TW200932511A - Machine-difference simulation press machine - Google Patents

Abstract

This invention provides a machine difference simulation press which can be adjusted to reduce or eliminate the machine difference from a simulation-target press which is taken from a press for mass production. The machine-difference simulation press machine 10 of this invention is provided with mold holding members 25. 36 on which molds for press forming a work are to be mounted, and supporting members 35, 3a supporting the outer periphery of the mold holding members 25, 36. It is characterized in having a load providing device 9 for adjusting the deflection of the mold holding members 25, 36 by causing the load to act on the part of the mold holding members 25, 36 that is not supported by the supporting members 34, 3a.

Description

200932511 VI. Description of the Invention: TECHNICAL FIELD OF THE INVENTION The present invention relates to a differential simulator that simulates the machine difference of a simulated object press. [Prior Art] A large-scale press die (hereinafter referred to as a "mold") used for mass production of an automobile body or the like is very important in determining the value of the automobile. Therefore, in terms of the mold, in order to correctly transfer the body design to the vehicular surface, the mold processing surface (the ramming surface) is simply produced by the cAD and GAM com-compensation of the thickness of the board. However, due to the molding pressure during the press working, the cookware (the upper mold and the lower mold) and the punching device (the bolster and the slide) are deformed, and the lower mold and the upper mold are deformed. The stamping surfaces are completely inconsistent. Therefore, in the final step of the die making process during the press working, the skill trainer must repeat the "closing work" so that the punched faces are correctly aligned. ❹ - The mold clamping step includes the steps of mold clamping by the mold manufacturer using the test press (manufacturing of the mold), and the step of mold clamping using the mass production press of the mold user (automotive manufacturer, etc.) (User's clamping). The total working time of the mold clamping step is equivalent to 1/2 to 2/5 of the mold production time. In order to improve the productivity, the reduction of the mold clamping step is highly anticipated. Further, the prior art related to the present invention has been disclosed in Patent Document 1. Patent Document 1 is provided with a plurality of elastically deformable members between a bed and a mold supporting plate to adjust the shape of the mold. In the mold clamping step of the above-mentioned mold, the mold clamping of the user usually takes 1 to 200 hours. Up to 1/3 of the total clamping step, the user's clamping has a stop loss of the press line during this period in addition to the operating cost. Therefore, the user's mold clamping step is also eagerly expected for the mold user (automotive manufacturer, etc.) to shorten the step time.

Although the mold manufacturer has completely completed the mold clamping in advance, it still takes a long time for the user to close the mold, which is due to the use of the press machine used by the mold maker and the mass production used by the mold user. The difference between the presses and the difference between the machines is). The non-fat day is to provide an adjustable machine phase = machine, which is used as a simulation target press for mass production, and the machine can be removed from the machine. SUMMARY OF THE INVENTION The above object is achieved. According to the present invention, it is possible to provide a mold holder having a mold for stamping a workpiece, and to support the mold holding. The support member of the outer peripheral portion of the member is characterized in that: the machine is characterized by: a weighing wedge::: means, which applies a load to a portion that does not support the above-mentioned mold holding member during press working According to the preferred embodiment of the present invention, the above-described load imparting means is provided with 320967 4 200932511, and the deflection adjusting device for applying load to the mold holding member is provided with: a deflection adjusting device for Adjust the deflection adjustment cylinder 奘^ to restore the load of the above mold holding member. The apparatus acts in accordance with a preferred embodiment of the present invention which maintains at least either of the frame and the slide. In the above configuration, the cows can adjust the deflection of the mold holding member at the time of the pressure by means of a load thief. By the flexing adjustment "work 〇 = ==== cloth and the mold of the simulated object press: reducing the mechanical difference caused by the release of the mold holding member, according to a preferred embodiment of the present invention The value of the above-described load of the target deflection amount is set such that the warpage adjustment red body device acts on the above-described deflection adjustment and the device is loaded with the calculated value. ==::, the mold can be automatically held in a preferred embodiment. The above-mentioned mold is a press-formed press machine that presses the workpiece (9) up and down. And the above-mentioned line lifting movement; the sliding member is ~, the woman is in the lower part and enters the bull movement mechanism to make the sliding piece rise and fall and is stamped into a force of 320967 5 zuvyjzjll zuvyjzjll; tilting to adjust the tilt of the cylinder member The square < 'to change the stroke position of the borrowing (four) to make the device 'to adjust the load applied to the two sliders; and to tilt 'in the above configuration, to adjust the stroke position of the cylinder device.蹩 可 可 可 可 可 倾斜 倾斜 倾斜 倾斜 倾斜 倾斜 倾斜 倾斜 倾斜 倾斜 倾斜 倾斜 倾斜 倾斜 倾斜 降低 降低 降低 降低 降低 降低This can also make the inclination of the slider related to ^ in accordance with the present invention in the up and down direction:: type, the above mold will be processed by the machine differential simulation press _: I plus the upper and lower mold The upper mold is lifted and moved; the mold is lowered to the bottom, and the upper mold is placed between the crucibles to hold the workpiece, and is placed in the press processing to be placed on the upper mold to control the decrease in the A state. The movable portion; the buffer control device has an action of memorizing the movable portion, wherein the buffer control device is configured to provide a memory portion of a specific form, and the movable portion is operated according to the target buffering characteristic of the movable second. Further, the above-described buffer control is incorporated in the above configuration, and the operation of the movable portion is controlled in a form. The above-described movable 1 rush control device for rushing characteristics is configured to control the movement of the movable portion by simulating a pair of simulations in accordance with the purpose of giving a target. The cushioning characteristic is related to the target cushioning characteristic of the press, and the mold can be removed according to the preferred embodiment of the present invention. The above-mentioned differential simulated press is in & ι_ ",,, There is a surface pressure distribution adjustment plate. The two "surface pressure distribution adjustment plates of the convex plane have a complex convex plane, and the two degrees of each convex thousand = are independently set. According to the surface pressure distribution adjustment plate, the above-mentioned mold 6 320967 200932511 can be adjusted to have a contact pressure distribution between the holding member and the mold. Therefore, the machine difference associated with the contact pressure distribution can be reduced or eliminated. According to a preferred embodiment of the present invention, it is possible to: (机) the machine difference of the deflection distribution of the mold holding member, (2) the machine difference associated with the inclination of the slider, and (3) the machine related to the characteristics of the mold cushioning. The difference, and (4) the contact pressure distribution between the mold holding member and the mold is reduced or eliminated. By doing this, you can make a simulation

