WO2009096272A1 - Presse de simulation d'erreur machine - Google Patents

Presse de simulation d'erreur machine Download PDF

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Publication number
WO2009096272A1
WO2009096272A1 PCT/JP2009/050806 JP2009050806W WO2009096272A1 WO 2009096272 A1 WO2009096272 A1 WO 2009096272A1 JP 2009050806 W JP2009050806 W JP 2009050806W WO 2009096272 A1 WO2009096272 A1 WO 2009096272A1
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WO
WIPO (PCT)
Prior art keywords
press
mold
slide
deflection
load
Prior art date
Application number
PCT/JP2009/050806
Other languages
English (en)
Japanese (ja)
Inventor
Shusaku Yamasaki
Mitsuaki Hayashi
Takahiro Shimada
Original Assignee
Ihi Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ihi Corporation filed Critical Ihi Corporation
Publication of WO2009096272A1 publication Critical patent/WO2009096272A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/02—Die-cushions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0029—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height
    • B30B15/0035—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height using an adjustable connection between the press drive means and the press slide
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0029—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height
    • B30B15/0041—Control arrangements therefor

Definitions

  • the present invention relates to a machine difference simulation press capable of simulating a machine difference from a simulation target press.
  • dies Large press dies (hereinafter referred to as dies) used for mass production of automobile bodies and the like are very important for determining the value of automobiles. For this reason, in order to accurately transfer the car body design to the panel processing surface, the mold processing surface (press surface) is manufactured by the CAD / CAM system so that the panel plate thickness is offset to completely match. Yes. However, the mold pressure (lower mold and upper mold) and the press apparatus (bolster and slide) are deformed by the molding pressure during the press working, and the press surfaces of the lower mold and the upper mold do not completely match. For this reason, it is necessary to repeat the “mold matching operation” by skilled technicians in the final process of manufacturing the mold so that the press surfaces accurately coincide with each other during the press working.
  • the mold matching process is a process performed by a mold maker using a prototype press (mold matching at the manufacturer) and a process performed using a mass production press of a mold user (automobile manufacturer, etc.) (die matching by the user). There is.
  • the working time of the mold matching process is equivalent to 1/2 to 2/5 of the mold production time, and reduction of the mold matching process is strongly demanded for improving productivity.
  • Patent Document 1 has already been disclosed as a prior art related to the present invention.
  • a plurality of members that are elastically deformed are provided between a bed and a mold support plate to adjust the mold shape.
  • the mold matching by the user is usually 100 to 200 hours, which is more than 1/3 of the entire mold matching process.
  • the mold matching by the user has a stop loss of the press line in addition to the work cost. For this reason, the mold matching process by the user is strongly demanded for mold users (automobile manufacturers, etc.) to shorten the process time.
  • an object of the present invention is to provide a machine difference simulation press that can be adjusted so that the machine difference from the simulation target press can be reduced or eliminated by using a mass production press or the like as a simulation target press.
  • a machine comprising a mold holding member to which a mold for pressing a workpiece is attached, and a support member for supporting an outer peripheral portion of the mold holding member.
  • a differential simulation press A machine difference simulation press comprising load applying means for adjusting a deflection of the mold holding member by applying a load to a portion of the mold holding member that is not supported by the support member during press working.
  • the load applying means is a deflection adjusting cylinder device that applies a load to the mold holding member, and further, a load that the deflection adjusting cylinder device applies to the mold holding member.
  • a deflection adjusting device for adjusting is provided.
  • the mold holding member is at least one of a bolster and a slide plate.
  • die holding member at the time of press work can be adjusted with a load provision means.
  • the deflection distribution of the mold holding member can be matched or approximated with the deflection distribution of the mold holding member of the simulation target press. Therefore, the machine difference regarding the deflection distribution of the mold holding member can be reduced or eliminated.
  • the machine difference simulation press calculates the value of the load based on the target deflection amount so that the deflection of the mold holding member at the time of press processing becomes the target deflection amount. Equipped with load calculation device, The deflection adjusting device adjusts the deflection adjusting cylinder device so that a load applied to the mold holding member by the deflection adjusting cylinder device becomes the calculated value. Thereby, it is possible to automatically adjust the deflection of the mold holding member to the target deflection only by inputting the target deflection.
  • the molds are an upper mold and a lower mold that are pressed by sandwiching a workpiece in the vertical direction.
  • the tilt of the slide can be adjusted by the tilt adjusting cylinder device and the tilt adjusting device. Therefore, machine differences related to the tilt of the slide can be reduced or eliminated.
  • the molds are an upper mold and a lower mold that are pressed by sandwiching a workpiece in the vertical direction.
  • a cushion control device for controlling the operation of the movable part The cushion control device has a storage unit that stores a movable unit operation pattern for giving a predetermined target cushion characteristic, The cushion control device controls the operation of the movable part according to the movable part operation pattern.
  • the cushion control device controls the operation of the movable part according to the movable part operation pattern for providing the target cushion characteristic.
  • the target cushion characteristic of the simulation target press can be simulated, and the machine difference regarding the characteristic of the die cushion can be reduced or eliminated.
  • the machine difference simulation press includes a surface pressure distribution adjusting plate between the mold holding member and the mold.
  • the surface pressure distribution adjusting plate has a plurality of convex planes, and the height of each convex plane is set independently.
  • a mass production press or the like can be used as a simulation target press, and machine differences from the simulation target press can be reduced or eliminated.
  • FIG. 2 is a sectional view taken along line AA in FIG. 1. It is a whole flowchart which shows the rigidity adjustment method by 1st Example of a machine difference simulation press. It is a whole flowchart which shows the rigidity adjustment method by 2nd Example of a machine difference simulation press. It is 1st Embodiment figure of the rigidity adjustment means of this invention. It is 1st Embodiment figure of the rigidity adjustment means of this invention. It is 1st Embodiment figure of the rigidity adjustment means of this invention. It is 1st Embodiment figure of the rigidity adjustment means of this invention. It is 2nd Embodiment figure of the rigidity adjustment means of this invention.
  • FIG. 4 is a relationship diagram between an initial charging pressure of accumulator gas and cylinder support rigidity. It is 7th Embodiment figure of the rigidity adjustment means of this invention. It is 7th Embodiment figure of the rigidity adjustment means of this invention. It is an Example of 7th Embodiment. It is a related figure of a bulk elastic modulus and a pressure. FIG.
  • FIG. 6 is a relationship diagram between a hydraulic cylinder reaction force and a stroke compression amount due to a change in initial pressure.
  • the figure shows the target deflection distribution of the bolster and the deflection distribution of the bolster after adjustment by the deflection adjusting cylinder device when the press load is not eccentric.
  • the figure shows the target deflection distribution of the bolster and the deflection distribution of the bolster after adjustment by the deflection adjusting cylinder device when the press load is eccentric.
  • It is a flowchart which shows the inclination adjustment method of a slide.
  • the 1st structural example of the inclination adjustment apparatus is shown.
  • the 2nd structural example of the inclination adjustment apparatus is shown.
