JP2009178726A - Press and its adjusting method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a press capable of reducing or eliminating a machine error relative to the posture of a slide at the time of pressing, and a method for adjusting the press. <P>SOLUTION: A press includes: an upper die and a lower die, which perform pressing while vertically clamping a workpiece; a slide 3, to whose lower surface the upper die is fixed and which is vertically moved; a slide driving mechanism 5, which generates press-molding force by vertically moving the slide 3; and a slide adjusting device 13 for adjusting the posture of the slide 3. The slide adjusting device 13 has a cylinder device 13A, which applies a load to the slide 3 to change the posture of the slide 3 by changing its stroke position, and an adjusting means 13B for adjusting the stroke position of the cylinder device 13A. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a press machine. In particular, the present invention relates to a press machine that can be used to simulate a press to be simulated, and a method for adjusting the press machine.

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 consists of a process performed by a mold manufacturer using a prototype press (mold matching at the manufacturer) and a process 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.

Note that Patent Documents 1 to 7 have already been disclosed as prior arts related to the present invention.
Of these, Patent Document 1 is capable of switching the frame vertical rigidity so that it can be adjusted to the frame rigidity suitable for the object to be processed, and Patent Documents 2 to 4 suppress the deformation of the frame by structural reinforcement or the like. Patent Documents 5 to 6 adjust the pressure oil acting on the hydraulic actuator to obtain a predetermined rigidity by switching / controlling the hydraulic circuit. . In Patent Document 7, a plurality of members that are elastically deformed are provided between a bed and a mold support plate to adjust the mold shape.

Japanese Patent Application Laid-Open No. 04-147800, “Press Machine” Japanese Patent Application Laid-Open No. 08-174295, “Press Machine” JP 2004-58123 A, “Reinforcement structure of press machine” Japanese Patent No. 2548508, “Hydraulic Press” Japanese Patent Laid-Open No. 61-24609, “Hydraulic Stabilizer Device” Japanese Patent Publication No. 07-17139, “Stabilizer Spring Constant Variable Device” Japanese Patent Application Laid-Open No. 2005-169408 “Die table for press working and press machine”

  In the mold matching process described above, mold matching by the user is usually 100 to 200 hours, and has reached 1/3 or more 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.

Even though mold matching has been completed in advance in the mold maker, it takes a long time for mold matching by the user. This is because there is a difference between the press for mass production (machine difference between presses).
One of the machine differences between the presses is the inclination and deflection of the slide during press working. In the following, the tilt and deflection of the slide are collectively referred to as the slide posture. That is, the attitude of the slide means one or both of the tilt and deflection of the slide during press working.

  The present invention has been developed to solve the above-described problems. That is, an object of the present invention is to provide a press machine that can adjust the slide attitude, and thereby reduce or eliminate the machine difference related to the slide attitude, and an adjustment method thereof.

In order to achieve the above object, according to the present invention, an upper mold and a lower mold for pressing a workpiece in a vertical direction, a slide on which an upper mold is fixed to a lower surface and moved up and down, and the slide A slide drive mechanism that raises and lowers the pressure and generates a press molding force, and a slide adjustment device for adjusting the attitude of the slide,
The slide adjusting device includes:
A cylinder device that applies a load to the slide so that the posture of the slide is changed by a change in the stroke position;
There is provided a press machine comprising adjusting means for adjusting a stroke position of the cylinder device.

In this configuration, the adjusting means can adjust the slide posture by adjusting the stroke position of the cylinder device. Therefore, it is possible to reduce or eliminate the machine difference regarding the posture of the slide during press working.
The adjusting means may indirectly adjust the stroke position by controlling the pressure of the cylinder device, or may directly control the stroke position of the cylinder device.

  According to a preferred embodiment of the present invention, the cylinder device connects the slide drive mechanism and the slide, whereby the relative position between the slide drive mechanism and the slide changes due to a stroke position change of the cylinder device.

  Since the relative position between the slide drive mechanism and the slide changes due to the change in the stroke position of the cylinder device, the posture of the slide during press working can be adjusted effectively.

  According to a preferred embodiment of the present invention, when the stroke position of the cylinder device changes, the inclination of the slide with respect to the horizontal direction changes.

