• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Method for operating a closing unit of a forming machine, wherein a movable platen (2) is controlled by a closing force mechanism (3) applied with a closing force, wherein an assisting force caused by the mass or at least one frictional force of at least one spar (6), the movable Form platen (2) or the movable platen (2) is measured together with a mold half (7) and is taken into account in the control or regulation of the closing force
    公开号:AT514317A4
    申请号:T652/2013
    申请日:2013-08-21
    公开日:2014-12-15
    发明作者:Herbert Dipl Ing Zeidlhofer；Anton Ing Lohnecker
    申请人:Engel Austria Gmbh；
    IPC主号:
    专利说明:

    1 9 9 9 9 9 9 9 9 9 ····················································· 74211 32 / cr ·· 9 9 9 a · · | 9 · 9 9 9 9 1
    The present invention relates to a method for operating a closing unit of a forming machine wherein a movable platen is controlled by a closing force mechanism or controlled with a closing force.
    Under shaping machines are understood injection molding machines, transfer molding, pressing or the like.
    High demands are placed on modern shaping machines with regard to the dimensional accuracy of the produced parts. This goes so far that the closing force and Schließbewegungsprofile that must be performed by movable platens or mounted on mold halves, have a major impact on the quality of the product.
    For example, in injection-compression molding, the closing unit of an injection molding machine must be controlled or regulated so that a defined embossing gap between the mold halves is closed controlled, whereupon the movable platen is to experience an increase in the closing force. There are also special forms of this method in which the embossing gap may be reopened more than once before the plastic dimensions cool.
    This shows how great the influence of the speed and closing force profile can be on the finished product.
    The circumstance described above causes the time required to set up such processes to increase steadily since many series of tests must be performed until the optimal profile is found. Since the situation within the mold halves is often quite complex in such processes, simulations can only help to a limited extent, because it is standard practice to perform a simulation of the injection molding mass per se, whereby the speed and force profiles are specified. It is not always clear, however, whether or not it is possible to use the 2/16 • ······················································
    Simulation entered profiles correspond to reality. Only the execution of many tests and test series can remedy the situation.
    The object of the invention is to provide a method which provides improved control of the speed or force profiles experienced by a movable platen.
    This object is achieved by a method having the features of claim 1. This is done by measuring an assist force caused by the mass or at least a frictional force of at least one spar, the movable platen or the movable platen along with a mold half and taken into account in the control of the closing force.
    It is always "inclusive" to understand, that is, even a combination of "by" or "separate options is of course conceivable and occasionally advantageous.
    In addition to the improved control, another advantage of the invention is that it is possible to at least estimate, if not calculate relatively accurately, the absolute closing force that prevails between the two mold halves. This makes it possible to make better use of simulations when setting up the processes, since the absolute force exerted by the machine can be used, for example, as the boundary condition of a realistic simulation.
    Further advantageous embodiments of the invention are defined in the dependent claims.
    In order to compensate for the influence of the weight, for example a mold half in vertical clamping units, it can be provided that the supporting force is measured by the at least one spar or the movable platen together with a mold half of the closing force mechanism or of a rapid traverse mechanism of the closing unit at a constant height The force exerted on it by the closing force mechanism or the rapid traction mechanism is measured.
    It may be provided that the support force is determined by means of a pressure sensor or a plurality of pressure sensors in at least one hydraulic cylinder of the closing force mechanism or the rapid traverse mechanism.
    In this regard, in a particularly preferred embodiment it can be provided that the assisting force is determined by means of a first pressure sensor in a first chamber of the at least one hydraulic cylinder and a second pressure sensor in a second chamber of the at least one hydraulic cylinder, wherein the value for the counterforce from one with effective Piston area weighted difference of the measured values of the first pressure sensor and the second pressure sensor is determined. It is true that in most operating conditions the pressure in one of the chambers is much lower than in the other. By means of the present invention, however, the control or regulation can be carried out so precisely that even this small effect can produce a relevant falsification.
    In a preferred embodiment it can be provided that the at least one frictional force is measured in the form of an adhesive force of the at least one spar or the movable platen.
    This can be done by measuring a force of gravity of the at least one spar or the movable platen for measuring the adhesive force, that the at least one spar or the movable platen from the closing force mechanism or a rapid traverse mechanism of the clamping unit is kept at a constant level that one of the Closing force mechanism or force exerted by the rapid traverse mechanism counterforce is measured and that the adhesive force from the difference of the amounts of the counterforce and the weight is determined. The weight of the spars and the movable platen is advantageously measured before the assembly of the clamping unit, for example, with a crane scale. 4/16 * · * * * I ·········································································
    Closing force mechanism or counterforce exerted by the rapid traction mechanism can be measured as previously described in the assist force, with the difference that in this case no mold half is mounted on the movable platen. In general, this embodiment is based on the assumption that the presence of a mold half, the adhesive force which occur between the movable platen and spars, or between spars and guides, are only slightly affected. Of course, it is also possible to measure the influence of the weight of the mold half on the adhesive force metrologically. But would have to be known or measured the weight of the mold half.