  • the 1st structural example of the cushion control apparatus is shown.
  • the structure of the cushion apparatus of simulation object is shown.
  • FIG. 1 is a configuration diagram of a machine difference simulation press according to a first embodiment of the present invention.
  • the machine difference simulation press 10 includes a slide 3, a slide drive mechanism 5, a counter balance cylinder 7, a deflection adjusting cylinder device 9, a deflection adjusting device 11, a tilt adjusting cylinder device 13, a tilt adjusting device 15, a die cushion device 17, and a cushion control device. 19 and surface pressure distribution adjusting plates 23A and 23B.
  • the slide 3 moves up and down with an upper die (not shown) fixed to the lower surface.
  • the slide 3 has a slide body 3a and a slide plate 3b fixed to the lower surface of the slide body 3a.
  • the slide main body 3a is a support member for the slide plate 3b and supports the outer peripheral portion of the slide plate 3b.
  • the upper die performs press working with a workpiece sandwiched between a lower die (not shown) fixed to the upper surface of a bolster 25 described later.
  • the slide drive mechanism 5 connects one or a plurality of servo motors (not shown), a drive gear 5a provided in the upper crown 27 and driven to rotate by the servo motor, the drive gear 5a and the slide 3. It has a conversion mechanism 5b (link in the example of FIG. 1) that converts the rotational movement of the drive gear 5a into the vertical movement of the slide 3.
  • the counter balance cylinder 7 applies an upward force that balances the weight of the slide 3 and the upper mold to the slide 3 so as to facilitate the vertical movement thereof.
  • the deflection adjusting cylinder device 9 applies a load to the mold holding member (in the example of FIG. 1, the bolster 25 and the slide plate 3b) during press working.
  • the outer periphery of the bolster 25 is supported by a support member (a carrier 34, which will be described later in the example of FIG. 1), and the deflection adjusting cylinder device 9 applies an upward load to the bolster portion that is not supported by the support member (carrier 34).
  • Including a lower rigidity adjusting cylinder 9a In the example of FIG. 1, the upper stiffness adjusting cylinder 9 b applies an upward load to the central portion of the bolster 25.
  • the outer periphery of the slide plate 3b is supported by a support member (slide main body 3a in the example of FIG.
  • the deflection adjusting cylinder device 9 is placed on the slide plate portion not supported by the support member (slide main body 3a).
  • An upper stiffness adjusting cylinder 9b that applies a downward load is included.
  • the upper rigidity adjusting cylinder 9b applies a downward load to the center portion of the slide plate 3b. Only one of the lower rigidity adjustment cylinder 9a and the upper rigidity adjustment cylinder 9b may be provided.
  • the deflection adjusting device 11 adjusts the load that the deflection adjusting cylinder device 9 acts on the mold holding member during press working.
  • the deflection adjusting device 11 can be separately provided with a deflection adjusting device 11 for the upper stiffness adjusting cylinder 9b and a deflection adjusting device 11 for the lower stiffness adjusting cylinder. The configuration of the deflection adjusting device 11 will be described later.
  • the tilt adjustment cylinder device 13 connects the slide drive mechanism 5 and the slide 3.
  • the relative position between the slide drive mechanism 5 and the slide 3 changes due to a change in the stroke position of the tilt adjustment cylinder device 13. That is, the slide drive mechanism 5 and the slide 3 are connected via the tilt adjustment cylinder device 13. Therefore, the inclination of the slide 3 with respect to the horizontal direction can be adjusted by adjusting the stroke amount (that is, the stroke position) of the inclination adjusting cylinder device 13.
  • FIG. 2 is a view taken along the line AA in FIG. 1 and shows only the vicinity of the slide 3. In the example of FIGS.
  • each of the tilt adjustment cylinder devices 13 is fixed at one end portion near the outer peripheral portion of the slide 3, and the other end portion is provided.
  • the slide drive mechanism 5 is rotatably connected to the link 5b by a pin.
  • the tilt adjusting device 15 is for adjusting the stroke position of the tilt adjusting cylinder device 13.
  • the tilt adjusting device 15 indirectly adjusts the stroke position of the tilt adjusting cylinder device 13 by controlling the pressure of the tilt adjusting cylinder device 13 or directly controls the stroke position of the tilt adjusting cylinder device 13.
  • the tilt adjustment device 15 can adjust the stroke position of each tilt adjustment cylinder device 13 independently of the stroke position adjustment of the other tilt adjustment cylinder devices 13.
  • the die cushion device 17 is a hydraulic cylinder device, and descends with a workpiece sandwiched between the upper die while applying a downward thrust during press working.
  • a movable portion 17a (piston in FIG. 1) that applies an upward load to the surface, a cushion pad 17b pushed upward by the upper end of the movable portion 17a, a pin plate 17c supported by the cushion pad 17b, and a pin plate And a cushion pin 17d supported by 17c.
  • the cushion control device 19 controls the die cushion device 17 so as to give a target cushion characteristic.
  • the configuration of the cushion control device 19 will be described later.
  • the surface pressure distribution adjusting plates 23A and 23B are provided between the bolster 25 and the slide 3 (slide plate 3b in the example of FIG. 1) and a support surface of a mold (not shown). Thereby, the machine difference of the contact pressure distribution between dies is reduced or eliminated.
  • the surface pressure distribution adjusting plates 23A and 23B have a plurality of convex planes 29 on the contact surface with the mold. Each convex plane 29 has a shim adjustment thickness obtained by FEM, and the height of each convex plane 29 is set so as to reduce the difference in contact pressure distribution independently.
  • the surface pressure distribution adjusting plates 23A and 23B are preferably integrated, but may be shim plates that can be separated for each convex plane 29 and have independent thicknesses. A pressure adjustment method using the surface pressure distribution adjusting plates 23A and 23B will be described later.
  • the frame of the machine difference simulation press 10 includes an upper load support member 27 (crown in the example of FIG. 1) that receives an upward load from the slide 3 during press processing, and a lower load support member 31 that receives a downward load from the bolster 25 during press processing. (In the example of FIG. 1) and a plurality of connecting members 33 (in the example of FIG. 1, a plurality of tie rods).
  • the upper load support member and the lower load support member are connected by the connecting member 33 in a state where the upright 20 is sandwiched between the upper load support member 27 and the lower load support member 31.
  • the bed 31 supports a carrier 34.
  • the carrier 34 is a support member for the bolster 25 and supports the outer peripheral portion of the bolster 25.
  • FIG. 3 is an overall flowchart showing a stiffness adjusting method according to the first embodiment of the machine difference simulation press 10 of the present invention.
  • the method of the present invention comprises steps S1 to S8.
  • step S1 strain data is acquired from strain measurement of the simulation target press.
  • the simulation target press is, for example, a press for mass production of a mold user.
  • strain at the time of pressing the mold holding member (bolster 25 and slide plate 3b) is measured.
  • the deflection distribution of the simulation target press is estimated and calculated from the obtained strain data. This calculation is based on FEM calculation or theoretical calculation.
  • the obtained deflection distribution is defined as a “target deflection distribution”.
