifically, such as Figure 2 As shown, the four telescopic devices 220 are respectively installed between adjacent first sliding holes 211 to facilitate the installation of the telescopic devices 220. Thus, the four telescopic devices 220 can form four driving points located between adjacent sliding holes by connecting with the moving template 300.

[0050] Understandably, in order to facilitate the setting of the drive point, the four telescopic devices 220 can be installed at the midpoint between adjacent first sliding holes 211.

[0051] In this embodiment, as Figure 3 and Figure 4 As shown, the four corners of the moving template 300 are provided with second sliding holes 310 that slide with the four guide posts 110 respectively, and the second sliding holes 310 are axially aligned with the first sliding holes 211. Meanwhile, a ring-shaped support rib 320 is fixedly provided on the non-locking surface of the moving template 300; the drive mechanism 200 is connected to the top of the support rib 320 to form a drive point. The ring structure of the support rib 320 can weaken and cancel the component of the driving force applied by the telescopic device 220 along the non-locking direction, so as to avoid this component force affecting the locking of the mold by the moving template 300.

[0052] Understandably, due to the relatively low machining precision of the non-locking surface of the moving template 300 and the output end of the telescopic device 220, the force-bearing plane of the driving point formed by the connection between the telescopic device 220 and the moving template 300 through the output end is not necessarily parallel to the moving template 300. Consequently, when the moving template 300 is subjected to the clamping force applied by the telescopic device 220, the clamping force may generate a component force in the non-locking direction. If the driving point is directly located on the non-locking surface of the moving template 300, the aforementioned component force will act directly on the moving template 300, causing the moving template 300 to bend or twist, thus affecting the molding quality of the product.

[0053] In this embodiment, an annular support rib 320 is provided on the non-locking surface of the moving template 300. The support rib 320 is connected to the output end of the telescopic device 220 to form the required driving point. Thus, when the clamping force applied by the telescopic device 220 generates a component force in the non-locking direction, the support rib 320 can offset or weaken the bending or twisting caused by this component force through corresponding deformation. Furthermore, the annular shape of the support rib 320 means that the component forces generated by different telescopic devices 220 at the driving point may cancel each other out, further reducing the deformation effect on the moving template 300.

[0054] In this embodiment, as Figure 3 and Figure 4 As shown, the cross-section of the support rib 320 can be circular or polygonal; that is, the support rib 320 can be annular, or the support rib 320 can be connected by polygons to form an annular shape.

[0055] In this embodiment, as Figure 3 and Figure 4 As shown, since the support rib 320 only needs to bear the force along the height direction, the thickness of the support rib 320 only needs to meet the strength requirements. However, the size of the output end of the telescopic device 220 is generally larger than the thickness of the support rib 320. Therefore, when connecting the support rib 320 and the output end of the telescopic device 220, the support rib 320 can be connected to the output end of the telescopic device 220 through the support block 322 provided at the top to form the required driving point.

[0056] In this embodiment, as Figure 5 As shown, if the height of the supporting rib 320 is H, then the value of H is 0.8r to 1.5r.

[0057] It is understandable that the supporting rib 320, subjected to the component of the closing force of the telescopic device 220, can be considered as a cantilever beam structure. The deflection of the cantilever beam represents the degree of deformation of the supporting rib 320. According to the deflection calculation formula for a cantilever beam, the longer the cantilever beam, the greater the deflection under the same driving force. Therefore, to reduce the degree of deformation of the supporting rib 320, its height should not be too high. At the same time, if the height of the supporting rib 320 is too low, the component of the closing force of the telescopic device 220 will easily affect the moving formwork 300. Therefore, the height of the supporting rib 320 can preferably be designed to be 0.8r to 1.5r.

[0058] In this embodiment, as Figure 3 As shown, the side of the support rib 320 is provided with multiple corresponding weight-reducing holes 321 to reduce the mass of the entire moving template 300.