The difference between the target press and the punching surface of the lower die between the target press and the differential press of the present invention is reduced or eliminated. According to the present invention described above, the press machine for mass production or the like is used as the simulation target press, and the difference from the press machine of the simulation target can be reduced or eliminated. [Embodiment] The best mode for carrying out the invention will be described with reference to the drawings. In the drawings, the common portions are denoted by the same reference numerals, and the repeated description is omitted. [Overall Configuration of Differential Simulator] 〇 f1 is a configuration diagram of a differential simulator of the first embodiment of the present invention. The differential simulator 10 includes a slider 3, a slider drive mechanism 5, a counter balance cylinder 7, a deflection adjusting cylinder 9, a deflection adjustment device u, and a tilt adjustment. The rainbow body device 13, the tilt adjusting device 15, the die cushioning device 17, the buffer control device 19, and the surface pressure distribution adjusting plates 23a, 23B. The upper mold (not shown) of the slider 3 is fixed to the lower surface and is moved up and down. In the illustration of Fig. 1, the slider 3 has a slider body 3a and a slide plate 3b fixed to the lower surface of the slider body 3a. Slide 320967 7 200932511 The body 3a is a support member of the slide plate 3b for supporting the outer periphery of the slide plate 3b. The workpiece is held between the upper mold and a lower mold (not shown) fixed to the upper surface of the holder 25 to be described later for press working. The slider driving mechanism 5 has: one or a plurality of servo motors (not shown); the driving gear 5a is disposed in an upper upper crown 27 and is rotationally driven by the servo motor; and the switching mechanism 5b (In the illustration of the figure, a link), the drive gear 5a and the slider 3 are coupled, and the rotational motion of the drive gear 5a is converted into the upward and downward movement of the slider 3. The balancing cylinder 7 attaches an upward force which is balanced with the weight of the slider 3 and the upper die to the slider 3' to facilitate vertical movement. The deflection adjusting cylinder device 9 applies a load to the mold holding member (in the example of Fig. 1, the holder 25 and the slider 3b are exemplified in the press working). The socket 25 supports the outer peripheral portion of the support member (the carrier 34 described later in the illustration of Fig. 1), and the deflection adjustment cylinder split 9 includes: the support member (the bracket is not supported) 34) The supported seat portion applies the lower rigid adjustment cylinder 9a to the upper load. In the example of Fig. 1, the upper rigid adjustment cylinder 9b applies an upward load to the central portion of the slider 3b. The slide plate 3b supports the outer peripheral portion thereof by the support member (the slide main body 3a in the illustration of Fig. 1), and the deflection adjustment cylinder device 9 includes the support member (slider body 3a) not supported by the support member (slider body 3a) The slider portion applies an upwardly loaded upper rigid adjustment cylinder 9b. In the example of Fig. 1, the upper rigidity adjusting cylinder 9b applies a downward load to the center portion of the slider 3b. Further, it is also possible to provide only one of the lower rigid adjustment cylinder 9a and the upper rigid adjustment cylinder 9b. 320967 200932511 Flexure adjustment device u is attached to the Chongwu and Cylinders. The above-mentioned model is adjusted (4). The 11-series can be set individually: the upper rigid adjustment cylinder = load. The configuration of the deflection adjusting device η for the deflection adjusting device 11 and the lower rigidity adjusting cylinder 9b will be described later. 'Assisted by the whole device. Flexing said that Lin Nahong Fortune 13 series (four) ❸ Ο Ο. With this configuration, by tilting the π-piece driving mechanism 5 and the sliding, the stroke positions of the slider driving mechanism 5 and the sliders 3 and i3 can be changed, that is, the slider driving mechanism 5 and the slider 3 are Fine, wild position changes. That is 13 links. Therefore, by adjusting the tilting and tilting adjustment body device, that is, the stroke position, the stroke amount of the slider 3 with respect to the set 13 can be adjusted (the second figure is the tilt of the second direction of the mA line. In the vicinity, in Fig. 1 and the second _ = surface view, only the slider whole cylinder device 13 is shown, and the tilt adjustment red is provided with four tilt adjustments fixed to the vicinity of the outer peripheral portion of the slider 3, and another 13 The one creeping portion is freely coupled to the slider driving mechanism 5, and then the scale is rotatable. In the first drawing, the tilting adjusting device 15 is two: the stroke position of the device 13. The tilt adjusting device x adjusts the tilt adjusting cylinder The pressure of the body device 13 is adjusted indirectly by adjusting the tilting system to adjust the tilting position, and the direct control of the tilting adjustment of the body dream "the whole red body farming 13 slanting adjustment device 15 is to set the tilt adjusting cylinders 13 The stroke position is adjusted, and the balance position of the other tilt adjustment cylinder device 13 is set to 13. The balance position adjustment of the touch-sensitive middle puller buffering skirt 17 is the oil-discharging device 200932511 ^ Preparation movable 17a (i-fi In the middle of the piston), during the stamping process, while giving the downward thrust 'side to The state in which the workpiece is held between the upper molds is lowered' to apply an upward load to the upper mold; the cushion ((4)

The pad) nb' is pushed upward by the upper end portion of the movable portion 17a; the pin plate 17c is supported by the cushion pad 17b; and the cushion pin 17d is supported by the pin plate 17c. The buffer control device 19 controls the mold cushioning device 17 so as to impart a target cushioning characteristic. The configuration of the buffer control device 19 will be described later. The surface pressure distribution adjusting plates 23A and 23B are provided between the socket 25 and the slider 3 (in the example of Fig. 1 and referred to as the slider 3b) and a die supporting surface (not shown). According to this configuration, the machine difference of the pressure distribution at the contact surface between the dies can be reduced or eliminated. The surface pressure distribution adjusting plates 23A, 23B have a plurality of convex planes 29 on the contact surface with the mold. Further, each of the convex planes 29 has a thickness adjusted by the FEM, and the height of each convex plane 29 is set so as to independently reduce the difference in contact pressure distribution. Further, it is preferable that the surface pressure distribution adjusting plates 23A, 23B are formed separately, but may be separated by the convex planes 29, and each has a separate thickness of the gusset plate. The pressure adjustment method according to the surface pressure distribution adjusting plates 23A, 23B will be described later. The frame of the machine differential simulation press 10 is connected to the load supporting member 27 by a plurality of connecting members 33 (in the example of the first drawing, a plurality of tie rods) (the upper beam is illustrated in the first drawing) And the lower load supporting member 31 (the bed surface in the example of Fig. 1), the upper load supporting member 27 is subjected to the upward load from the slider 3 when the ink processing 10 320967 200932511, and the lower load supporting member 31 is subjected to the press working It is subjected to a downward load from the socket 25. Further, between the upper load supporting member 27 and the lower load supporting member μ, the upright 20 is held, and the upper load supporting member and the lower load supporting member are coupled by the connecting member 33. The bed 31 is used to support the bracket 34. - As described above, the bracket 34 is a supporting member of the socket 25 for supporting the outer peripheral portion of the socket. [Flexure Adjustment Method] 第 (First Embodiment) Fig. 3 is a general flow chart showing the rigidity adjustment method of the first embodiment of the differential simulation press 10 of the present invention. In the figure, the method of the present invention is constituted by the steps of S1 to S8. In step S1, the deformation data is obtained by a distortion measuring instrument of the simulated object press. The simulated object press is a mass production press such as a mold user. Further, the deformation measuring instrument is for measuring the deformation of the mold holding member (the socket 25 and the slider 3b) at the time of pressing. In step S2, the deflection distribution of the simulated object press is estimated from the obtained deformation data. This calculation is based on FEM calculations or theoretical calculations. The obtained deflection distribution is referred to as "target deflection distribution". In step S3, the deflection calculation of the differential simulation press 1 of the present invention is performed. This calculation is performed in accordance with the FEM as an equal distributed load. In step S4, the load setting of the above-described deflection adjusting cylinder device 9 is performed. That is, the deflection adjustment cylinder device 9 is set in such a manner that the deflection distribution of the socket 25 or the slider 3b at the time of press processing becomes the target deflection distribution or the equation 11 320967 200932511 which is similar to the target deflection distribution. A load acting on the center portion of the socket 25 or the slider 3b during press working. In step S5, the deflection calculation at the time of setting the load of the cylinder device 9 is flexibly adjusted by the FEM. In step S6, it is confirmed that the deflection distribution obtained by the deflection is in agreement with the target. In step S7, the deflection calculation including the mold is performed with the FEM. In step S8, it is confirmed that the influence of the mold is small. In the steps S6 and S8, if there is no problem, the deflection adjustment (rigidity adjustment) of the present invention is ended. In the case of a problem, steps S3 to S7 are repeated. (Second Embodiment) In the second embodiment, the target deflection amount Wt is calculated by the following formula (1). The target deflection amount of the mold holding member of the Wt system differential simulation press 10 at the time of press working. Preferably, the Wt is a displacement amount in the center of the mold holding member of the simulation target press.

Wt = Pt/Kt (1) In the above formula (1), when Pt is subjected to press working by a dummy pressing machine, the pressing load acting on the mold during press working varies depending on each mold. Further, the press load Pt may be a total punch load applied to the mold at the time of press working. Further, in the formula (1), the Kt is a rigidity of the relationship between the deflection W and the press load P acting on the mold when the press is performed by the dummy pressing machine, and can be expressed by the following formula (2).