  In this configuration, since the slide inclination can be adjusted by adjusting the stroke position of the cylinder device, the slide inclination can be adjusted effectively.

According to a preferred embodiment of the present invention, the cylinder device connects the slide drive mechanism and the slide,
Furthermore, an upper load support member that supports an upward load acting from the slide drive mechanism during press working,
A lower load support member for supporting a downward load acting from the lower mold during press working;
A connecting member that connects the upper load supporting member and the lower load supporting member,
By adjusting the stroke position, the extension amount of the connecting member at the time of press working can be adjusted.

  In this configuration, by adjusting the stroke position of the cylinder device, it is possible to adjust the extension amount of the connecting member at the time of press processing. Therefore, by adjusting the extension amount of the connecting member, the slide at the time of press processing can be adjusted. The amount of deformation can be adjusted effectively.

  According to a preferred embodiment of the present invention, a plurality of the cylinder devices are provided, and each of these cylinder devices applies a load to a plurality of slides.

  In this configuration, each of the plurality of cylinder devices applies a load to a plurality of slides, and by adjusting these cylinder devices separately, the slide posture can be adjusted more finely, thereby further reducing machine differences. Or you can eliminate it.

In order to achieve the above object, according to the present invention, an upper mold and a lower mold for pressing a workpiece in a vertical direction, a slide on which the upper mold is fixed to the lower surface and moved up and down, A slide drive mechanism that raises and lowers the slide to generate a press molding force, and a method for adjusting a simulation press machine comprising:
A cylinder device that applies a load to the slide so as to change the posture of the slide by changing the stroke position is provided in the simulation press machine,
Acquire the posture data of the slide of the simulation target press as target posture data,
There is provided a method for adjusting a press machine, wherein the stroke position of the cylinder device is adjusted so as to reduce or eliminate the difference between the slide attitude data and the target attitude data in the simulation press machine.

  In this simulation press machine adjustment method, the stroke position of the cylinder device is adjusted so as to reduce or eliminate the difference between the slide posture data and the target posture data in the simulation press machine. Machine differences can be reduced or eliminated.

The simulation press machine and the simulation target press include an upper load support member that supports an upward load that acts from the slide drive mechanism during press processing, and a lower load support that supports a downward load that acts from a lower mold during press processing. A member, and a connecting member that connects the upper load supporting member and the lower load supporting member,
The cylinder device connects the slide drive mechanism and the slide,
The rigidity of the connecting member of the simulation press machine is set higher than the rigidity of the connecting member of the corresponding press to be simulated.

  Thus, since the rigidity of the connecting member of the simulation press machine is higher than the rigidity of the connecting member of the simulation target press, by reducing the stroke position of the cylinder device in the direction of decreasing the rigidity of the cylinder device, The posture can be adjusted effectively.

  According to the above-described present invention, it is possible to reduce or eliminate the machine difference related to the posture of the slide during press working.

  The best mode for carrying out the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the common part in each figure, and the overlapping description is abbreviate | omitted.

  FIG. 1 is a configuration diagram of a press machine according to an embodiment of the present invention. The press machine 10 includes a slide 3, a slide drive mechanism 5, a counter balance cylinder 7, a lower load support member 9 (bed), an upper load support member 11 (crown), a slide adjusting device 13, and a connecting member 15 (upright).

  The slide 3 is moved up and down with an upper mold (not shown) fixed to the lower surface. In the example of FIG. 1, the slide 3 has a slide body 3a and a slide plate 3b fixed to the lower surface of the slide body 3a. The upper die performs press working with a workpiece sandwiched between a lower die (not shown) fixed to the upper surface of a bolster 17 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 11 and driven to rotate by the servo motor, and the drive gear 5a and the slide 3. And 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 lower load support member 9 supports a downward load acting from the lower mold during press working (for example, when the slide 3 is located at the bottom dead center). In the example of FIG. 1, the lower load support member 9 is a bed fixed to an external foundation. The bed 9 supports the carrier 19 on its upper surface. The carrier 19 is movable in a direction perpendicular to the paper surface of FIG. 1 and supports the outer peripheral portion of the bolster 17. A lower mold (not shown) is attached to the upper surface of the bolster 17. The bolster 17 is provided with a through hole through which the cushion pin 21 passes, and the cushion pin 21 and the cushion pad 23 that supports the cushion pin 21 are supported by a cushion cylinder 25 in the bed 9 so as to be vertically movable.