[0059] Another aspect of this application provides a design method for a direct pressure mold clamping mechanism, a preferred embodiment of which includes the following steps:

[0060] S100: Establish a simulation model of the dynamic template in the simulation software, and preliminarily estimate the range of values ​​for r.

[0061] S200: Apply a set clamping force to the corresponding position of the simulation model according to the extreme value of the range of r, and then obtain the deformation of the clamping surface of the moving template at the corresponding extreme point.

[0062] S300: Compare the simulation results of the current step S200 with the simulation results of the previous step S200.

[0063] S400: Based on the comparison results of step S300, optimize the range of r values ​​and incorporate it into step S200 until the optimal r value is obtained.

[0064] Understandably, the design of a direct-pressure mold clamping mechanism primarily involves determining the position of the driving point on the moving mold plate 300. After obtaining the optimal driving point position, the installation position of the telescopic device 220 on the drive seat 210 can be determined accordingly. Furthermore, based on the optimal driving point position, the optimal thickness of the moving mold plate 300 can be obtained through simulation and other methods. Therefore, when designing a direct-pressure mold clamping mechanism, it is only necessary to determine the optimal position of the driving point on the moving mold plate 300.

[0065] It should be noted that ANSYS software is a commonly used simulation software. By setting different driving points, the deformation of the moving template 300 can be obtained. Based on the deformation, the position of the driving point can be optimized to finally obtain the desired optimal driving point position.

[0066] In this embodiment, let the deformation values ​​corresponding to the two extreme points obtained from the first simulation in step S200 be A1 and A2, respectively, and let the deformation value of the traditional moving template 300 during mold locking be A0; then in step S400, if A0 > A1 > A2, the optimal value of r is located at the position where the extreme point corresponding to A2 decreases, or the optimal value of r is located between the extreme points corresponding to deformation values ​​A1 and A2; if A0 > A2 > A1, the optimal value of r is located between the extreme points corresponding to deformation values ​​A1 and A2, or the optimal value of r is located at the position where the extreme point corresponding to deformation A1 increases.

[0067] In this embodiment, when A0 > A1 > A2, the extreme point corresponding to deformation A2 is first reduced to obtain a new extreme point r*, which is then substituted into step S200. If the deformation A3 corresponding to the extreme point r* is less than A2, it indicates that the optimal value of r is close to the extreme point r*; otherwise, the optimal value of r is located between the extreme points corresponding to deformation A1 and A2. When A0 > A2 > A1, the extreme point corresponding to deformation A1 is first increased to obtain a new extreme point r**, which is then substituted into step S200. If the deformation A4 corresponding to the extreme point r** is greater than A1, it indicates that the optimal value of r is located between the extreme points corresponding to deformation A1 and A2; otherwise, the optimal value of r is close to the extreme point r**. The value of the extreme point r* is 95% to 99% of the value of the extreme point corresponding to deformation A2, and the value of the extreme point r** is 101% to 105% of the value of the extreme point corresponding to deformation A1.

[0068] To facilitate understanding, the specific design process of the direct pressure mold clamping mechanism will be explained in more detail below:

[0069] (1) Model creation: The required 3D model of the moving template 300 can be created in 3D software or simulation software. At this time, the size of the moving template 300 can be referenced from the size of the traditional moving template 300.

[0070] (2) Obtaining the deformation of the traditional moving template 300: In the simulation software, a quarter-size clamping force is applied to the second sliding hole 310 positions corresponding to the four corners of the non-locking surface of the moving template 300. Then, constraints are applied to the locking surface of the moving template 300 according to the corresponding projected area positions of the mold. Finally, the deformation is solved to obtain the deformation A0 generated by the moving template 300 using the traditional driving method.