Kt = P/W ... (2) 200932511 P is used in the press processing of the analog target press. Press load, which is synonymous with Pt. The die for the wedge tool is a mold and the amount of curvature during the press working of the simulated object press, and can also be performed by the calculation of the above-mentioned step 82, and can also be the mold holding member/戽 table of the simulated object press. Got it. • When the second embodiment is represented by a flowchart, it is a displacement amount such as a central portion. • Next, it will be explained with reference to Fig. 4. Figure 4 shows. (Steps ST2 to ST5): For the machine to be machined in advance and the simulator to be simulated, the mold is used for the simulation, and the object A is simulated, and the machine B is used to simulate the use of the machine B of the die 1 Line description. , a C:" mold d simulation object is worse than the machine differential simulation press 10 simulation using the mold ❹ object press A, and the machine simulation simulation pressure = Mo or mold d simulation object: simulation Molds C KtA, Ptc, Ptd, KtB were used. The pre-existing Yongxun, Ptb,

Pta is applied to the press load of the mold a after the mold of the mold a is used, and the Ptb is used for the press working of the press A, and the press work of the dummy press B of the mold 〇 is used.睹七在c的冲(四)Loading 'Ptd' is applied to the die (d) of the mold d when the root is used and the mode of d is biased by the die press. The edge press B's rushing '仏 模 _ _ press machine A's lining plus ^ (4) retaining structure 320967 13 200932511 pieces of flexing 'and the analog object presses that will not change due to the mold A - some value. The amount of deflection of the mold holding member during the press working of the Κΐβ-based simulation target press B is based on the value of the dummy object that is not changed by the mold.

Pta and lanthanum were obtained as follows. The press is performed by the dummy target press A using the mold a, and the amount of deflection of the pta and the mold holding member Wa°Pta at the time of the press working is determined by, for example, a distortion gauge adhered to the back surface of the mold a or the like. The obtained deformation data is obtained (ST2, ST3). The deflection amount Wa of the mold holding member can also be obtained by the same method as the above-described step S2 of the first embodiment (ST2, ST3). Following the above equation (2), KtA is found to be KtA = Pta/Wa (ST4). In the same manner as in the case of Pta, the Ptb is pressed by the dummy press A using the mold b, and ptb at the time of the press working is obtained. p seven, ptd,

KtB is also obtained in the same way. In this way, steps ST2 to ST5 are repeated, and the obtained pta, ptb,

KtA Pte, Ptd, and KtB are stored in a specific memory device to make the stamping load of the mold and the rigid database of the simulated object stamping (ST5). 〇 (Step ST6) The above-described condition (1) of the simulation target press A using the die a is simulated by using the machine-difference simulation press 1 to obtain WtA as M = pta/KtA (ST6). In the case of simulating the target press A using the die b by the machine differential simulation press 1G, the above equation (1) was used to obtain Wt == ptb/Kh(10)). The same applies to the simulation of the use of the mold 〇 or the mold d of the mold d by the machine simulator 10. In addition, the number of modules used in each model object is increased or decreased from the above examples, or the number of simulated object presses is increased or decreased from the above examples. As described above, in step ST1, when the data required for the simulation of the simulation target press (that is, the punching load acting on the mold and the rigidity of the simulated target press) is not known, the pressure is applied to each of the simulated objects. In the machine, the steps ST2 to ST5 are performed in accordance with the respective molds to obtain the desired materials. In the above description, Pta, Ptb, KtA, Ptc, Ptd, and KtB are obtained. If the required information is obtained in this way, in step ST6, the target deflection amount wt is calculated using the above (1). In the above example, in the case of simulating the simulation target press A using the mold a, in the above formula (1), Pta is substituted into Pt, KtA is substituted into Kt, and Wt = Pta/KtA is obtained; In the case of the simulation target press A, in the above formula (1), Ptb is substituted into Pt, KtA is substituted into Kt, and Wt = Ptb/K1:A is obtained. The same is true for the simulated object downtime B. Thereafter, steps S3 and S5 to S8 of the first embodiment are performed in the same manner as in the first embodiment. Q The target deflection calculation device for performing the calculation of the second embodiment will be described. In the second embodiment, as described above, the press load Pt acting on the mold is obtained for each mold (in the above example, the simulation target press A is Pta, Ptb, and the simulation target press B is Pte, Ptd). According to each of the simulation target presses, the rigidity Kt (in the above example, ΚΪΑ, KtB) is obtained, and these data are previously stored in the above memory device. The target deflection calculation device calculates the target deflection amount Wt using the above formula (1) as described above based on the press load Pt of each mold memorized in the memory device in the above manner and the rigidity Kt of each of the simulation target presses. The load calculation device will be described later. In addition, the target deflection calculation device 15 320967 200932511 is used to match the simulated object press and is to be used as a confrontation. When the operator (operatQr) operates the operation section, * = the operation section ' ^ 如模 (4) coffee press wins 'calculates the target deflection amount wt for simulation (at this time, *, a) [load calculation device] Ta/KtA) ° The machine differential simulation press 10 is provided with a load calculation device, and the first embodiment or the second embodiment of the deflection adjustment method is used to calculate the deflection of the mold holding member when the press amount is calculated. ^The value of the above-mentioned set load of the above step S4 of the curvature amount.

The load calculation device can also be: based on the above steps %

The deflection distribution/target deflection amount obtained by the calculation (preferably the displacement of the center of the modulo=ST6}, and the winding characteristic of the differential simulator 1Q: the value of the above-mentioned differential load of the step S4 Device, deflection characteristics = deflection during the dust processing adjustment cylinder device 9 acts on the mold holding structure = , the central portion of the load, and the amount of the mold holding member during the press processing (preferably the central portion) The relationship of the amount of displacement below the vertical direction, and ^ is set in advance. In this case, the load calculation device can calculate the value of the set load so that the displacement amount in the center of the mold holding member of the machine simulator 10 matches the displacement amount in the center of the mold holding member of the simulation target press. . Further, the load calculation device preferably has a memory portion for storing the above-described deflection characteristics. Further, the load calculation device may perform the calculation of the above step S2 based on the deformation data obtained in the above step S1. At this time, the load calculation means calculates the value of the set negative 16 320967 200932511 from the deformation data obtained in the above step S1. The value carried is used as the converted value F. "Flexural characteristics, the calculation of the above settings negative