  The upper load support member 11 supports an upward load acting from the slide drive mechanism 5 during press working. In the example of FIG. 1, the upper load support member 11 is a crown.

The slide adjusting device 13 is for adjusting the posture of the slide 3 at the time of press working, and the load is applied to the slide 3 so that the posture of the slide 3 at the time of press working is changed by the change of the stroke position at the time of press working. Act. The slide adjusting device 13 includes a cylinder device 13A and adjusting means 13B.
The cylinder device 13A may be a hydraulic cylinder, and supports the slide 3 by pressing the slide 3 downward during press working. In the example of FIG. 1, the cylinder device 13A includes an overload cylinder 13A1 and a stiffness adjusting cylinder device 13A2. FIG. 2 is a view taken along the line II-II in FIG. 1, but shows only the vicinity of the slide 3.
The overload cylinder 13A1 connects the slide drive mechanism 5 and the slide 3, so that the relative position between the slide drive mechanism 5 and the slide 3 changes due to a change in the stroke position of the overload cylinder 13A1. That is, the slide drive mechanism 5 and the slide 3 are connected via the overload cylinder 13A1. Further, 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 overload cylinder 13A1. In the example of FIGS. 1 and 2, four overload cylinders 13A1 are provided. One end of each overload cylinder 13A1 is fixed in the vicinity of the outer periphery of the slide 3, and the other end is slide driven. It is rotatably connected to the link 5b of the mechanism 5 by a pin. Such an overload cylinder 13A1 is effective for adjusting the inclination of the slide 3 to be described later. The overload cylinder 13A1 opens the relief valve that controls the supply of pressure oil to the hydraulic cylinder chamber when an abnormal load occurs, thereby moving the piston by the cylinder stroke and damaging the upper die. It can also be avoided.
The rigidity adjusting cylinder 13A2 is provided on the slide body 3a. That is, the rigidity adjustment cylinder 13A2 is disposed inside the slide body 3a, and one end of the rigidity adjustment cylinder 13A2 is fixed to the upper portion of the slide body 3a. This upper part is formed integrally with the slide body 3a. An opening is provided in the lower center portion of the slide body 3a, and the other end portion of the rigidity adjusting cylinder 13A2 presses the center portion of the upper surface of the slide plate 3b through the opening. The slide plate 3b is fixed to the lower surface of the slide body 3a. Such a rigidity adjusting cylinder 13A2 is effective for adjusting the deflection of a slide 3 (slide plate 3b in the example of FIG. 1) described later.
The adjusting means 13B adjusts the stroke position of the cylinder device 13A. The adjusting means 13B controls the pressure of the cylinder device 13A to indirectly adjust the stroke position of the cylinder device 13A, or directly controls the stroke position of the cylinder device 13A. The adjusting means 13B can adjust the adjustment of each overload cylinder 13A1 independently of the adjustment of the other cylinder devices 13A1 and 13A2. Further, the adjusting means 13B can adjust the adjustment of the rigidity adjusting cylinder 13A2 independently of the adjustment of the overload cylinder 13A1. In FIG. 1, the adjusting means 13 </ b> B is provided on the upper load support member (crown) 11, but may be provided at another location.

  The connecting member 15 connects the upper load support member 11 and the lower load support member 9. In the example of FIG. 1, the connecting member 15 is a columnar upright, and a plurality of connecting members 15 are provided. The amount of extension of the upright 15 during press working can be adjusted by adjusting the stroke position of the cylinder device 13A.

  Next, the adjustment method of the press machine 10 mentioned above is demonstrated.

[Slide tilt adjustment]
First, the case where the inclination of the slide 3 is adjusted will be described. FIG. 3 is a flowchart showing an adjustment method of the press machine 10 and shows a case where the inclination of the slide 3 is adjusted. 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).