[0071] (3) Setting the initial optimization position of the driving point: As mentioned above, the range of the distance r between the driving point and the driving point is 0.4R to 0.8R; therefore, the initial range of the distance r between the driving point and the driving point can be selected as 0.6R to 0.8R. Based on the selected initial range, two extreme points r can be obtained. max1 =0.8R, r min1=0.6R. Using the value of the corresponding extreme point as the radius, four driving points are selected on the non-locking surface of the moving mold plate 300, evenly distributed along the circumference, and a quarter-sized clamping force is applied to each. Then, by solving for the deformation, the extreme point r can be obtained. max1 and r min1 The corresponding shape variables are A1 and A2, respectively.

[0072] (4) Analyze the obtained deformable variables: Compare the deformable variables A0, A1 and A2. There are two main results of the comparison. The first is: A0 > A1 > A2; the second is: A0 > A2 > A1.

[0073] Curve fitting for the first case above yields the following result: Figure 6 The fitting results are shown in (1) and (2).

[0074] Curve fitting for the second case above yields the following result: Figure 7 The fitting results are shown in (1) and (2).

[0075] (5) Determine the fitting result: When the comparison result is the first case mentioned above, a small step size can be used to judge the fitting result. That is, first determine the extreme point r corresponding to the deformation A2. min1 A small step size is reduced to obtain a new extreme point r*. Then, the simulation process is repeated based on the new extreme point r* to obtain the deformation A3 of the moving template 300 corresponding to the extreme point r*. The values ​​of deformation A3 and deformation A2 are compared; if A3 < A2, it indicates that the optimal value of r is close to the extreme point r*; that is, the curve fitting result is as follows. Figure 6 As shown in (1). Otherwise, the optimal value of r lies between the extreme points corresponding to deformation variables A1 and A2; that is, the result of curve fitting is as shown in (1). Figure 6 As shown in (2).

[0076] When the comparison result is the second case mentioned above, a small step size can also be used to judge the fitting result. That is, first set the extreme point r corresponding to the deformation A1. max1 Increase the step size slightly to obtain a new extreme point r**. Then repeat the simulation process based on the new extreme point r** to obtain the deformation A4 of the moving template 300 corresponding to the extreme point r**. Compare the values ​​of A4 and deformation A1; if A4 > A1, it means that the optimal value of r lies between the extreme points corresponding to deformation A1 and A2; that is, the curve fitting result is as follows. Figure 7 As shown in (1). Otherwise, the optimal value of r is close to the extreme point r**; that is, the result of curve fitting is as shown in (1). Figure 7 As shown in (2).

[0077] Understandably, let the small step size be t, where t can be a constant or a variable. As optimization progresses, the range between extreme points gradually narrows, and a constant small step size t might lead to inconsistent optimization results. Therefore, a variable value is preferred for the small step size t. That is, the small step size t is 1% to 5% of the extreme value range to be optimized; then the value of the extreme point r* is r. min1 -(0.01~0.05)(r max1 -r min1 The value of the extreme point r** is r. max1 +(0.01~0.05)(r max1 -r min1 ).

[0078] (6) Secondary optimization: Based on step (5), the approximate fitting curve of the deformation following the extreme point can be determined. Figure 6 Taking the curve fitting result shown in (2) as an example, a large step size can be used to define the new range of values ​​for r; let the large step size be T, then the value of T is half of the range of values ​​to be optimized, that is, T = 0.5(r max1 -r min1 Thus, the extreme point r corresponding to the deformation A2 can be determined. min1 Increasing the step size T by a large increment yields a new range of r values ​​between 0.6R and 0.7R. The corresponding two extreme points are then points r and r. max2 =0.7R, r min1 =0.6R. Due to the extreme value r min1 The corresponding deformation result is known; we only need to find the new extreme point r. max2 By substituting the value of r into the simulation software and performing the above simulation process, a new extreme point r can be obtained. max2 The corresponding shape variable is A5.

[0079] (7) Continuous optimization: The values ​​of the three newly obtained extreme points A1, A5 and A2 are compared and fitted. The fitting results are basically similar to the fitting results mentioned above. The range of r values ​​can be gradually moved closer to the optimal result by repeating the steps (5) and (6).