Wt==^ + wlxF (3) Ο 目标 The target of the holding member is: the mold value during the press processing with a difference of 10. Preferably, the target deflection amount "the center shift amount of the member obtained by the calculation of the above step S2. The mold holding structure w° of the press is in the machine differential simulation machine 1 the body device 9 in the mold supporting member ^ When the thief force=the deflection adjusts the rainbow to adjust the deflection amount. The no-wl of the mold support member at the time of loading is the unit load deflection of the deflection adjustment support member when the machine differential simulation pressure body device 9 applies the mold support member The amount of curvature 17 = the mold and the two molds at the time of load: it is better to use the above-mentioned deformation data with the holding member as the image pressure == library. Therefore, each analog material, the cloth, and the set load value are negative in advance. It is better to plant and operate the memory unit. At this time, the 'loading calculation device can have an operation unit, and the machine can use the operation unit to control the deflection according to which surface pressure and the set load value. It is preferable to adjust the cylinder device. 17 320967 200932511 The set load value calculated by the load calculation device is preferably wheeled to the deflection adjusting device 11. At this time, the deflection adjusting device is based on the input setting. Load value to adjust the red body device The load for the mold holding member is set to a load value to adjust/control the deflection adjusting cylinder device 9. [Configuration of the deflection adjusting device] Hereinafter, a specific example of the deflection adjusting device U of the present invention will be described. In the following description, the seat 25 is used as the object, but the slide plate 3b is also the same. The configuration of the deflection adjusting device 11 for the upper rigid adjustment cylinder 9b is used for the lower rigidity adjusting cylinder 9b. The configuration of the deflection adjusting device u is the same. Fig. 5A to Fig. 5D are views showing a first embodiment of the deflection adjusting device I of the present invention. In the figure, the '25 series bearing, the A series hydraulic cylinder, b is the servo controller, the C-system hydraulic control circuit, the dx-based displacement amount, and the p-series load. In this example, the hydraulic cylinder A is adjusted by the servo control of the hydraulic cylinder A for supporting the socket 25. The resulting support rigidity (that is, the amount of displacement in the center of the socket during press working). Fig. 6A and Fig. 6B are diagrams showing the second embodiment of the deflection adjusting device I of the present invention. Medium, support rigid force calculation, B2 system cylinder thrust servo control, dw system deflection , F1 system cylinder thrust control target value, F2 system cylinder thrust control command value. In this example, the thrust of the hydraulic cylinder is controlled according to the deflection amount dw. That is, by the pressure control valve or the feedback control ( Feedbackc〇ntr〇1) is used to control the thrust of the hydraulic pressure red A of the bearing seat 25. Hydraulic cylinder thrust 320967 18 200932511 The control target value F1 of the control is set by the support stiffness characteristic μ according to the deflection of the bearing 25 The detection value of the amount dw is set. 'Jun 7A and 7B are diagrams of the implementation of the deflection adjusting device A i of the present invention. In the figure, the β3 system supports rigid displacement conversion and 3-body position servo. Control, P system generates load, L1 system cylinder position interesting system cylinder value, L2 system red body position control command value. In this example, the displacement amount dL of the hydraulic cylinder is controlled in accordance with the production item P. Negative planting, that is, the hydraulic cylinder A supporting the seat 25 performs position control. The control command value L2 of the cylinder position control is set by the set supporting rigid oil pressure, and is set according to the detected value of the load p applied to the hydraulic cylinder. Characteristics Ο 8A to 8D are diagrams of the deflection adjusting device & embodiment of the present invention. In the figure, Sb is the stroke position. In this example, 4, the stroke position of the support base 25 is changed, and S2 is changed to adjust the support rigidity generated by the rolling rainbow. The deflection of the secret seat 25 and the anti-reverse force generated by the oil are determined according to the amount of compression of the oil that is enclosed in the red body. Qingdan, the following formula (4). In the sputum, AP = KxAV/V - (4) ▽, ΔΡ system _ Quantification, Κ 作 作 体积 体积 体积 体积 体积 体积 体积 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 According to the relation (4), even if the same amount of change in the volume of the operating oil Λν is generated by the deflection of the socket, the value of ΔΡ generated by the initial volume ν of the oil is different. That is, by changing the cylinder stroke positions SI, S2 of the support base 25, the red body anti-320967 19 200932511 force p generated for the deflection of the socket 25 can be changed 'and the hydraulic cylinder can be adjusted. rigidity. Figs. 9A and 9B are views showing a fifth embodiment of the deflection adjusting device π of the present invention. In the figure, the E is a linear motion mechanism, a G1, and a G2 system. As shown in Fig. 9A, in order to change the stroke position of the cylinder, some direct acting mechanisms E (feed screw mechanism, cylinder, jack) having a rigidity sufficiently higher than that of the hydraulic cylinder A described above are utilized. Jack)), and can be achieved by lifting the above-mentioned oil-pressed casing. As shown in Fig. 9B, it is also possible to prepare a plurality of stages G1, G2' of different heights so that the gantry in which the outer casing of the hydraulic cylinder A is placed serves as a support position for supporting the rigidity ,, and the gantry is replaced. In this case, any supporting rigidity can be adjusted by using an accumulator or a method of pre-pressure described later in combination. Fig. 10A to Fig. 10D are views showing a sixth embodiment of the deflection adjusting device η of the present invention. In the figure, Ac is an accumulator. In this example, the support rigidity is adjusted by changing the volume of the accumulator. That is, the compressibility of the gas is sealed by the pressure gauge to generate the support rigidity of the hydraulic cylinder A. Since the cylinder reaction force ' generated by the cylinder stroke compression amount is determined by the amount of compression of the gas in the accumulator AC, the hydraulic cylinder support rigidity can be adjusted by changing the gas volume in the accumulator AC. . The method of changing the volume of the gas in the accumulator can be exemplified by the following method. (1) Setting of the initial sealing pressure of the body pressure device (2) Setting the constant pressure supply value of the working oil pressure (3) Set a plurality of accumulators and select the accumulator to be used. 320967 20 200932511 In the 11th figure, the initial pressure of the body is sealed, and the "12" diagram shows the amount of gasification according to the accumulator. In Fig. 11, the pressure-receiving area of the cylinder supporting rigidity generated by the setting, the PS-based rod-side-receiving area, and the S2-series side are subject to the setting of the storage-system constant-pressure supply balance pressure. In addition to the method of supplying the cylinder hip + initial sealing pressure p〇, the setting of S and Pb (constant pressure supply value) in the accumulator AC can also change the volume of the gas, so the same can be used. Adjust the cylinder support 〇 and read difficult with each woven field. Furthermore, as long as the methods are used in combination, the adjustment range can be expanded. 13A ® and 13B are diagrams of the "transmission mode of the deflection adjusting device of the present invention. In this example, the support rigidity is adjusted by changing the amount of pre-grinding of the oil pressure red a. The volume elastic modulus of the oil is controlled by the operating pressure, so that the supporting rigidity generated by the hydraulic cylinder A can be adjusted by changing the operating pressure region. Fig. 14 to Fig. 16 are the preloading amount of the hydraulic cylinder. An example of the support rigidity adjustment performed by the change. As shown in Fig. 15, as long as the pressure 〇 is in the range of 4〇μρ & ▲, the flow of the volume elastic modulus in the range of about 17 to 22 can be changed. In Fig. 14, the initial force of the oil pressure red A is set, so that the volume bomb is changed by the coefficient 'this can be difficult (4) (four) branch _ sex. As an example, the figure 16 is not caused by the change of the initial pressure ps. The relationship between the output of the oil-covered cylinder and the stroke. 21 320967 200932511 By applying the above-mentioned set load to the center position of the socket 25 from the bottom upward, the bearing 25 of the simulated object press can be simulated with good precision. Target deflection distribution. Not only in the impact on the seat 25 When the center of gravity of the load is the center position of the socket 25, and when the center of gravity deviates from the center position of the socket 25, it is confirmed by analysis that the target deflection distribution can be simulated with good precision. Fig. 18 and Fig. 18 show the results of the analysis. Fig. 17 shows the case where the center of gravity is the center position of the socket 25, and Fig. 18 shows the case where the center of gravity deviates from the center position of the socket 25. Fig. 17 In Fig. 18, the horizontal axis indicates the position of the holder 25 in the left-right direction of Fig. 1, and the vertical axis indicates the amount of socket deflection when the center of the holder is pressed in the direction perpendicular to the plane of the first sheet. Further, in the seventeenth and eighteenth drawings, the broken line indicates the target deflection distribution, and the solid line indicates that the set load is applied to the center of the socket by the deflection adjusting cylinder device 9a. The deflection distribution of the time. By the above-described deflection adjustment, the difference in the deflection of the socket 25 and the slider 3b can be reduced or eliminated. [Slope adjustment of the slider] Fig. 19 shows the slider 3 Flow chart of the tilt adjustment method. The inclination substantially means the inclination of the lower surface of the slider 3 (the lower surface of the slider 3b in the example of Fig. 1). In step S11, the inclination of the slider 3 of the simulation target press is obtained as "target tilt". For example, the target tilt of the slider 3 of the simulated object press can be obtained by measurement. The inclination of the slider 3 is performed during the stamping process in which the above mold is in contact with the workpiece 22 320967 200932511 (for example, the inclination of the sneaker is better. When the field is at the position of the bottom dead center), the towel is used in step S12. Adding ^ 3 10 tilt adjusts the stroke position of the red body device 13. - Mode, adjustment ο * Pair = even: = first 3 = _ machine " The connecting member 33 can effectively perform the adjustment of the steps. Increasing the direction of the tilting body L=ir (for example, adjusting the tilting adjustment cylinder in the whole device 15;:: toward) 'by tilting, the target press and the machine simulator are the same, The difference in inclination is reduced or eliminated. The configuration of the tilt adjusting device 15 for performing the step S12 during the press processing can also be controlled to control the stroke position by controlling the pressure of the tilting cylinder. The h body device is two. The tilt adjusting device 15 also directly controls the stroke as shown in Fig. 20 or Fig. 21.