In step S1, the inclination data of the slide 3 of the simulation target press is acquired as target inclination data. The target inclination data may be each load acting on the slide 3 at the time of pressing at a plurality of points on the slide 3. These multiple positions correspond to the positions at which each overload cylinder 13A1 applies a load to the slide 3 in the press machine 10. The press working is when the workpiece is pressed while the upper die is in contact with the workpiece.
In an example, when the overload cylinder 13A1 is provided in the same plural positions as the press machine 10 (for example, the same four positions as in FIG. 2) in the simulation target press, these overload cylinders at the time of press working Measure the pressure. These measured pressure values are used as inclination data.
In another example, strains at a plurality of positions of the slide 3 are measured with a strain gauge, and these measured strain values are converted into load values at a plurality of positions of the slide 3 by FEM or the like. Each load value thus obtained is used as inclination data. Note that the number of positions at which distortion is measured is equal to or greater than the number of load value acquisition positions. Thereby, it can convert into the load value of a several position by FEM from a some distortion measured value.

In step S2, the stroke position of the overload cylinder 13A1 is adjusted so as to reduce or eliminate the difference between the inclination data of the slide 3 and the target inclination data in the simulation press machine 10 during press working. Note that the inclination data of the slide 3 in the press machine 10 is each load value that each overload cylinder 13 </ b> A <b> 1 applies to the slide 3.
Preferably, by adjusting the connecting member 15 of the simulation press machine 10 to be higher than the rigidity of the corresponding connecting member 15 of the simulation target press, the adjustment in step S2 can be performed effectively. In this case, in step S2, the stroke position of the overload cylinder 13A1 is adjusted by the adjusting means 13B in the direction of decreasing the rigidity of the overload cylinder 13A1 (for example, in the direction of increasing the elastic modulus of the overload cylinder 13A1). The difference in the inclination of the slide 3 during press working is reduced or eliminated between the simulation press machine 10 and the machine difference simulation press.

  The configuration of the adjusting unit 13B for performing step S2 will be described.

  For example, the adjusting means 13B may control the pressure when supplying fluid of a constant pressure to the cylinder chamber of the overload cylinder 13A1, or may directly control the stroke position. Further, the adjusting means 13B may be configured as shown in FIG.

FIG. 4 is a configuration diagram of the adjusting means 13B in the case of adjusting the inclination of the slide 3 by positively controlling the pressure of the overload cylinder 13A1 (that is, the pressure in the cylinder chamber). As shown in FIG. 4, the adjusting means 13 </ b> B includes a pressure command device 27, a control device 29, and a hydraulic pressure control circuit 31.
The control device 29 has a data input unit (for example, an interface, a panel, a keyboard, etc.) into which the target inclination data is input. Based on the input target inclination data (load values at a plurality of positions described above) and the pressure detection values (that is, inclination data) from the pressure sensors that detect the pressure of each overload cylinder 13A1, the control device 29 The hydraulic control circuit 31 is controlled so that the pressure (inclination data) of each overload cylinder 13A1 is the same as the target inclination data. That is, control is performed so that each pressure detection value, which is inclination data, becomes each load value of the corresponding target inclination data.
The hydraulic pressure control circuit 31 controls the hydraulic pressure supplied to each overload cylinder 13A1 under the control of the control device 29.
Note that such control and acquisition of tilt characteristics may be performed for the press working.

[Adjust slide deflection]
Next, a case where the deflection of the slide plate 3b is adjusted will be described. FIG. 5 is a flowchart showing an adjustment method of the press machine 10 and shows a case where the deflection of the slide plate 3b is adjusted.

In step S11, 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. In the strain measurement, the strain at the time of pressing the slide plate 3b is measured.
In step S12, 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 “target deflection distribution (ie, target deflection data)”.
In step S13, 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.
In step S14, the load of the rigidity adjustment cylinder 13A2 is set. In this load setting, the center deflection is matched with the target deflection distribution using the adjusting means 13B.
In step S15, the deflection calculation with the set load of the stiffness adjusting cylinder 13A2 is performed by FEM.
In step S16, it is confirmed that the deflection distribution (deflection data) obtained by the deflection calculation is in accordance with the target (matches or substantially matches the target deflection data).
In step S17, the deflection calculation including the mold is performed by FEM.
In step S18, it is confirmed that the influence of the mold is small.
If there is no problem in steps S16 and S18, the stiffness adjustment (ie, deflection adjustment) is terminated. If there is a problem, steps S13 to S17 are repeated.