  • step S3 the deflection of the machine difference simulation press 10 of the present invention is calculated. This calculation is based on FEM as an evenly distributed load.
  • step S4 the load of the deflection adjusting cylinder device 9 described above is set. That is, the deflection adjusting cylinder device 9 is configured so that the bolster 25 or the slide plate 3b is pressed during the press process so that the deflection distribution of the bolster 25 or the slide plate 3b during the press process becomes the target deflection distribution or approximates the target deflection distribution. Set the load to be applied to the center of the.
  • step S5 the deflection calculation with the set load of the deflection adjusting cylinder device 9 is performed by FEM.
  • step S6 it is confirmed that the deflection distribution obtained by the deflection calculation is as intended.
  • step S7 the deflection calculation including the mold is performed by FEM.
  • step S8 it is confirmed that the influence of the mold is small. If there is no problem in steps S6 and S8, the deflection adjustment (rigidity adjustment) according to the present invention is terminated. If there is a problem, steps S3 to S7 are repeated.
  • the target deflection amount Wt is calculated by the following equation (1).
  • Wt is a target deflection amount of the die holding member at the time of press working in the machine difference simulation press 10.
  • Wt is a displacement amount at the center of the die holding member in the simulation target press.
  • Wt Pt / Kt (1)
  • Pt is a press load that acts on the mold during press working when the press work is performed with a simulation target press, and is different for each mold.
  • the press load Pt may be a total press load that acts on the mold during press working.
  • FIG. 4 shows the second embodiment in a flowchart.
  • a description will be given with reference to FIG.
  • Steps ST2 to ST5 Pt is previously determined for each die and Kt is previously determined for each simulation target press (steps ST2 to ST5).
  • a simulation target press A and a simulation target press B As an example, there is a simulation target press A and a simulation target press B.
  • the simulation target press A using the mold a or the mold b is simulated, and the simulation target press B using the mold c or the mold d is simulated.
  • the simulation target press A using the mold a or the mold b is simulated by the machine difference simulation press 10
  • the simulation target press B using the mold c or the mold d is simulated by the machine difference simulation press 10.
  • Pt a , Pt b , Kt A , Pt c , Pt d , and Kt B are obtained in advance.
  • Pt a upon pressing the simulated subject press A using a mold a, a pressing load acting on the mold a
  • Pt b upon pressing the simulated subject press A using a die b, gold It is a press load acting on the mold b
  • Pt c is a press load acting on the mold c at the time of press processing in the simulation target press B using the mold c
  • Pt d is the mold d used. This is the press load acting on the mold d during the press work in the simulation target press B.
  • Kt A is a deflection amount of the die holding member at the time of press processing in the simulation target press A, and is a value specific to the simulation target press A that does not change depending on the die.
  • Kt B is a deflection amount of the die holding member at the time of press processing in the simulation target press B, and is a value specific to the simulation target press B that does not change depending on the die.
  • Pt a and Kt A are obtained as follows. It performs pressing in simulated target press A using a mold a, obtaining a deflection amount Wa of Pt a mold holding member during the pressing.
  • Pt a is, for example, determined from the obtained distortion data by pasted strain gauges like the back surface of the mold a (ST2, ST3), the deflection amount Wa of the die holding member, a step S2 of the first embodiment You may obtain
  • Pt b as in the case of Pt a , pressing is performed with the simulation target press A using the mold b, and Pt b at the time of this pressing is obtained.
  • Pt c , Pt d , and Kt B are obtained in the same manner.
  • steps ST2 to ST5 are repeated, and the obtained Pt a , Pt b , Kt A , Pt c , Pt d , and Kt B are stored in a predetermined storage device, and the press load of the mold and the rigidity of the simulation target press are stored. Is made into a database (ST5).
  • the simulation target press B using the mold c or the mold d is simulated by the machine difference simulation press 10. The same applies to the case where the number of dies used in each simulation target press increases or decreases from the above example, and the case where the number of simulation target presses increases or decreases from the above example.
  • step ST1 when the data necessary for simulating the simulation target press (that is, the press load acting on the mold and the rigidity of the simulation target press) is not known, the metal used in each simulation target press.
  • the necessary data is obtained by performing steps ST2 to ST5 for each mold.
  • Pt a , Pt b , Kt A , Pt c , Pt d , and Kt B are obtained.
  • the target deflection amount Wt is calculated using the above equation (1).
  • a target deflection calculation device that performs the calculation of the second embodiment will be described.
  • the press load Pt acting on the die for each die in the above example, Pt a and Pt b for the simulation target press A and Pt for the simulation target press B).
  • c , Pt d ), rigidity Kt (Kt A , Kt B in the above example) is obtained for each simulation target press, and these data are stored in the storage device.
  • the target deflection calculation device uses the above equation (1) as described above.
  • a target deflection amount Wt is calculated and output to a load calculation device described later.
  • the machine difference simulation press 10 is configured such that the deflection of the mold holding member at the time of press working becomes the target deflection amount based on the target deflection amount obtained in the first embodiment or the second embodiment of the deflection adjusting method described above.
  • a load calculation device for calculating the value of the set load in step S4 is provided. This load calculation device is based on the deflection distribution / target deflection amount (preferably, the displacement amount at the center of the mold holding member) obtained by the calculation in step S2 or ST6 and the deflection characteristics of the machine difference simulation press 10. Thus, it may be a device that calculates the value of the set load in step S4.
  • This deflection characteristic includes the load that the deflection adjusting cylinder device 9 exerts on the mold holding member (preferably the central part) during the press working, and the deflection amount (preferably the central part thereof) of the mold holding member during the press working. (The amount of displacement below the vertical axis), and is set in advance.
  • the load calculation device sets the value of the set load so that the displacement amount at the center of the die holding member of the machine difference simulation press 10 matches the displacement amount at the center of the die holding member of the simulation target press. It may be calculated.
  • a load calculating apparatus it is good for a load calculating apparatus to have a memory
  • the load calculation device may perform the calculation in step S2 based on the strain data obtained in step S1.
  • the load calculation device calculates the set load value from the strain data obtained in step S1.
  • the load calculation device calculates the set load value as a converted value F based on the deflection characteristic represented by the following equation (3).
  • Wt W 0 + w1 ⁇ F (3)
  • Wt is a target deflection amount of the die holding member at the time of press working in the machine difference simulation press 10, and is a value obtained by the calculation in the above step S2.
  • the target deflection amount Wt is a displacement amount at the center of the mold holding member in the simulation target press.
  • W 0 is an unadjusted deflection amount of the die support member when the deflection adjusting cylinder device 9 does not apply a load to the die support member during press working in the machine difference simulation press 10.
  • w1 is a unit load deflection amount of the die support member when the deflection adjusting cylinder device 9 applies a predetermined unit load to the die support member during press working in the machine difference simulation press 10.
  • the unit load deflection amount w1 is a displacement amount at the center of the mold holding member.
  • the unit load deflection w1 is set in advance.
  • the strain data and deflection distribution of the mold holding member in the simulation target press and the set load value are preferably stored in a database for each simulation target press.