The Q 0 map adjusts the configuration of the pressing device U of the slider = body device 13 by actively controlling the tilt 敕 ^, that is, the pressure in the chamber. As shown in Fig. 2, the inclination is adjusted when tilting, so that the device, the control device l5b = the adjustment device, and the five force command device (5) have the power supply for the wheel. . The data input unit (for example, the inclination of the interface, the target tilt, and the m-disk to be described later) of the data of the target target of 320967 23 200932511 is based on the pressure command value of the input 13 . Tilt; tilt to adjust the heart of the red body device, ^ the bottom of the way is not. For each fem. or experiment m 1 complex pressure value 'by theoretical calculation, the complex array of people adjusts the pressure value of the cylinder device 13 and pre-records and memorizes the pressure control device 15b #你μ女遮丄〇 Oblique adjustment (4) device 13: = command value, and the pressure detection value from the pressure sensor that detects each tilt pi, nAiB., ΈΛ., pressure is controlled by the pressure of the red material set 13 to the local force command value The oil pressure control circuit 15c. The hydraulic control circuit 15c is supplied to the hydraulic pressure of each of the inclined orthotic devices 13 by the control unit 15b.乂 Control As the control of the =3 control and the acquisition of the tilting characteristic, it is also possible to press the 加工 裎 position! 2i! By actively adjusting the inclination of the tilt adjustment cylinder device is, the tilt adjustment device 16 of the tilt adjustment device when the tilting of the slide member 3 is tilted is shown by the TM^ device 165. The tilt adjustment device 16 has: The position command a controls the device wb and the hydraulic control circuit i6c. The resource device _ has an interface such as an interface for inputting the target tilt, a panel 'keyboard, and the like', and outputs a stroke position command value for each tilt adjustment cylinder based on the input = target tilt and a tilt characteristic to be described later. The tilt characteristics were obtained in the following manner. Needle 320967 24 200932511 For each of the plurality of tilting adjustment cylinder devices 13, the respective punches 3 of the other three tilting adjustment red body devices 2 are obtained by theoretical =, cis, or experiment respectively. Tilting, and prior to this relationship, has been recalled to the position command device 16a as the tilt characteristic. The control device 16b sets the detection value ST according to each stroke position command value and each stroke detected by the punching sensor for detecting each tilt adjustment cylinder 13 to make each tilt adjustment The hydraulic pressure control circuit 16c is controlled by the control device 16b so that the stroke position of the cylinder block Ο device 13 is the stroke position command value, and the oil pressure supplied to each of the tilt avoidance devices is controlled. . Further, the acquisition of such control and tilt characteristics can be performed as a target during press working. Right, according to the tilt adjustment of the slider 3 described above, the tilt of the slider can be adjusted by adjusting the stroke position of the tilt adjustment cylinder p device 13. Therefore, the machine difference associated with the inclination of the rushing/month 3 can be reduced or eliminated. Further, since the relative position of the I/moon member driving device 5 and the slider 3 is changed by the change in the stroke position of the tilt adjusting cylinder device 13, the tilt of the slider 3 during the press working can be effectively adjusted. Since the stroke position of the body device 13 is adjusted by (4) tilting, the amount of the joint member 33 when the C is added to the king is adjusted, so that the joint member is