  Hereinafter, a specific example of the rigidity adjusting cylinder 13A2 of the present invention will be described.

  6A to 6D are diagrams showing a first embodiment of the adjusting means 13B. In this example, the support rigidity by the hydraulic cylinder is adjusted by servo control (position control or thrust control) of the hydraulic cylinder that supports the slide plate 3b.

7A and 7B are diagrams showing a second embodiment of the adjusting means 13B of the present invention. In this example, the thrust of the hydraulic cylinder is controlled according to the amount of deflection.
That is, thrust control of the hydraulic cylinder that supports the slide plate 3b is performed by a pressure control valve or feedback control. The control target value of the hydraulic cylinder thrust control is set based on the detected value of the deflection amount of the slide plate 3b from the set support rigidity characteristic.

8A and 8B are diagrams showing a third embodiment of the adjusting means 13B. In this example, the displacement amount of the hydraulic cylinder is controlled according to the generated load.
That is, the hydraulic cylinder that supports the slide plate 3b performs position control. The control command value for the hydraulic cylinder position control is set based on the detected value of the load applied to the hydraulic cylinder from the support rigidity characteristics to be set.

  9A to 9D are diagrams showing a fourth embodiment of the adjusting means 13B of the present invention. In this example, the support position by the hydraulic cylinder is adjusted by changing the stroke position for supporting the slide plate 3b.

The reaction force generated by the hydraulic cylinder against the bending of the slide plate 3b is determined by the compression amount of the hydraulic oil sealed in the cylinder. The amount of change in pressure is expressed by equation (1).
ΔP = K × ΔV / V (1)
Here, ΔP is the pressure change amount, K is the hydraulic fluid bulk modulus, ΔV is the hydraulic fluid volume change amount, and V is the hydraulic fluid initial volume.

  According to this relational expression (1), even if ΔV is generated due to the same bending of the slide plate, the value of ΔP generated varies depending on the state of V. That is, by changing the cylinder stroke position for supporting the slide plate 3b, it is possible to change the cylinder reaction force generated against the slide plate deflection, and to adjust the support rigidity of the hydraulic cylinder.

10A and 10B are diagrams showing a fifth embodiment of the adjusting means 13B of the present invention.
As shown in FIG. 10A, in order to change the cylinder stroke position, the casing of the hydraulic cylinder is moved up and down by some linear motion mechanism (feed screw mechanism, cylinder, jack, etc.) having rigidity sufficiently higher than that of the hydraulic cylinder. Is possible.
Also, as shown in FIG. 10B, prepare a platform with several different heights for the installation base of the hydraulic cylinder casing, and replace the platform so that the support position becomes the target support rigidity. Also good. In this case, the support stiffness can be adjusted to any desired value by using the accumulator or preload method described later.

11A to 11D are diagrams showing a sixth embodiment of the adjusting means 13B of the present invention. In this example, the support rigidity is adjusted by changing the accumulator volume.
That is, the support rigidity by the hydraulic cylinder 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, the hydraulic cylinder support rigidity can be adjusted by changing the gas volume in the accumulator.

The following method is mentioned as a method of changing the gas volume in the accumulator.
・ Set initial charging pressure of accumulator gas ・ Set constant pressure supply value of hydraulic pressure ・ Install multiple accumulators and select the accumulator to be used

  As an example, FIGS. 12 and 13 show the amount of change in the cylinder support rigidity depending on the setting of the initial charging pressure of the accumulator gas.

  In addition to the method of setting the initial enclosed pressure of the accumulator, the gas volume in the accumulator can be changed by setting the pressure supplied to the cylinder (constant pressure supply value), so the cylinder support rigidity can be adjusted in the same way It becomes. Also, the cylinder support rigidity can be adjusted by preparing a plurality of accumulators and selecting / switching the accumulator to be used. Furthermore, if each method is used in combination, the adjustment range can be expanded.