  • the load calculation device has an operation unit, and the operator can select which simulation target press to control the deflection adjusting cylinder device 9 based on the set load value by operating the operation unit. It is good to be.
  • the set load value calculated by the load calculation device may be input to the deflection adjusting device 11.
  • the deflection adjusting device 11 adjusts the deflection adjusting cylinder device 9 based on the input set load value so that the load applied to the mold holding member by the deflection adjusting cylinder device 9 becomes the set load value. Control.
  • deflection adjusting device 11 of the present invention [Configuration of deflection adjusting device]
  • the bolster 25 is targeted, but the same applies to the slide plate 3b.
  • the configuration of the deflection adjusting device 11 for the upper stiffness adjusting cylinder 9b is the same as the configuration of the deflection adjusting device 11 for the lower stiffness adjusting cylinder 9a.
  • 5A to 5D are diagrams showing a first embodiment of the deflection adjusting device 11 of the present invention.
  • 25 is a bolster
  • A is a hydraulic cylinder
  • B is a servo controller
  • C is a hydraulic control circuit
  • dx is a displacement amount
  • P is a load.
  • the support rigidity of the hydraulic cylinder A (that is, the displacement amount at the center of the bolster during press working) is adjusted by servo control of the hydraulic cylinder A that supports the bolster 25.
  • FIGS. 6A and 6B are diagrams showing a second embodiment of the deflection adjusting device 11 of the present invention.
  • B1 is a support stiffness calculation
  • B2 is a cylinder thrust servo control
  • dw is a deflection amount
  • F1 is a cylinder thrust control target value
  • F2 is a cylinder thrust control command value.
  • the thrust of the hydraulic cylinder is controlled according to the deflection amount dw. That is, thrust control of the hydraulic cylinder A that supports the bolster 25 is performed by a pressure control valve or feedback control.
  • the control target value F1 of hydraulic cylinder thrust control is set based on the detected value of the deflection amount dw of the bolster 25 from the support rigidity characteristic D1 to be set.
  • FIGS. 7A and 7B are diagrams showing a third embodiment of the deflection adjusting device 11 of the present invention.
  • B3 is a support rigidity displacement conversion
  • B4 is a cylinder position servo control
  • P is a generated load
  • L1 is a cylinder position control target value
  • L2 is a cylinder position control command value.
  • the displacement amount dL of the hydraulic cylinder is controlled according to the generated load P. That is, the hydraulic cylinder A that supports the bolster 25 performs position control.
  • the control command value L2 for the hydraulic cylinder position control is set based on the detected value of the load value P applied to the hydraulic cylinder from the support rigidity characteristic D2 to be set.
  • S1 and S2 are stroke positions.
  • the stroke positions S1 and S2 for supporting the bolster 25 are changed to adjust the support rigidity by the hydraulic cylinder.
  • the reaction force generated by the hydraulic cylinder with respect to the deflection of the bolster 25 is determined by the compression amount of the hydraulic oil sealed in the cylinder.
  • the amount of change in pressure is expressed by equation (4).
  • ⁇ P K ⁇ ⁇ V / V (4)
  • K is the hydraulic fluid bulk modulus
  • ⁇ V is the hydraulic fluid volume change amount
  • V is the hydraulic fluid initial volume.
  • FIGS. 9A and 9B are diagrams of a fifth embodiment of the deflection adjusting device 11 of the present invention.
  • E is a linear motion mechanism
  • G1 and G2 are mounts.
  • a casing of the hydraulic cylinder is provided by some linear motion mechanism E (feed screw mechanism, cylinder, jack, etc.) having sufficiently higher rigidity than the hydraulic cylinder A. It is possible by raising and lowering.
  • the base for installing the casing of the hydraulic cylinder A is prepared by using bases G1 and G2 having several different heights so that the base is at a support position where the target support rigidity is obtained. May be replaced. In this case, it is possible to adjust to an arbitrary support rigidity by using an accumulator or a pre-pressure method introduced later.
  • FIGS. 10A to 10D are diagrams showing a sixth embodiment of the deflection adjusting device 11 of the present invention.
  • AC is an accumulator.
  • the support rigidity is adjusted by changing the accumulator volume. That is, the support rigidity by the hydraulic cylinder A is generated using the compressibility of the accumulator gas. Since the cylinder reaction force generated with respect to the cylinder stroke compression amount is determined by the compression amount of the gas in the accumulator AC, the hydraulic cylinder support rigidity can be adjusted by changing the gas volume in the accumulator AC. Become.
  • FIG. 11 and FIG. 12 show changes in the cylinder support rigidity depending on the setting of the initial charging pressure P0 of the accumulator gas.
  • S1 is a rod side pressure receiving area
  • S2 is a piston side pressure receiving area
  • Ps is a constant pressure supply pressure
  • Pb is a constant pressure supply balance pressure.
  • the gas volume in the accumulator AC can be changed by setting the pressures Ps and Pb (constant pressure supply values) supplied to the cylinder. Can be adjusted.
  • the cylinder support rigidity can also be adjusted by preparing a plurality of accumulators and selecting / switching the accumulator AC to be used. Furthermore, if each method is used in combination, the adjustment range can be expanded.
  • FIGS. 13A and 13B are diagrams showing a seventh embodiment of the deflection adjusting device 11 of the present invention.
  • the support rigidity is adjusted by changing the preload amount of the hydraulic cylinder A. Since the bulk elastic coefficient of the hydraulic fluid changes depending on the operating pressure, the support rigidity by the hydraulic cylinder A can be adjusted by changing the operating pressure region.
  • FIG. 14 to FIG. 16 are examples of the support rigidity adjustment by changing the hydraulic cylinder preload amount.
  • FIG. 15 if a working fluid whose volume modulus of elasticity changes within a range of about 1.7 to 2.2 GPa in a pressure range of 0 to 40 MPa.abs is used, the hydraulic cylinder A of FIG.
  • the support rigidity of the hydraulic cylinder can be adjusted by setting the initial pressure and changing the bulk modulus.
  • FIG. 16 shows a relationship diagram between the hydraulic cylinder output and the stroke according to the change of the initial pressure Ps.
  • the target deflection distribution of the bolster 25 in the simulation target press can be accurately simulated.
  • the analysis confirms that the target deflection distribution can be accurately simulated not only when the center of gravity of the press load acting on the bolster 25 is at the center position of the bolster 25 but also when the center of gravity deviates from the center position of the bolster 25. did. 17 and 18 show the analysis results.
  • FIG. 17 shows a case where the center of gravity is the center position of the bolster 25, and
  • FIG. 18 shows a case where the center of gravity is shifted from the center position of the bolster 25.
  • the horizontal axis indicates the position of the bolster 25 in the left-right direction in FIG.
  • the vertical axis indicates the amount of bolster deflection at the time of pressing at the center of the bolster in the direction perpendicular to the paper surface in FIG. (Displacement in the vertical direction).
  • the broken line indicates the target deflection distribution
  • the solid line indicates the deflection distribution when the set load is applied to the central portion of the bolster by the deflection adjusting cylinder device 9a.