The adjustment in Kt can effectively adjust the amount of deformation of the slider during press working. Since the plurality of tilt adjustment rainbow body devices 13 respectively apply loads to the plurality of portions of the sliders 3 of 25 320967 200932511, the inclination of the sliders 3 can be adjusted more finely by adjusting the tilting body devices 13' by the staff member. Therefore, the machine difference can be further reduced or eliminated. Since the rigidity of the connecting member 33 of the differential simulator 1G is higher than the rigidity of the connecting member of the analog pressing machine, the tilt adjusting red body is adjusted in the direction in which the rigidity of the set 13 is lowered by tilting the red body. The stroke position of the device η can effectively adjust the inclination of the slider 3. Further, the adjustment method of Fig. 19 and the adjustment method of Fig. 3 or Fig. 4 can be performed in parallel. For example, first, the adjustment of the rainbow body device 9 is not performed, and the tilting adjustment of the rainbow body device 13 is performed to adjust the inclination of the slider 3, and then the adjustment of the cylinder device η is not performed. The adjustment of the change of the slider 3b is performed by performing the adjustment of the deflection adjustment cylinder device 9. Further, the adjustment method of FIG. 19 and the adjustment method of FIG. 3 or FIG. 4 may be alternately performed alternately until the inclination of the slider 3 and the deviation of the mold holding member are sufficiently reduced or eliminated. stop. [Buffering characteristic simulation] A first configuration example of the buffer control device 19 is shown in Fig. 22. The buffer control device 19 has a movable portion position detecting t set 19a, a thrust command device 19b, a thrust detecting device 19c, and a thrust control device i9d. The movable portion position detecting device 193 is for detecting the position of the movable portion 17 & (the middle portion in Fig. 1 is the stroke position of the hydraulic pressure rainbow), and may be, for example, a linear scale wear scale. The thrust command device (10) has the above-described memory unit, and outputs a command thrust value in accordance with a thrust pattern recorded in the memory unit and a detected position from the movable portion na from the position detecting device 19a of the movable portion 320967 26 200932511. The thrust detecting device 19c is for detecting the upward thrust of the movable portion 17a. The thrust control device 19d controls the movable portion 17a in accordance with the command thrust value (command value of the upward thrust) from the thrust command device i9b and the upward thrust value detected by the thrust detecting device 19c. Further, the above memory system has a plurality of movable portion operation patterns, and the buffer control device 19 has an operation portion, and the operator can operate the operation portion to select whether or not to implement any of the plurality of movable portion actuation forms. The thrust detecting device 19c has a first pressure sensor 19c-i for detecting the pressure in the upper cylinder chamber and outputting the pressure detection value, and a second pressure sensor 19c-2 for detecting the lower cylinder chamber. And outputting the pressure detection value; and the thrust calculation unit 29c_3 calculates the movable value based on the pressure detection value from the second pressure sensor 19c-1 and the pressure detection value from the first pressure sensor 19c-2. The upward thrust of the portion 17a. The thrust control device 19d has control signal output means 19d-j and hydraulic pressure circuit 19d-2. The control signal output means 19d-j outputs a thrust control signal based on the command thrust value from the thrust release device 19b and the upward thrust value detected by the thrust detecting means 19c. The hydraulic circuit 19d-2 controls the hydraulic pressure of the cylinder chamber (in the example of Fig. 22, the upper cylinder chamber and the lower cylinder chamber) by the thrust control signal. For example, the hydraulic circuit 19d-2 has an oil dust source 37 and a switching valve (servo valve) 38 controlled by the above-described thrust control signal, and the pressure from the oil pressure source 37 is controlled by the switching valve 38. The oil is supplied to the upper cylinder chamber or the lower cylinder chamber, and the oil of the lower cylinder chamber or the upper cylinder chamber is discharged to the oil sump. 320967 27 200932511 Further, the buffer control device 19 has a slider position detecting device 19e. The slider position loosening device 19e is for detecting the lifting position of the slider 3. The slider position detecting device 19e may further include: a rotation angle sensor (for example, a rotary encoder) for detecting a rotation angle of the servo motor or a rotation angle of the driving gear 5a that drives the slider 3 The rotation position of the slider and the calculation unit 'calculate the elevation position of the slider 3 based on the rotation position detected by the rotation angle sensor. Alternatively, the slider position detecting means 19e may be a position sensor (for example, a linear scale) for directly detecting the lifting position of the slider 3, in order to lock the movable portion 17a at its upper limit position, the upper limit is broadcasted. The stopper member 2 is set to the differential simulator 1Q. The upper limit stop member 22 is for locking the movable portion 17a at the upper limit position so that the movable portion i?a does not rise above the upper limit position. The upper limit stop member 22 secures the frame of the simulated press 10 (e.g., the bed 31). And the control of the buffer control device 1 g Lu lacks ^山# 〇Based on the use of the slider position detection to install the 2 ship-b position, it is judged that the slider 3 has reached the opening and the detection of the slider 3 = the upper limit Upward of the movable part of the member 22: Set: Department: In addition, the control rim is turned off 19d~~i Wei 摅 _ = when the movable part 17a is applied to the sliding member 3, the Z starts to move according to the movable Operation of the second part: The start of the generation of the bit is based on the buffer mode of the first configuration example of the buffer control device 130967 28 200932511. Fig. 23 is a view showing a mold cushioning device for a simulated object press. In the figure, a 17b cushion, an AS cylinder, an AT air tank, and a 22-stage upper limiter are used. In this example, the simulation target buffer characteristic of the simulation target press is obtained by the buffer characteristics obtained by enclosing the cylinder AS having a specific air pressure and the air box AT, and the damping force is determined by enclosing the air pressure. Figure 24 shows the analog object buffering characteristics at this time. At this time, in the standby state before the press working, the upper limit stop member 22 receives the upward thrust of the cylinder AS. The slider 3 descends from this state, and a cushioning force is generated from the point at which the slider 3 starts to apply a downward load to the cylinder AS. This cushioning force compresses the sealed air pressure of the cylinder chamber of the air cylinder AS by the lowering of the slider 3, thereby raising the slider 3 by the lowering. Fig. 25 is a flow chart showing the buffer simulation operation of the first configuration example. In the step S21, before the slider 3 and the upper die are applied with the workpiece to the lower side of the die cushioning device 17, the 0 piston 17a having the upward thrust is applied to the upper limit stopper 22. Standby. That is, in the standby state before the press working, the buffer control device 19 controls the mold cushioning device 17° so as to give the movable portion 17a an upward thrust of a specific magnitude, and in step S22, the slider 3 gradually descends. The control signal output means 19d-1 judges whether the slider 3 and the upper mold have reached the front position immediately before the workpiece reaches the buffering force immediately before the application of the downward load to the mold cushioning device 17. The control signal output means 19d_1 performs the judgment of 29 320967 200932511 based on the detection position of the slider 3 from the slider position detecting means 19e. When the control signal output device 丨9 d-1 judges that the slider 3 has not reached the board (four), the judgment of the step milk is performed. When the control signal output device ship-! judges that the slider 3 has reached the position where the above-mentioned cushioning force is about to be generated, it proceeds to step S23. In step S23, the control signal output means "u-slipper 3" = up to the money impulse (4) to generate (four) material, and the control of the upward thrust reduction to the movable portion 17a. For example, the control of the wide output 舻 is performed to control the pressure oil discharge of the cylinder chamber of the hydraulic cylinder (Fig. 22::: transmission = cylinder chamber), thereby lowering the thrust on the 欤'. In the step S24 of the piston 17a, it is judged that the buffering force applied to the downward load by the slider 3 and the upper zirconia mode buffer device 17 has reached the start of the signal output device l9d-i. position. The detection position of the slider 3 of the control W is controlled, and when the position detecting and discharging device 19d-1 judges that the slider 3 has not reached the self-control signal transmission, the determination of step S24 is repeated at any time. When the control generates position-1, it is judged that the slider 3 has reached the above buffering force. ^=Set the coffee to step 9Ε; · When the king position is entered, the fourth is in the (4) s24, and the control signal output device continues to decrease by π (four). Performing (4) push-up of the plug i:a: in step S25, 'determine that the slider 3 has reached the above-mentioned buffer force type=========================================== The slider position detecting device 丨9 e slide position 320967 30 200932511 detection value, it is judged that the slider 3 has reached the far distance....., t. ^ ^, when the iron inquiry force starts to generate the position, it will come from the thrust day·? The command wheel of the device 19b is smashed and the thrust value is increased, and the thrust value from the movable portion 17a of the thrust detecting device 19c is pushed up, m / ± R 17 thrust detection value is compared 'at any time: Τ二之The control position 19b of the upward thrust following command thrust value and the detected position of the upper escape slider are not detected, and the detected position of the movable portion 17a of the movable portion position detecting device 19a is detected, and the command thrust value is output at any time. Figure 26 is a diagram showing the displacement of the movable portion 17a (stroke position of the hydraulic cylinder, π displacement), the upward thrust of the movable portion 17a, and the movable portion 17a in the case of the flow chart of the π-Fig. + $b diagram. A graph of the upward load (ie, the buffering force) of the & μ of the slider 3 with respect to time. Further, in the graph of the upward thrust curve and the buffer force in the movable portion of the second diagram, the solid line indicates the result of the buffer simulation operation of the buffer control device 19 of the first configuration example, and the broken line indicates the simulation target. Further, in Fig. 26, the buffering portion 3 is about to start before the downward load is applied to the piston 17a, and the front position is about to be generated. Since the upward thrust of the movable portion 17a is lowered, the slider 3 can be avoided. Shortly after the upper mold applies a downward thrust to the mold cushioning device 17, the cushioning force becomes excessive. Further, in a state in which the movable portion 17a is locked to the upper limit stopper member 22, the damper control device 19 applies the upward thrust of the same magnitude as the initial upward thrust of the movable portion 17a set to the movable portion operation mode to the movable portion. Since the portion 17a is at the start time of the operation mode of the movable portion, the difference between the initial upward thrust force set in the operation mode of the movable portion and the upward thrust force of the actual movable portion 17a can be reduced or eliminated. Next, the configuration of the buffer control device 21 of the second configuration example is described as 320967 200932511. The buffer control load control device 19 of the second configuration example is provided. In Item 22. Referring to Fig. 27, the buffer control of the second configuration example is shown. The buffer control device I 21 includes a body force command device 21b for the movable portion position detection 21, a thrust detecting device 21c, a thrust control device 2a, a movable portion position detecting device 2ia of the second configuration example, a guard device 2ld 〇21b, and thrust detection. The f21c is configured in the same manner as the second: device detection device 19&, the thrust command device 19b, and the thrust detection device. C has the control device 21d-1 of the 'thrust control skirt 21d' in the second configuration example in that the slider 3 is attached to the movable portion; the stroke position of the piston 17a is kept fixed before the load is released, and the self-sliding member 3 The buffering force for applying the downward load to the hydraulic cylinder starts to generate a position, and the slip: 3 is further lowered, whereby if the upward thrust of the movable portion 17a increases by two, a certain value is started, and control according to the operation form of the movable portion is started. . In the buffer control device 21 of the second configuration example, the slider position detecting device 21e may be omitted. The configuration of the hydraulic circuit 21d-2 of the thrust control device 21d of the second configuration example may be the same as that of the hydraulic circuit 19d-2 of the first configuration example. Next, the buffer simulation operation of the buffer control device 21 of the second configuration example will be described. Fig. 28 is a flow chart showing the buffer simulation operation of the buffer control device 21 according to the second configuration example. Further, in this case, the buffering characteristic of Fig. 24 is also the buffering characteristic of the simulation object. In step S31, the thrust control device 21d stands by in response to the detection position of the piston 17a from the position detecting device 21a of the movable portion 320967 32 200932511, and holds the piston 17a at a specific buffer position. In this case, the pressure of the upper cylinder chamber and the lower narrative chamber of the hydraulic cylinder may be set to a fixed value by the thrust control device 21d. For example, the switching valve 38 may be set to the state of Fig. 27 in advance. Then, the slider 3 is lowered to come into contact with the mold cushioning device 17 to push the movable portion 17a downward. In step 32, it is judged whether or not the push oil of the movable portion 17a generated by the slider 3 is pushed down, and whether or not the pressure oil of the cylinder chamber of the hydraulic cylinder is compressed, so that the upward thrust of the movable portion 17a reaches a specific value. This judgment system control signal output means 21d_1 is performed in accordance with the thrust detection value from the thrust detecting means 21c. Again, this determination is repeated at any time until the upward thrust reaches a certain value. When it is judged that the upward thrust has reached the above specific value, it proceeds to step S33. In the step S32, in this example, the switching valve 38 can also be in the state of Fig. 27. q, in step S33, when the control signal output means 21d-1 determines that the upward thrust has reached the above specific value, the command thrust value from the thrust command device 21b and the upward thrust detection value from the movable portion 17a of the thrust detecting device 21c are made. In comparison, a control signal for causing the upward thrust of the movable portion 17a to follow the command thrust value is outputted at any time. Further, the thrust command device 21b has no relation to the command thrust value from the thrust detecting device 21c, and outputs the command thrust value at any time in accordance with the thrust form and the detected position from the movable portion 17a of the movable portion position detecting device 21a. Figure 29 is a view of the flow chart according to Figure 28, the movable part 33 320967 200932511