14A and 14B are diagrams showing a seventh embodiment of the adjusting means 13B of the present invention. In this example, the support rigidity is adjusted by changing the preload amount of the hydraulic cylinder.
Since the bulk elastic coefficient of the hydraulic fluid changes depending on the operating pressure, the support rigidity by the hydraulic cylinder can be adjusted by changing the operating pressure region.

15 to 17 are examples of mineral-based hydraulic fluid and bulk modulus.
As shown in FIG. 16, if a working fluid whose volume elastic modulus changes in a range of about 1.7 to 2.2 GPa in a pressure range of 0 to 40 MPa · abs is used, an initial hydraulic cylinder in FIG. The support stiffness of the hydraulic cylinder can be adjusted by setting the pressure and changing the bulk modulus. As an example, FIG. 17 shows changes in characteristics of the hydraulic cylinder reaction force vs. stroke compression amount due to changes in the initial pressure. However, the range of values taken by the bulk modulus (about 1.7 to 2.2 GPa) in FIG. 16 is merely an example, and the range of values taken by the bulk modulus is greatly different depending on the type of hydraulic oil. FIG. 17 shows the above characteristic change in the case where there is a change in the bulk modulus as shown in FIG.

[Adjustment of slide tilt and deflection]
When adjusting both the inclination and the deflection of the slide 3, the adjustment method of FIG. 3 and the adjustment method of FIG. 5 can be performed together. For example, first, according to FIG. 3, the inclination of the slide 3 is adjusted by adjusting the overload cylinder 13A1 without adjusting the rigidity adjustment cylinder 13A2, and the inclination of the slide 3 is adjusted in this way. According to FIG. 5, the deflection of the slide plate 3b can be adjusted by adjusting the rigidity adjusting cylinder 13A2. As a result, the difference between the attitude data of the slide 3 (a combination of the inclination data and the deflection data) and the target attitude data (a combination of the target inclination data and the target deflection data) in the simulation press machine 10 is sufficiently reduced. Or can be eliminated.

  According to the press machine 10 and the adjustment method thereof according to the above-described embodiment, the slide posture can be adjusted by adjusting the stroke position of the cylinder device 13A. Therefore, it is possible to reduce or eliminate the machine difference regarding the posture of the slide 3 during the press working.

  Further, since the relative position between the slide drive mechanism 5 and the slide 3 changes due to the change in the stroke position of the cylinder device 13A, the posture of the slide 3 during the press working can be adjusted effectively.

  Since the inclination of the slide 3 can be adjusted by adjusting the stroke position of the cylinder device 13A, the inclination of the slide 3 can be adjusted effectively.

  By adjusting the stroke position of the cylinder device 13A, the extension amount of the connecting member 15 at the time of pressing can be adjusted. Therefore, the amount of deformation of the slide 3 at the time of pressing by adjusting the extension amount of the connecting member 15 can be adjusted. Can be adjusted effectively.

  Since a plurality of cylinder devices 13A apply a load to a plurality of slides 3 respectively, the posture of the slide 3 can be adjusted more finely by adjusting these cylinder devices 13A separately, thereby further reducing machine differences. Or you can eliminate it.

  Since the rigidity of the connecting member 15 of the simulation press machine 10 is higher than the rigidity of the connecting member of the simulation target press, the slide 3 can be moved by reducing the stroke position of the cylinder device 13A in the direction of decreasing the rigidity of the cylinder device 13A. Can be adjusted effectively.

  The present invention is not limited to the above-described embodiment, and various changes can be made without departing from the scope of the present invention.

  In the slide drive mechanism 5, the slide is moved up and down using the drive gear 5 a and the link 5 b, but the slide drive mechanism may be configured by other means for moving up and down the slide 3.

  In the embodiment described above, four overload cylinders 13A1 are provided, but other numbers (including one) of overload cylinders 13A1 other than four may be provided.

  The adjusting means 13B may have a configuration other than that shown in FIG.