[0080] There are several ways to determine the optimal value of r. One method is based on the number of optimization attempts; for example, if the number of optimization attempts reaches 10, the r value can be considered optimal. Another method is based on the ratio of the range between the two optimized extreme points to the preset range between the two extreme points. For example, if the range between the two extreme points is within 5% of the initially preset range, the r value can be considered optimal.

[0081] Another aspect of this application provides a die-casting machine, such as Figures 8 to 11As shown, one preferred embodiment includes the aforementioned direct pressure mold closing mechanism, frame 100, and a pair of support components 4; the lower ends of the drive mechanism 200 and the moving template 300 respectively cooperate with the frame 100 through corresponding support components 4; when the direct pressure mold closing mechanism moves horizontally, the support components 4 are adapted to move synchronously along the frame 100, thereby providing vertical support for the direct pressure mold closing mechanism; when the direct pressure mold closing mechanism vibrates, the support components 4 are adapted to elastically extend and retract in the vertical direction.

[0082] Understandably, traditional die-casting machines employ a horizontal structure, meaning the guide columns 110 are horizontally positioned. This allows the direct-pressure mold-closing mechanism to move horizontally along the guide columns 110 to open and close the mold. During the movement of the direct-pressure mold-closing mechanism, most of the weight of the drive mechanism 200 and the moving platen 300 is supported by the pair of guide columns 110 located above. Consequently, after prolonged use, the wear on the upper pair of guide columns 110 may be greater than that on the lower pair. Over time, this can cause a slight deviation in the movement direction of the drive mechanism 200 and / or the moving platen 300, leading to a shift in the direction of the extrusion force exerted by the drive mechanism 200 on the moving platen 300. This can result in gaps in the mold-closing mechanism of the moving platen 300, causing mold-closing failure. Furthermore, due to the different wear levels of the guide columns 110, the movement of the drive mechanism 200 and the moving platen 300 can also increase vibration intensity, generating significant noise.

[0083] Therefore, this application allows for the installation of a support component 4, which can move and cooperate with the frame 100, below both the drive mechanism 200 and the moving template 300. The support component 4 has an elastic telescopic function in the vertical direction, allowing for vibration reduction through its elastic telescopic movement when the drive mechanism 200 and / or the moving template 300 vibrate. Simultaneously, as the drive mechanism 200 and the moving template 300 move horizontally along the guide column 110, the support component 4 moves horizontally along the frame 100 synchronously with them. This provides an upward supporting force to the drive mechanism 200 and the moving template 300, balancing their weight and reducing friction between them and the guide column 110, thereby reducing wear.

[0084] In this embodiment, as Figure 8As shown, the frame 100 also includes a tail plate 120 and a base 130; the tail plate 120 is vertically fixed to the end of the base 130, so that the guide column 110 can be fixed by connecting its end to the four corners of the tail plate 120. The extension direction of the base 130 is parallel to the axial direction of the guide column 110, and the lower ends of the drive mechanism 200 and the moving template 300 can move and cooperate with the base 130 through the support assembly 4.

[0085] In this embodiment, as Figures 9 to 11 As shown, the support assembly 4, from top to bottom, includes an upper sliding foot 43, a lower sliding foot 42, and a roller assembly 41. The upper sliding foot 43 is fixedly installed at the lower end of the direct pressure mold closing mechanism, and the roller assembly 41 is installed at the lower end of the lower sliding foot 42 for rolling engagement with the base 130. Thus, when the drive mechanism 200 and the moving template 300 move horizontally along the guide post 110, the support assembly 4 can roll along the base 130 via the roller assembly 41, effectively reducing the friction between the support assembly 4 and the base 130, ensuring smooth movement of the drive mechanism 200 and the moving template 300. The upper sliding foot 43 and the lower sliding foot 42 are elastically connected by a deformation assembly 44. Therefore, when vibration occurs during the movement of the drive mechanism 200 and the moving template 300, vibration compensation can be achieved through the elastic expansion and contraction between the upper sliding foot 43 and the lower sliding foot 42. In other words, the support assembly 4 provides flexible support for the drive mechanism 200 and the moving template 300, thereby preventing rigid support from transmitting vibration to the base 130.