  • the above-described deflection adjustment can reduce or eliminate the machine difference related to the deflection between the bolster 25 and the slide plate 3b.
  • FIG. 19 is a flowchart showing a method of adjusting the tilt of the slide 3.
  • the inclination of the slide 3 substantially means the inclination of the lower surface of the slide 3 (the lower surface of the slide plate 3b in the example of FIG. 1).
  • step S11 the inclination of the slide 3 of the simulation target press is acquired as the “target inclination”.
  • the target inclination can be acquired by measuring the inclination of the slide 3 of the simulation target press.
  • the inclination of the slide 3 is preferably set at the time of press processing in which the upper mold is in contact with the workpiece (for example, when the slide 3 is located at the bottom dead center).
  • step S12 the stroke position of the tilt adjusting cylinder device 13 is adjusted so as to reduce or eliminate the difference between the tilt of the slide 3 and the target tilt in the machine difference simulation press 10 during press working.
  • the adjustment in step S12 can be effectively performed.
  • the stroke position of the tilt adjustment cylinder device 13 is adjusted by the tilt adjustment device 15 in the direction of decreasing the rigidity of the tilt adjustment cylinder device 13 (for example, in the direction of increasing the elastic modulus of the tilt adjustment cylinder device 13).
  • the difference in the inclination of the slide 3 during the press working is reduced or eliminated between the simulation target press and the machine difference simulation press 10.
  • step S12 The configuration of the tilt adjusting device 15 for carrying out step S12 will be described.
  • the tilt adjusting device 15 may control the stroke position by controlling the pressure in the cylinder chamber of the tilt adjusting cylinder device 13, or may directly control the stroke position.
  • the inclination adjusting device 15 may be configured as shown in FIGS. 20 and 21, for example.
  • FIG. 20 is a configuration diagram of the tilt adjusting device 15 when the tilt of the slide 3 is adjusted by positively controlling the pressure of the tilt adjusting cylinder device 13 (that is, the pressure in the cylinder chamber).
  • the inclination adjusting device 15 includes a pressure command device 15a, a control device 15b, and a hydraulic pressure control circuit 15c.
  • the pressure command device 15a has a data input unit (for example, an interface, a panel, a keyboard, etc.) to which the above target inclination data is input, and based on the input target inclination and inclination characteristics described later,
  • the pressure command value for the tilt adjusting cylinder device 13 is output.
  • the slope characteristics are obtained as follows.
  • each inclination adjustment cylinder device 13 For each of the plurality of pressure values of each inclination adjustment cylinder device 13, the inclination of the slide 3 at each of a plurality of combinations of the pressure values of the other three inclination adjustment cylinder devices 13 is obtained by theoretical calculation, FEM or experiment. This relationship is stored in the pressure command device 15a as an inclination characteristic. Based on each pressure command value and each pressure detection value P1 from a pressure sensor that detects the pressure of each tilt adjustment cylinder device 13, the control device 15b makes the pressure of each tilt adjustment cylinder device 13 become a pressure command value. The hydraulic control circuit 15c is controlled. The hydraulic pressure control circuit 15 c controls the hydraulic pressure supplied to each tilt adjustment cylinder device 13 under the control of the control device 15 b. Note that such control and acquisition of tilt characteristics may be performed for the press working.
  • FIG. 21 is a configuration diagram of the tilt adjusting device 16 when the tilt of the slide 3 is adjusted by positively adjusting the stroke position of the tilt adjusting cylinder device 13.
  • the tilt adjusting device 16 is provided in place of the tilt adjusting device 15.
  • the tilt adjusting device 16 includes a position command device 16a, a control device 16b, and a hydraulic pressure control circuit 16c.
  • the position command device 16a has a data input unit (for example, an interface, a panel, a keyboard, etc.) to which the above target inclination data is input, and based on the input target inclination and inclination characteristics described later, A stroke position command value for the tilt adjusting cylinder device 13 is output.
  • the slope characteristics are obtained as follows.
  • the inclination of the slide 3 at each of a plurality of combinations of stroke positions of the other three tilt adjustment cylinder devices 13 is obtained by theoretical calculation, FEM or experiment. This relationship is stored in the position command device 16a as an inclination characteristic.
  • the control device 16b Based on each stroke position command value and each stroke position detection value ST1 from a stroke position sensor that detects the stroke position of each inclination adjustment cylinder device 13, the control device 16b determines the stroke position of each inclination adjustment cylinder device 13 as follows.
  • the hydraulic control circuit 16c is controlled so that the stroke position command value is obtained.
  • the hydraulic pressure control circuit 16c controls the hydraulic pressure supplied to each tilt adjustment cylinder device 13 under the control of the control device 16b. Note that such control and acquisition of tilt characteristics may be performed for the press working.
  • the slide tilt can be adjusted by adjusting the stroke position of the tilt adjusting cylinder device 13. Accordingly, it is possible to reduce or eliminate the machine difference related to the inclination of the slide 3 during press working.
  • the extension amount of the connecting member 33 at the time of press working can be adjusted. Therefore, by adjusting the extension amount of the connecting member 33, the slide 3 at the time of press working can be adjusted. The amount of deformation can be adjusted effectively.
  • the tilt of the slide 3 can be adjusted more finely by adjusting these tilt adjusting cylinder devices 13 separately. The difference can be further reduced or eliminated.
  • the stroke position of the inclination adjustment cylinder device 13 is reduced in the direction of decreasing the rigidity of the inclination adjustment cylinder device 13. The tilt of the slide 3 can be adjusted effectively.
  • the adjustment method in FIG. 19 and the adjustment method in FIG. 3 or 4 can be performed together.
  • the tilt adjustment cylinder device 13 is adjusted without adjusting the deflection adjustment cylinder device 9 to adjust the tilt of the slide 3, and then the deflection adjustment is performed without adjusting the tilt adjustment cylinder device 13.
  • the deflection of the slide plate 3b can be adjusted.
  • the adjustment method of FIG. 19 and the adjustment method of FIG. 3 or FIG. 4 may be alternately repeated until the machine difference regarding the inclination of the slide 3 and the deflection of the mold holding member is sufficiently reduced or eliminated.
  • the cushion control device 19 includes a movable part position detection device 19a, a thrust command device 19b, a thrust detection device 19c, and a thrust control device 19d.
  • the movable part position detection device 19a detects the position of the movable part 17a (in the example of FIG. 1, the stroke position of the hydraulic cylinder), and may be, for example, a linear scale.
  • the thrust command device 19b includes the storage unit, and outputs a command thrust value based on the thrust pattern stored in the storage unit and the detected position of the movable portion 17a from the movable portion position detection device 19a.
  • the thrust detection device 19c detects the upward thrust of the movable part 17a.
  • the thrust control device 19d controls the movable portion 17a based on the command thrust value (upward thrust command value) from the thrust command device 19b and the upward thrust value detected by the thrust detection device 19c.