It is a block diagram of the press machine by embodiment of this invention. Although it is the II-II line arrow figure of FIG. 1, only the structure of slide vicinity is shown. It is a flowchart which shows the method of adjusting the inclination of a slide. It is a block diagram of the adjustment means which adjusts the inclination of a slide. It is a flowchart which shows the method of adjusting the deflection | deviation of a slide. It is 1st Embodiment figure of the adjustment means which adjusts the deflection | deviation of a slide. It is 2nd Embodiment figure of the adjustment means which adjusts the deflection | deviation of a slide. It is 3rd Embodiment figure of the adjustment means which adjusts the deflection | deviation of a slide. It is a 4th embodiment figure of the adjustment means which adjusts the deflection of a slide. It is 5th Embodiment figure of the adjustment means which adjusts the deflection | deviation of a slide. It is 6th Embodiment figure of the adjustment means which adjusts the deflection | deviation of a slide. It is an Example of 6th Embodiment. FIG. 4 is a relationship diagram between an initial charging pressure of accumulator gas and cylinder support rigidity. It is a 7th embodiment figure of the adjustment means which adjusts the deflection of a slide. It is an Example of 7th Embodiment. It is a related figure of a bulk elastic modulus and a pressure. FIG. 6 is a relationship diagram between a hydraulic cylinder reaction force and a stroke compression amount due to a change in initial pressure.

Explanation of symbols

3 slide, 3a slide body, 3b slide plate,
5 slide drive mechanism, 5a drive gear, 5b conversion mechanism (link),
7 counter balance cylinder, 9 under load support member (bed),
10 Press machine, 11 Upper load support member (crown),
13 Slide adjusting device, 13A Cylinder device, 13B Adjusting means 13A1 Overload cylinder, 13A2 Rigidity adjusting cylinder device 15 Connecting member (upright), 17 Bolster, 19 Carrier,
21 cushion pins, 23 cushion pads, 25 cushion cylinders,
29 control device, 31 hydraulic control circuit

Claims (7)

An upper die and a lower die that are pressed by sandwiching a workpiece in the vertical direction, a slide in which the upper die is fixed to the lower surface and moved up and down, and a slide drive mechanism that raises and lowers the slide to generate a press forming force And a slide adjusting device for adjusting the attitude of the slide,
The slide adjusting device includes:
A cylinder device that applies a load to the slide so that the posture of the slide is changed by a change in the stroke position;
A press machine comprising: adjusting means for adjusting a stroke position of the cylinder device.   The said cylinder apparatus connects the said slide drive mechanism and the said slide, The relative position of the said slide drive mechanism and the said slide changes by the stroke position change of a cylinder apparatus by this, The Claim 1 characterized by the above-mentioned. Press machine.   The press machine according to claim 1, wherein when the stroke position of the cylinder device changes, the inclination of the slide with respect to a horizontal direction changes. The cylinder device connects the slide drive mechanism and the slide,
Furthermore, an upper load support member that supports an upward load acting from the slide drive mechanism during press working,
A lower load support member for supporting a downward load acting from the lower mold during press working;
A connecting member that connects the upper load supporting member and the lower load supporting member,
2. The press machine according to claim 1, wherein an extension amount of the connecting member at the time of pressing is adjustable by adjusting the stroke position.   The press machine according to any one of claims 1 to 4, wherein a plurality of the cylinder devices are provided, and each of the cylinder devices applies a load to a plurality of slides. An upper die and a lower die that are pressed by sandwiching a workpiece in the vertical direction, a slide in which the upper die is fixed to the lower surface and moved up and down, and a slide drive mechanism that raises and lowers the slide to generate a press forming force A method for adjusting a simulation press machine comprising:
A cylinder device that applies a load to the slide so as to change the posture of the slide by changing the stroke position is provided in the simulation press machine,
Acquire the posture data of the slide of the simulation target press as target posture data,
A method for adjusting a press machine, comprising: adjusting a stroke position of a cylinder device so as to reduce or eliminate a difference between slide attitude data and target attitude data in the simulation press machine. The simulation press machine and the simulation target press include an upper load support member that supports an upward load that acts from the slide drive mechanism during press processing, and a lower load support that supports a downward load that acts from a lower mold during press processing. A member, and a connecting member that connects the upper load supporting member and the lower load supporting member,
The cylinder device connects the slide drive mechanism and the slide,
7. The method of adjusting a press machine according to claim 6, wherein the rigidity of the connecting member of the simulation press machine is set higher than the rigidity of the corresponding connecting member of the simulation target press.

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