[0086] It should be understood that for large mechanical equipment, resonance must be avoided during operation. If the various parts of a large mechanical equipment are rigidly connected, the vibration of one or more components can be transmitted to other components, causing resonance in multiple or all components. In this application, by elastically connecting the upper sliding foot 43 and the lower sliding foot 42 through the deformation component 44, a flexible support structure is formed between the drive mechanism 200, the moving template 300, and the base 130. This effectively isolates the vibrations generated by the drive mechanism 200 and the moving template 300 from the base 130, thereby suppressing resonance.

[0087] In this embodiment, as Figure 11As shown, multiple sets of deformation components 44 are spaced apart along the length of the upper sliding foot 43 and the lower sliding foot 42. Each set of deformation components 44 contains at least one component; for example, as shown in Figure 11, each set contains two components. By evenly distributing multiple deformation components 44, sufficient support force can be ensured while providing flexible support for the drive mechanism 200 and the moving template 300. Each deformation component 44 includes a connecting pin 441 and a disc spring assembly 442. The connecting pin 441 can pass upward through the lower sliding foot 42 and be threadedly connected to the upper sliding foot 43. The disc spring assembly 442 is sleeved on the connecting pin 441, with its upper end abutting against the upper sliding foot 43 and its lower end abutting against the lower sliding foot 42. Thus, a compensation gap with a certain height is formed between the upper sliding foot 43 and the lower sliding foot 42 through the elastic force of the disc spring assembly 442. Furthermore, when the drive mechanism 200 and the moving template 300 vibrate, the disc spring assembly 442 can absorb vibration by elastically deforming to reduce or increase the height of the compensation gap.

[0088] It is understood that the threaded section of the connecting pin 441 is fixedly connected to the upper sliding foot 43, while the smooth section of the connecting pin 441 is slidably engaged with the lower sliding foot 42. Therefore, when the drive mechanism 200 and the moving template 300 vibrate, the upper sliding foot 43 can drive the connecting pin 441 to move vertically relative to the lower sliding foot 42 along with the drive mechanism 200 and the moving template 300, thereby changing the degree of deformation of the disc spring assembly 442. The disc spring assembly 442 can generate a large elastic force with a small deformation to meet the requirements of this application. If the elastic coefficient of other elastic elements meets the usage requirements, other elastic elements can also be used to replace the disc spring assembly 442.

[0089] In this embodiment, as Figure 9 and Figure 10 As shown, multiple roller assemblies 41 are installed at equal intervals along the length of the sliding foot 42, thereby improving the support force on the sliding foot 42. Each roller assembly 41 includes a rotating shaft 411 rotatably mounted on the sliding foot 42, and at least one roller 412 mounted on the rotating shaft 411. The specific number of rollers 412 can be set according to actual needs, for example... Figure 10 As shown, the roller assembly 41 includes a pair of rollers 412, which are spaced apart along the axial direction of the shaft 411, thereby further improving the support force on the sliding foot 42.

[0090] The basic principles, main features, and advantages of this application have been described above. Those skilled in the art should understand that this application is not limited to the above embodiments. The embodiments and descriptions in the specification are merely the principles of this application. Various changes and modifications can be made to this application without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claims. The scope of protection claimed by this application is defined by the appended claims and their equivalents.