  • storage part has memorize
  • the cushion control apparatus 19 has an operation part, and an operator operates any operation part and implements any of several movable part operation
  • the thrust detection device 19c detects the pressure in the upper cylinder chamber and outputs this pressure detection value, and the second pressure that detects the pressure in the lower cylinder chamber and outputs this pressure detection value.
  • a thrust calculation unit 19c- that calculates the upward thrust of the movable portion 17a based on the pressure detection value from the sensor 19c-2, the first pressure sensor 19c-1, and the pressure detection value from the second pressure sensor 19c-2.
  • the thrust control device 19d includes a control signal output device 19d-1 and a hydraulic circuit 19d-2.
  • the control signal output device 19d-1 outputs a thrust control signal based on the command thrust value from the thrust command device 19b and the upward thrust value detected by the thrust detection device 19c.
  • the hydraulic circuit 19d-2 controls the hydraulic pressure in the cylinder chamber (in the example of FIG. 22, the upper cylinder chamber and the lower cylinder chamber) by this thrust control signal.
  • the hydraulic circuit 19d-2 has a hydraulic pressure source 37 and a switching valve (servo valve) 38 controlled by the thrust control signal. Under the control of the switching valve 38, pressure oil from the hydraulic power source 37 is supplied to the upper cylinder. The pressure oil in the lower cylinder chamber or the upper cylinder chamber is discharged to the oil tank.
  • the cushion control device 19 has a slide position detection device 19e.
  • the slide position detection device 19e detects the lift position of the slide 3.
  • the slide position detection device 19e detects a rotation angle sensor (for example, a rotary encoder) that detects a rotation position such as a rotation angle of the servo motor that drives the slide 3 or a rotation angle of the drive gear 5a, and the rotation angle sensor detects the rotation position.
  • a calculation unit that calculates the lift position of the slide 3 based on the rotated position.
  • the slide position detection device 19e may be a position sensor (for example, a linear scale) that directly detects the lift position of the slide 3.
  • an upper limit stopper member 22 is provided in the machine difference simulation press 10.
  • the upper limit stopper member 22 locks the movable portion 17a that has been raised to the upper limit position so that the movable portion 17a does not rise above the predetermined upper limit position.
  • the upper limit stopper member 22 is fixed to the frame (for example, the bed 31) of the machine difference simulation press 10.
  • control signal output device 19d-1 of the cushion control device 19 is a position immediately before the occurrence of the cushioning force immediately before the slide 3 starts to apply a downward load to the movable portion 17a based on the detection position of the slide 3 by the slide position detection device 19e.
  • the die cushion device 17 is controlled to reduce the upward thrust of the movable portion 17a that is locked to the upper limit stopper member 22.
  • the control signal output device 19d-1 determines that the slide 3 is lowered to the cushion force generation start position that applies a downward load to the movable portion 17a based on the detection position of the slide 3 by the slide position detection device 19e. Then, control according to the moving part operation pattern is started.
  • FIG. 23 shows a die cushion device of a simulation target press.
  • 17b is a cushion pad
  • AS is an air cylinder
  • AT is an air tank
  • 22 is an upper limit stopper.
  • the simulation target cushion characteristic of the simulation target press is assumed to be a cushion characteristic obtained by the air cylinder AS and the tank AT in which a constant air pressure is enclosed, and the cushion force is determined by the enclosed air pressure.
  • FIG. 24 shows simulation target cushion characteristics in such a case.
  • the upper limit stopper member 22 receives the upward thrust of the air cylinder AS in the standby state before press working. From this state, the slide 3 descends, and the cushion force is generated when the slide 3 starts to apply a downward load to the air cylinder AS. This cushioning force increases as the slide 3 descends as the enclosed air pressure in the cylinder chamber of the air cylinder AS is compressed as the slide 3 descends.
  • FIG. 25 is a flowchart showing a cushion simulation operation according to the first configuration example.
  • step S21 the piston 17a to which the upward thrust is applied is locked to the upper limit stopper member 22 before the slide 3 and the upper mold begin to apply a downward load to the die cushion device 17 via the workpiece. Wait in state. That is, in the standby state before press working, the cushion control device 19 controls the die cushion device 17 so as to apply an upward thrust of a predetermined magnitude to the movable portion 17a.
  • step S22 it is determined whether or not the slide 3 has come down, and the slide 3 and the upper mold have reached the position immediately before the cushion force generation just before starting to apply a downward load to the die cushion device 17 via the workpiece.
  • the control signal output device 19d-1 determines.
  • the control signal output device 19d-1 makes this determination based on the detected position of the slide 3 from the slide position detecting device 19e. If the control signal output device 19d-1 determines that the slide 3 has not reached the position immediately before the occurrence of the cushioning force, the determination in step S22 is repeated momentarily.
  • the control signal output device 19d-1 determines that the slide 3 has reached the position immediately before the cushion force is generated, the process proceeds to step S23.
  • step S23 the control signal output device 19d-1 performs control to reduce the upward thrust applied to the movable portion 17a when it is determined that the slide 3 has reached the position immediately before the cushion force is generated.
  • the control signal output device 19d-1 performs control to release the pressure oil in the cylinder chamber of the hydraulic cylinder (the lower cylinder chamber in the example of FIG. 22), thereby reducing the upward thrust applied to the piston 17a.
  • step S24 it is determined whether the slide 3 and the upper mold have reached the cushion force generation start position at which the downward load is applied to the die cushion device 17 or not.
  • the control signal output device 19d-1 makes this determination based on the detected position of the slide 3 from the slide position detecting device 19e.
  • the determination in step S24 is repeated momentarily.
  • the control signal output device 19d-1 determines that the slide 3 has reached the cushion force generation start position, the process proceeds to step S25.
  • the control signal output device 19d-1 may perform control on the die cushion device 17 so as to continuously reduce the upward thrust of the piston 17a.
  • step S25 when it is determined that the slide 3 has reached the cushion force generation start position, the cushion control device 19 starts control according to the movable part operation pattern. Specifically, when the control signal output device 19d-1 of the cushion control device 19 determines that the slide 3 has reached the cushion force generation start position based on the slide position detection value from the slide position detection device 19e. Thus, the control signal for comparing the command thrust value from the thrust command device 19b with the upward thrust detection value of the movable portion 17a from the thrust detection device 19c and causing the upward thrust of the movable portion 17a to follow the command thrust value. Output every moment. The thrust command device 19b outputs a command thrust value from moment to moment based on the thrust pattern and the detection position of the movable portion 17a from the movable portion position detection device 19a, regardless of the slide position detection value.
  • FIG. 26 shows the displacement of the movable portion 17a (stroke displacement of the hydraulic cylinder), the upward thrust of the movable portion 17a, and the upward load applied to the slide 3 by the movable portion 17a in the case of following the flowchart of FIG. That is, it is a graph showing the cushioning force) with respect to time.
  • the solid line indicates the result of the cushion simulation operation of the cushion control device 19 according to the first configuration example, and the broken line indicates the simulation target. Further, in FIG.