The displacement of 17a (the stroke displacement of the hydraulic cylinder), the upward thrust of the movable portion 17a, and the upward load (i.e., the cushioning force) of the movable portion 17a acting on the slider 3 are plotted against time. Further, in the graph of the upward thrust curve and the buffering force of the movable portion in Fig. 29, the solid line indicates the result of the buffer simulation operation by the buffer control device 21 of the second configuration example, and the broken line indicates the simulation target. Further, in Fig. 29, since the slider 3 is lowered from the state in which the movable portion 17a stands by the specific position by the thrust control device 21d, the downward load acts on the movable portion 17a from the slider 3, whereby When the upward thrust of the movable portion 17a reaches a certain value, control according to the thrust form is started. Therefore, even if the upper limit stop member 22 is not used, the cushioning characteristic of the target can be simulated only by the hydraulic servo control function of the buffer control device 21. ' [Pressure Adjustment Method by Dust Distribution Adjustment Plate] Fig. 30 is a general flow chart showing the pressure distribution adjustment method of the machine differential simulation press of the present invention. In Fig. 30, the method of the present invention is constituted by the steps of S41 to S46. In step S41

_ Tian Hao narrowly obtained deformation data for the deformation measuring instrument of the rolling press. The simulated object press is a mass production press such as a mold user. Further, the deformation measuring instrument is used to measure the deformation of the mold holding members (the holders 25 and 3b) at the time of press working. In step S42, it is estimated from the obtained deformation data to calculate the contact Lili distribution of the simulated press. The calculation is based on a cis calculation or theory = 仃. The obtained contact pressure distribution is set as "visual contact pressure: 320967 34 200932511, and Fig. 31 is a schematic diagram of steps S43, S44. In step S43, the shim adjustment position is set. Between the socket 25 and the slider 3 and the support surface of the mold (not shown), the cushion pin 17d, the deflection adjusting cylinder device 9 and the like do not interfere with each other, and are set on both sides and the socket as shown in Fig. 31A. 25 and the position of the slide plate 3b and the mold support surface. The position of each spacer adjustment is k (k = 1, 2, 3, ... N). In step S44, the unit thickness of each spacer adjustment position is calculated. The rate of change of the contact pressure distribution generated by the pad® sheet, that is, the spacers of the respective thickness adjustment positions in the FEM mode as shown in FIG. 31B are used as the forced displacement, and the mold is calculated as shown in FIG. 31C.

The rate of change of contact pressure of I. The rate of change of the contact pressure distribution generated by the spacer of the unit thickness of each of the spacer adjustment positions is dPk (x, y). In step S45, the required Q pad adjustment amount for obtaining the target contact pressure distribution is calculated. That is, the difference between the target contact pressure distribution and the contact pressure distribution after the spacer adjustment is expressed by an appropriate evaluation function, and the amount of spacer adjustment which minimizes the evaluation function is obtained. Such an evaluation function may also be, for example, P of the following formula (5). In the following formula (5), Ρτ(χ, y) is the target contact pressure distribution of the simulated target press, and P〇(x, y) is the contact pressure distribution before the adjustment of the differential press 10, a(k) The amount of gasket adjustment required to adjust the position of each gasket, and the required gasket adjustment amount a(k) to minimize P by the method of least squares 35 320967 200932511 * P== (P〇(x, y)+ Ea(k)xdPk(x, γ))2_Ρτ(χ, y)2 (5) ' That is, in step S43, the mode is first calculated by the FEM, and no spacer is used. The contact pressure distribution at the time of adjustment was previously determined as Ρϋ(χ, y). Then, N (the π-part in Fig. 31A) pad setting position is set. In step S44, in the FEM § ten calculation mode, the unit gasket adjustment amount is given to each of the n points as the forcible displacement, and the rate of change of the contact pressure distribution at this time is previously stored as dPk (x, y). Set the required shim adjustment amount for each point to a(k) ’ as the target ❹