Claims

1. A design method for a direct-pressure mold clamping mechanism, the direct-pressure mold clamping mechanism comprising a driving mechanism and a moving mold plate; both the driving mechanism and the moving mold plate are slidably engaged with a frame via sliding holes at four corners; the end face of the moving mold plate facing away from the mold-locking direction is provided with a plurality of driving points along the circumferential direction for driving connection with the driving mechanism; the distance from the driving point to the center of the moving mold plate is less than the distance from the sliding hole to the center of the moving mold plate; let the distance from the sliding hole to the center of the moving mold plate be R, and the distance from the driving point to the center of the moving mold plate be r; characterized in that: The specific design steps are as follows: S100: Establish a simulation model of the dynamic template in the simulation software, and preliminarily estimate the range of values ​​for r; S200: Apply a set clamping force to the corresponding position of the simulation model according to the extreme value of the range of r values, thereby obtaining the deformation of the clamping surface of the moving template at the corresponding extreme point; S300: Compare the simulation results of the current step S200 with the simulation results of the previous step S200; S400: Based on the comparison results of step S300, optimize the range of r values ​​and bring it into step S200 until the optimal r value is obtained; Let the deformations corresponding to the two extreme points obtained from the first simulation in step S200, from largest to smallest, be A1 and A2, respectively; let the deformation of the traditional moving template during mold locking be A0; then in step S400: If A0 > A1 > A2, then the optimal value of r is located at the position where the extreme point corresponding to A2 decreases, or the optimal value of r is located between the extreme points corresponding to deformation A1 and A2. If A0 > A2 > A1, then the optimal value of r is located between the extreme points corresponding to deformation A1 and A2, or the optimal value of r is located at the position where the extreme point corresponding to deformation A1 increases. When A0 > A1 > A2, first reduce the extreme point corresponding to deformation A2 to obtain a new extreme point r* and substitute it into step S200; if the deformation A3 corresponding to the extreme point r* is < A2, it means that the optimal value of r is close to the extreme point r*; otherwise, the optimal value of r is located between the extreme points corresponding to deformation A1 and A2. When A0 > A2 > A1, first increase the extreme point corresponding to deformation A1 to obtain a new extreme point r** and substitute it into step S200; if the deformation A4 corresponding to the extreme point r** > A1, it means that the optimal value of r is located between the extreme points corresponding to deformation A1 and A2; otherwise, the optimal value of r is close to the extreme point r**. Wherein, the extreme point corresponding to the deformation variable A1 and A2 is r max1 and r min1 , the value of the extreme point r* is r min1 - (0.01~0.05) (r max1 -r min1 ), the value of the extreme point r** is r max1 + (0.01~0.05) (r max1 -r min1 ).

2. The design method of the direct pressure mold clamping mechanism as described in claim 1, characterized in that: The value of r ranges from 0.4R to 0.8R.

3. The design method of the direct pressure mold clamping mechanism as described in claim 1, characterized in that: The non-locking surface of the moving template is fixedly provided with an annular support rib, the cross-section of which is circular or polygonal; the driving mechanism is connected to the top of the support rib to form the driving point.

4. The design method of the direct pressure mold clamping mechanism as described in claim 3, characterized in that: Let the height of the supporting rib be H, then the value of H is 0.8r~1.5r.

5. A die-casting machine, characterized in that: The direct pressure mold closing mechanism designed by the design method of the direct pressure mold closing mechanism according to any one of claims 1-4 further includes a frame and a pair of support components; the lower ends of the drive mechanism and the moving mold plate are respectively engaged with the frame through the corresponding support components; when the direct pressure mold closing mechanism moves horizontally, the support components are adapted to move synchronously along the frame, thereby providing vertical support for the direct pressure mold closing mechanism; when the direct pressure mold closing mechanism vibrates, the support components are adapted to elastically extend and retract in the vertical direction.

6. The die-casting machine as described in claim 5, characterized in that: The support assembly includes, from top to bottom, an upper sliding foot, a lower sliding foot, and a roller assembly; the upper sliding foot is fixedly installed at the lower end of the direct pressure mold closing mechanism, and the roller assembly is installed at the lower end of the lower sliding foot for rolling engagement with the frame; the upper sliding foot and the lower sliding foot are elastically connected by a deformation assembly.

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