  • the slide 3 or the upper mold is applied to the die cushion device 17 because the upward thrust of the movable portion 17a is reduced at the position immediately before the occurrence of the cushioning force immediately before the slide 3 starts to apply the downward load to the piston 17a. It can be avoided that the cushion force becomes excessive immediately after the downward load is applied.
  • the cushion control device 19 applies an upward thrust of the same magnitude as the initial upward thrust of the movable portion 17a defined in the movable portion operation pattern. Since it is applied to the movable portion 17a, the difference between the initial upward thrust determined in the movable portion actuation pattern and the actual upward thrust of the movable portion 17a can be reduced or eliminated at the start of the movable portion actuation pattern.
  • the cushion control device 21 according to the second configuration example is provided instead of the cushion control device 19 according to the first configuration example.
  • the upper limit stopper member 22 is omitted.
  • FIG. 27 shows a configuration of the cushion control device 21 according to the second configuration example.
  • the cushion control device 21 includes a movable part position detection device 21a, a thrust command device 21b, a thrust detection device 21c, and a thrust control device 21d.
  • the movable part position detection device 21a, the thrust command device 21b, and the thrust detection device 21c in the second configuration example have the same configurations as the movable part position detection device 19a, the thrust command device 19b, and the thrust detection device 19c in the first configuration example, respectively. It may be.
  • the control signal output device 21d-1 of the thrust control device 21d holds the stroke position of the piston 17a constant before the slide 3 applies a downward load to the movable portion 17a.
  • FIG. 28 is a flowchart showing a cushion simulation operation by the cushion control device 21 of the second configuration example. Also in this case, the cushion characteristic of FIG. 24 is the cushion characteristic to be simulated.
  • step S31 the thrust control device 21d stands by holding the piston 17a at a predetermined stroke position based on the detection position of the piston 17a from the movable portion position detection device 21a.
  • the pressure in the upper cylinder chamber and the lower cylinder chamber of the hydraulic cylinder may be set to constant values by the thrust control device 21d.
  • the switching valve 38 is set to the state shown in FIG. Thereafter, the slide 3 descends and comes into contact with the die cushion device 17 to push down the movable portion 17a.
  • step S32 it is determined whether or not the upward thrust of the movable portion 17a has reached a predetermined value due to the pressure oil in the cylinder chamber of the hydraulic cylinder being compressed by the pressing of the movable portion 17a by the slide 3.
  • step S33 the switching valve 38 may be in the state shown in FIG.
  • step S33 since the control signal output device 21d-1 determines that the upward thrust has reached the predetermined value, the control thrust value from the thrust command device 21b and the upward movement of the movable portion 17a from the thrust detection device 21c are detected. The thrust detection value is compared, and a control signal for causing the upward thrust of the movable portion 17a to follow the command thrust value is output momentarily.
  • the thrust command device 21b does not depend on the command thrust value from the thrust detection device 21c, but changes the command thrust value from time to time based on the thrust pattern and the detection position of the movable portion 17a from the movable portion position detection device 21a. Is output.
  • FIG. 29 shows the displacement of the movable portion 17a (the displacement of the stroke of the hydraulic cylinder), the upward thrust of the movable portion 17a, and the upward load applied to the slide 3 by the movable portion 17a in the case of following the flowchart of FIG. That is, it is a graph showing the cushioning force) with respect to time.
  • the solid line indicates the result of the cushion simulation operation by the cushion control device 21 of the second configuration example, and the broken line indicates the simulation target.
  • the slide 3 is lowered from the state in which the movable portion 17a is kept at a predetermined position by the thrust control device 21d, so that a downward load is applied from the slide 3 to the movable portion 17a.
  • the upward thrust reaches a predetermined value, control by the thrust pattern is started. Therefore, the target cushion characteristic can be simulated only by the hydraulic servo control function of the cushion control device 21 without using the upper limit stopper member 22.
  • FIG. 30 is an overall flowchart showing the pressure distribution adjusting method of the machine difference simulation press 10 of the present invention.
  • the method of the present invention comprises steps S41 to S46.
  • step S41 strain data is acquired from strain measurement of the simulation target press.
  • the simulation target press is, for example, a press for mass production of a mold user.
  • the strain at the time of press working of the mold holding member is measured.
  • step S42 the contact pressure distribution of the simulation target press is estimated and calculated from the obtained strain data. This calculation is based on FEM calculation or theoretical calculation.
  • the obtained contact pressure distribution is defined as “target contact pressure distribution”.
  • FIG. 31 is a schematic diagram of steps S43 and S44.
  • step S43 a shim adjustment position is set.
  • the shim adjustment position is between the bolster 25 and the slide 3 and the support surface of the mold (not shown), does not interfere with the cushion pin 17d, the deflection adjusting cylinder device 9 and the like, and is not in contact with the bolster 25 and the slide plate 3b.
  • the positions are set as shown in FIG. 31A so that both surfaces coincide with both of the support surfaces.
  • step S44 the rate of change of the contact pressure distribution due to the unit thickness shim at each shim adjustment position is calculated. That is, a shim of unit thickness is given as a forced displacement to each shim adjustment position on the FEM model as shown in FIG. 31B, and the change rate of the contact pressure of the mold is calculated as shown in FIG. 31C.
  • dP k (x, y) be the rate of change of the contact pressure distribution due to shims of unit thickness at each shim adjustment position.
  • a necessary shim 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 shim adjustment is expressed by an appropriate evaluation function, and the shim adjustment amount that minimizes the difference is obtained.
  • an evaluation function may be P in the following equation (5), for example.
  • P T (x, y) is the target contact pressure distribution of the simulation target press
  • P 0 (x, y) is the contact pressure distribution before adjustment of the machine difference simulation press 10
  • a (K) is a necessary shim adjustment amount at each shim adjustment position
  • a necessary shim adjustment amount a (k) that minimizes P is obtained by the least square method.
  • step S43 first, P 0 (x, y) is obtained from the contact pressure distribution when the shim adjustment is not performed using the FEM calculation model. Next, N shim adjustment positions (15 positions in FIG. 31A) are set.
  • step S44 on the FEM calculation model, the unit shim adjustment amount is given to each of the N points as a forced displacement, and the change rate of the contact pressure distribution at that time is stored as dP k (x, y).
  • the necessary shim adjustment amount at each point is a (k), and the target P T (x, y) and the calculated P 0 (x, y) and dP k (x, y) are used.
  • step S46 it is confirmed by the analysis using the necessary shim adjustment amount a (k) that the contact pressure distribution is as intended. If there is no problem in step S46, the pressure distribution adjustment according to the present invention is terminated. If there is a problem, steps S43 to S45 are repeated.
  • the shim adjustment position is set in step S43, the rate of change of the contact pressure distribution due to the unit thickness shim at each shim adjustment position is calculated in step S44, and the target contact pressure distribution is determined in step S45. Since the required shim adjustment amount obtained is calculated, the surface pressure distribution adjusting plates 23A and 23B having the shim adjustment thickness of the required shim adjustment amount at each shim adjustment position can be prepared. Further, by holding the surface pressure distribution adjusting plates 23A and 23B between the bolster 25 and / or the slide plate 3b and the support surface of the mold, the difference in contact pressure distribution between the molds is reduced or eliminated. Can do.