Pt(x, y), and calculated P〇(x, y) and dPk(x, y), in formula (5), determine the required gasket adjustment amount a(k) to minimize N) . In step S46, it is confirmed that the contact pressure distribution coincides with the target by applying the analysis of the required gasket adjustment amount a(k). In step S46, if there is no problem, the pressure distribution adjustment of the present invention is ended. In case of a problem, steps S43 to S45 are repeated. According to the pressure adjustment method described above, the slab adjustment position is set in step §43, and the rate of change of the contact pressure distribution generated by the 单位 sheet of the unit thickness of each of the shims adjustment positions is calculated in step S44, and is calculated in step S45. Since the required blade adjustment amount of the target contact pressure distribution is obtained, it is possible to prepare the surface pressure distribution adjusting plates 23A and 23B having the spacer-adjusted thicknesses of the respective pad adjustment positions at the respective pad adjustment positions. Further, by holding the surface pressure distribution adjusting plates 23A, 23B between the socket 25 and/or the sliding plate and the supporting surface of the mold, the difference in the contact pressure distribution between the cookware can be reduced or eliminated. 10 As described above, in the differential simulator 23 36967 200932511 of the embodiment of the present invention, (1) the tilting phase of the differential slider 3 related to the shift distribution of the mold holding member is _ machine difference, (3) the mold buffer The difference in characteristics is related to, and (4) the difference in the contact distribution between the mold and the mold 3b and the mold is all reduced or eliminated. Thereby, the stamping (four) difference between the mold and the lower mold can be reduced or eliminated by the difference between the simulated object press and the engine. The present invention is not limited to the above-described embodiments, and various modifications can of course be made without departing from the spirit and scope of the invention. 0 For example, a single one-turn adjustment catching device 9a' for applying a load to the socket 25 is provided, but a plurality of flexing adjustment cylinders for applying an upward load to the socket 25 may be provided. Similarly, although a single deflection adjusting cylinder device 9b for applying a load to the slider 3b is provided, a plurality of deflection adjusting cylinder devices for applying a downward load to the slider north may be provided. Thereby, the deflection distribution of the socket 25 or the slider 3b can also be made coincident or similar to the target deflection distribution. In the above embodiment, the load applying means is a deflection adjusting cylinder block device 9, but may be a spring having a rigidity that causes the set load to act on the seat or the slider 3b, respectively, instead of the deflection adjusting cylinder. Body device 9. In the above-described embodiment, the load applying means is a deflection adjusting cylinder device 9 that uses hydraulic pressure. However, a piezoelectric element or a magnetostrictive element may be used to form a load applying means instead of scratching. The cylinder device 9 is adjusted. In the above embodiment, although the inclination of the slider of the simulation target press during the press working is measured, and the measured tilt of the slider is set as the target tilt, the non-contact between the upper mold and the workpiece may be measured. Die during stamping processing 320967 37 200932511 The tilt of the slider of the intended press and the tilt of the measured slider is set to the target tilt. At this time, the adjustment of the inclination of the slider of the differential simulation press 10 is also targeted to the inclination of the slider during the non-pressing process. Further, at this time, it is preferable to perform the inclination adjustment by supplying the liquid to both the upper cylinder chamber and the lower cylinder chamber of the tilt adjustment cylinder device 13. In addition to the configuration of the tilt adjusting cylinder device 13 and the tilt adjusting cylinder device 15 and the slider tilt adjusting method when the tilt of the slider during the non-pressing processing is adjusted, the other embodiments are the same as the above-described embodiment. The slider drive mechanism 5 uses the drive gear 5a and the link 5b to raise and lower the slider 〇3. However, the slider drive mechanism may be constituted by another means for raising and lowering the slider 3. In the above embodiment, although four tilt adjustment cylinder devices 13 are provided, it is also possible to provide a plurality of (including one) tilt adjustment cylinder devices 13 other than four. In the above embodiment, the die cushioning device 17 is constituted by a hydraulic cylinder device. However, according to the present invention, the die cushioning device 17 may be constituted by another liquid cylinder or cylinder. At this time, the target cushioning characteristic (the movable part operation form) can be obtained by controlling the hydraulic pressure or the air pressure of the cylinder chamber (preferably the upper cylinder chamber and the lower cylinder chamber) of the hydraulic cylinder or the cylinder block. In a manner, the buffer control device controls the above hydraulic pressure or air pressure. Further, according to the present invention, the die cushioning device 17 is not limited to the cylinder device, and may be another means for controlling the upward thrust. For example, the die cushioning device 17 may be a drive motor including a servo motor or the like and a conversion mechanism that converts the rotational driving force of the drive motor into an upward thrust (for example, a ball screw 38 320967 200932511 =::Γ at this time] The reduction of the downward thrust is performed by lowering the supply voltage of the poem driving motor. As shown in the first lap, in the case of the mold buffering device 17 f in which the plurality of hydraulic cylinders are provided, the mold cushioning device 17 can also be used in the body compartment. The plurality of mold buffering devices 17 are controlled by the control device to control the plurality of mold buffering devices 17 by the control device. The mold cushioning device 17 is provided with a slow == for the piston, and the movable portion m of the mold-type buffering device 17 is moved to the surface of the cylinder portion 31 or the like, and the operation form of the upper and lower movable portions with respect to the piston is The upward thrust of the movable portion 17a is in the form of a thrust of the position of the portion 17a, but the present invention is not limited thereto. '2: The movable portion can also be operated in the form of 2 forces for the position or time of the slider 3. this In this case, the buffer control device controls the die cushioning device 17 in such a manner that the movable portion m operates in accordance with the operation mode of the movable portion in accordance with the cardiac measurement position or the measurement time of the slider 3. [Simple description of the drawing] FIG. FIG. 2 is a cross-sectional view taken along line A-A of the first embodiment, and FIG. 3 is a view showing the overall rigidity adjustment method of the third embodiment of the differential simulator. Fig. 4 is a general flow chart showing the rigidity adjustment method of the second embodiment of the differential simulator. 320967 39 200932511 5A to 5D are the i-th embodiment of the rigidity adjustment means of the present invention. Fig. 6A and Fig. 6B are views showing a second embodiment of the rigidity adjusting means of the present invention. Fig. 7A and Fig. 7B are views showing a third embodiment of the rigidity adjusting means of the present invention. Fig. 8A Fig. 8D is a fifth embodiment of the rigidity adjusting means of the present invention, and the fifth embodiment of Fig. 9A, Fig. 9A and Fig. 9B are the fifth embodiment of the rigidity adjusting means of the present invention. Fig. 10A to Fig. Fig. 6 is a view showing a sixth embodiment of the rigidity adjusting means of the present invention. Fig. 11 is an embodiment of the sixth embodiment. Fig. 12 is a diagram showing the relationship between the initial sealing pressure of the accumulator gas and the support rigidity of the cylinder. Figs. 13A and 13B are diagrams of the rigidity adjusting means of the present invention. 7 Embodiments Fig. 14 is an embodiment of the seventh embodiment. Fig. 15 is a graph showing the relationship between the volume elastic modulus and the pressure. Fig. 16 is the reaction force of the hydraulic cylinder due to the change of the initial pressure. The relationship between the stroke compression amount and Fig. 17 shows the target deflection distribution of the socket when the punching load is not eccentric, and the deflection distribution of the socket after the adjustment of the cylinder device by the deflection adjustment. Indicates the target deflection of the socket when the stamping load is eccentric. 320967 40 200932511 The distribution of the deflection of the socket after adjustment by the deflection adjustment cylinder device. Fig. 19 is a flow chart showing a method of adjusting the tilt of the slider. Fig. 20 is a view showing a first configuration example of the tilt adjusting device. Fig. 21 is a view showing a second configuration example of the tilt adjusting device. Fig. 22 is a view showing a first configuration example of the buffer control device. Fig. 23 is a view showing the configuration of a buffer device for simulating an object. Figure 24 is a diagram showing the buffer characteristics of the simulated object. Fig. 25 is a flow chart showing the buffering operation of the buffer control device according to the first configuration example. Fig. 26 is a view showing the result of simulating the cushioning characteristics of Fig. 24 by the buffer control device of the first configuration example. Fig. 27 is a view showing a second configuration example of the buffer control device. Fig. 28 is a flow chart showing the buffering simulation operation of the buffer control device according to the second configuration example. Fig. 29 is a view showing the result of simulating the buffering characteristic of Fig. 24 by the buffer control device of the second configuration example. Figure 30 is a general flow chart showing the pressure distribution adjustment method. 31A to 31C are schematic views of steps S43 and S44. [Main component symbol description] 3 Slider 3a Slider body 3b Slider 5 Slider drive mechanism 5a Drive gear 5b Conversion mechanism 7 Balance cylinder 9 Flex adjustment cylinder device 9a Lower rigidity adjustment device 9b Upper adjustment device 41 320967 200932511 10 differential simulator 19 deflection adjustment device 13 tilt adjustment cylinder device 15, 16 tilt adjustment device 15a pressure command device 15b, 16b control device 15c, 16c hydraulic control circuit 16a position command device 17 mold buffer device 17a movable Portion (piston) 17b cushion 17c pin plate 17d cushion pin 19, 21 buffer control device 19a, 21a movable portion position detecting device 19b, 21b thrust command device 19c, 21c thrust detecting device 19c-1 first pressure sensor 19c- 2 second pressure sensor 19c-3 thrust calculation unit 19d > 21d thrust control device 19d-1, 21d-1 control signal output device 19d-2, 21d-2 hydraulic circuit 19e slider position detecting device 20 column 22 Upper limit stop member 23A ' 23B Surface pressure distribution adjustment plate 25 Seat 27 Upper cross member 29 . Convex flat surface 31 Lower load support member (bed 33 Linking member 34 Bracket 37 Oil pressure source 38 Switching valve (servo valve) A Hydraulic cylinder AC Accumulator AS Cylinder AT Air box B Servo controller C Oil pressure control circuit dx Displacement amount E Direct acting mechanism G1 ' G2 Stand P load 320967 42

Claims (1)

200932511 VII. Patent application scope: A machine differential simulation press, which is a mold holding member of a mold, and a supporting member at the periphery of the dust-removed workpiece, the machine is different from the core member. The means is characterized in that: 2. = mold holding member: the second cut = the load applied to the cow that does not support the adjustment of the mold holding member, and ο as claimed in the second paragraph of the patent application: The duty means is for the above-mentioned money press, wherein the negative yaw adjusts the red body to be swayed, and the mold holding member applies a negative cut to the fulcrum adjusting device, and acts on the mold transfer member = adjustment Adjusting the red body of the winding is as follows: A holder having a retaining member and a slide plate, wherein the mold is as described in the second item of the patent application. The load is performed according to the eyepiece, wherein the damage is caused by: the deflection of the mold holding member; the value of the stamping process is calculated as the load of the target amount of the cranking and the deflection adjusting device is The two-cylinder device of the mold holding member adjusts the above-mentioned deflection adjusting cylinder to the above-mentioned machine as calculated in the scope of the application of the above-mentioned patent item = the system holds the workpiece in the upper machine, the above-mentioned mold The mold and the lower mold, the machine is different from the upper 320967 43 200932511 sliding member, the upper mold is installed under the lifting movement; the sliding member driving mechanism causes the sliding member to lift and generate the stamping forming force; The cylinder device is adjusted to apply a load to the slider by changing the inclination of the slider to change the inclination of the slider; and the tilt adjustment device for adjusting the stroke position of the tilt adjustment cylinder device. 6. The machine differential simulation press according to the first aspect of the patent application, wherein the mold is an upper mold and a lower mold for holding a workpiece in a vertical direction, and the machine is equipped with a sliding member. The upper mold is mounted on the lower surface to perform the lifting movement; the mold cushioning device has a movable portion that is lowered in a state in which the workpiece is held between the upper mold and the upper mold; and a buffer control device for controlling the movable portion And the buffer control device has a memory portion in which a movable portion is operated, and the movable portion operates to impart a specific target buffering characteristic, and the buffer control device controls the movable according to the movable portion operation form. Department of action. 7. The machine differential simulation press according to claim 1, wherein a surface pressure distribution adjusting plate is provided between the mold holding member and the mold. 320967