  • machine difference simulation press 10 As described above, in the machine difference simulation press 10 according to the embodiment of the present invention, (1) machine difference relating to the deflection distribution of the mold holding member, (2) machine difference relating to the inclination of the slide 3, and (3) characteristics of the die cushion. And (4) all the machine differences related to the contact pressure distribution between the mold holding member 3b and the mold can be reduced or eliminated. Thereby, the difference of the press surface by an upper metal mold
  • the single deflection adjusting cylinder device 9a for applying a load to the bolster 25 is provided, a plurality of deflection adjusting cylinder devices for applying an upward load to the bolster 2 may be provided.
  • the single deflection adjusting cylinder device 9b that applies a load to the slide plate 3b is provided, a plurality of deflection adjusting cylinder devices that apply a downward load to the slide plate 3b may be provided.
  • the deflection distribution of the bolster 25 or the slide play and 3b may be matched or approximated to the target deflection distribution.
  • the load applying means is the deflection adjusting cylinder device 9, but instead of the deflection adjusting cylinder device 9, a spring having rigidity that applies the set load to the bolster 25 or the slide play and 3 b, respectively. It may be.
  • the load applying means is the deflection adjusting cylinder device 9 using hydraulic pressure, but the load applying means may be configured using a piezoelectric element, a giant magnetostrictive element, or the like instead of the deflection adjusting cylinder device 9. Good.
  • the slide inclination of the simulation target press at the time of pressing is measured, and the measured slide inclination is set as the target inclination, but the upper mold and the workpiece are not in contact with each other during non-pressing processing.
  • the slide inclination of the simulation target press may be measured, and the measured slide inclination may be set as the target inclination.
  • the adjustment of the slide inclination of the machine difference simulation press 10 is also targeted at the time of non-pressing.
  • it is preferable to adjust the tilt by supplying liquid to both the upper cylinder chamber and the lower cylinder chamber of the tilt adjusting cylinder device 13.
  • the configuration of the tilt adjusting cylinder device 13 and the tilt adjusting device 15 and other points of the slide tilt adjusting method when the slide tilt at the time of non-pressing is an adjustment target may be the same as those in the above embodiment.
  • slide drive mechanism 5 moves the slide 3 up and down using the drive gear 5a and the link 5b
  • the slide drive mechanism may be configured by other means for moving the slide 3 up and down.
  • tilt adjusting cylinder devices 13 are provided, but other numbers (including one) of tilt adjusting cylinder devices 13 other than four may be provided.
  • the die cushion device 17 is constituted by a hydraulic cylinder device.
  • the die cushion device 17 may be constituted by another hydraulic cylinder or an air cylinder.
  • the cushion control device may control the hydraulic pressure or air pressure.
  • the die cushion device 17 is not limited to the cylinder device, and may be other means whose upward thrust can be controlled.
  • the die cushion device 17 may include a drive motor such as a servo motor and a conversion mechanism (for example, a ball screw and a ball nut) that converts the rotational driving force of the drive motor into upward thrust.
  • a drive motor such as a servo motor and a conversion mechanism (for example, a ball screw and a ball nut) that converts the rotational driving force of the drive motor into upward thrust.
  • the upward thrust in step S23 may be reduced by reducing the supply voltage to the drive motor.
  • the cylinder chambers of the die cushion device 17 are connected to each other (for example, the lower cylinder chambers are connected to each other, and the upper cylinder chambers are connected to each other).
  • a plurality of die cushion devices 17 may be controlled by a single cushion control device.
  • a cushion control device may be provided for each die cushion device 17.
  • the movable portion 17a of the die cushion device 17 is a piston.
  • the cylinder portion that can move up and down with respect to the piston may be the movable portion.
  • the movable part operation pattern is a thrust pattern in which the upward thrust of the movable part 17a is determined with respect to the position of the movable part 17a, but the present invention is not limited to this. That is, the movable part operation pattern may be a thrust pattern determined with respect to the position or time of the slide 3.
  • the cushion control device controls the die cushion device 17 based on the detection position or measurement time of the slide 3 so that the movable portion 17a operates according to the movable portion operation pattern.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Control Of Presses (AREA)

Abstract

L'invention porte sur une presse de simulation d'erreur machine. Une erreur machine se produit entre ladite presse de simulation et une presse destinée à la production de masse ou similaire, utilisée comme presse cible de simulation. La presse de simulation d'erreur machine (10) comporte des organes porte-moule (25a et 3b) servant à monter un moule aux fins de pressage d'une pièce à usiner, et des organes de support (34 et 3a) formant support pour les parties de la circonférence externe desdits organes porte-moule (25a et 3b). L'invention inclut en outre un moyen d'application de charge (9) servant à appliquer une charge lors du pressage sur les parties desdits organes porte-moule (25 et 3b) qui ne sont pas supportées par les organes de support (34 et 3a), pour ainsi ajuster les déflexions desdits organes porte-moule (25 et 3b).
PCT/JP2009/050806 2008-01-29 2009-01-21 Presse de simulation d'erreur machine WO2009096272A1 (fr)

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JP2008017263A JP2009178718A (ja) 2008-01-29 2008-01-29 機差模擬プレス
JP2008-017263 2008-01-29

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WO2009096272A1 true WO2009096272A1 (fr) 2009-08-06

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US8916526B2 (en) 2009-07-31 2014-12-23 National University Corporation Okayama University Flavanone derivative
FR3060446B1 (fr) * 2016-12-20 2019-05-31 Porcher Industries Presse chauffante, ensemble de pressage, procede de reglage et utilisations d'une telle presse chauffante.
JP7068394B2 (ja) * 2020-07-30 2022-05-16 株式会社エイチアンドエフ プレス機械及びそれを用いたワークのプレス方法
DE102021001805A1 (de) * 2021-04-08 2022-10-13 Weinig Dimter Gmbh & Co. Kg Pressvorrichtung zum Pressen von Werkstücken aus Holz, Kunststoff, Metall und dergleichen
JP7306558B1 (ja) 2022-01-11 2023-07-11 Ｊｆｅスチール株式会社 プレス成形品の外周形状評価方法、装置及びプログラム、並びにプレス成形品の製造方法

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Publication number Priority date Publication date Assignee Title
JPS6161918B2 (fr) * 1984-02-06 1986-12-27 Kootaki Kk
JPH0281799U (fr) * 1988-12-02 1990-06-25
JP2000312998A (ja) * 1999-03-19 2000-11-14 Minster Mach Co:The プレスたわみ制御装置

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Publication number Priority date Publication date Assignee Title
JP2005118854A (ja) * 2003-10-20 2005-05-12 Komatsu Ltd プレス機械の金型取付け位置補正装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6161918B2 (fr) * 1984-02-06 1986-12-27 Kootaki Kk
JPH0281799U (fr) * 1988-12-02 1990-06-25
JP2000312998A (ja) * 1999-03-19 2000-11-14 Minster Mach Co:The プレスたわみ制御装置

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