    A further particularly preferred embodiment may be that the at least one frictional force is measured in the form of a sliding friction force of the at least one spar or the movable platen.
    Again, the weight of the at least one spar or the movable platen can be advantageously measured before assembly of the clamping unit. Likewise, the motive force can be measured in a similar manner as suggested for the counterforce. The effect of the weight of a mold half unfolds similarly as described with respect to the adhesive force.
    At least three different methods have been described for determining forces that distort the absolute closing force. These can be used individually and in combination. It can be decided by the person skilled in which situation (process properties, vertical or horizontal clamping unit) which method makes sense, or which distorting force exerts a relatively large influence.
    Further advantages and details of the invention will become apparent from the figures and the associated description of the figures. Show: 5/16 • ······················································
    1 is a schematic side view of a clamping unit, in the measurement of an assisting force,
    2 is a schematic side view of a closing unit in the measurement of a sliding friction force,
    Fig. 3 is a schematic side view of a closing unit in the closing force structure and
    4 shows a schematic representation of a control concept corresponding to a method according to the invention.
    In Figure 1, a vertical clamping unit 1 is shown purely schematically. It has a pressure mechanism 3, which can cause over Flolme 6 an admission of the movable platen 2 with a closing force. For locking the movable platen 2 with the bars 6, a locking mechanism 13 is provided. In the unlocked state, a movement of the movable platen 2 by means of the rapid traverse mechanism 4 is possible.
    The control or regulation of the printing mechanism 3 and the rapid traverse mechanism 4 is performed by a control or regulating device 5. The illustrated connections between rapid traverse mechanism, control or regulating device and closing force mechanism are of course of a purely schematic nature.
    Both the pressure mechanism 3 and the rapid traverse mechanism 4 have hydraulic cylinders 8.
    The construction of the hydraulic cylinder is analogous in this embodiment both for the rapid traverse mechanism 4 and for the printing mechanism 3. The hydraulic cylinders 8 differ only depending on the requirement profile in their stroke and in their effective piston area.
    The hydraulic cylinders 8 each have a first chamber 10 and a second, rod-side chamber 12, each of which has a different pressure 6/16. . The hydraulic connection of the cylinder is prior art and therefore not shown in detail. At the first chamber 10 and at the second chamber 12 of each hydraulic cylinder 8, a first pressure sensor 9 and a second pressure sensor 11 are arranged, which serve to measure the hydraulic pressure in the respective chamber. Also, the first pressure sensors 9 and the second pressure sensors 11 are connected to the control or regulating device 5. This is not shown for clarity. In the case that the control or regulating device 5 is designed as a control device, serve the first pressure sensors 9 and the second pressure sensors 11 of the feedback of measured values for the control loop.
    In the situation shown in Figure 1, the assisting force (ie, assisting the closing force) exerted by the spars 6 of the movable platen 2 and the mold half 7 in the molding process is measured separately by the rapid traverse mechanism 4 and the printing mechanism 3. For this purpose, the locking mechanism 13 is unlocked. By the sensors in the hydraulic cylinders 8 of the rapid traverse mechanism 4, a first part of the assisting force originating from the movable platen 2 and the mold half 7 is measured. A second part, which originates from the spars 6, is measured by the sensors in the hydraulic cylinders 8 of the pressure mechanism 3. The support force is then determined as the sum of the first and second partial forces.
    The force measurement by the sensors in the hydraulic cylinders 8 will be described below: The effective area in the second chambers 12 is slightly less than the effective area in the first chambers 10. The magnitude of the measured partial forces of the assisting force will therefore be one with the effective areas weighted difference in the amounts of the hydraulic pressures measured by the first pressure sensors 9 and the second pressure sensors 11, determined.
    In the embodiments shown here, any force measured by the pressure sensors in the hydraulic cylinders 8 is performed in the manner described. However, this is not absolutely necessary, since for example the 7/16
    Pressure from those chambers, which have the respective lower pressure, can be completely drained, whereby only the pressure in the respective other chamber contributes to the force application of the hydraulic cylinder 8.
    If the weight forces of the movable platen 2 and the spars 6 are known (for example, by measuring by means of a crane scale before assembly of the clamping unit), with a similar procedure, as described above, and the adhesive force of the movable platen or the spars 6 can be measured , This adhesive force is mainly caused by the guides of the movable platen 2 and the spars 6 and the static frictional force occurring in the hydraulic cylinders. A counterforce is measured analogously to the supporting force, wherein the mold half 7 must be dismantled. The adhesive force can then be determined quite simply from the difference between the amounts of the counterforce and the weight.
    In Figure 2, the purely schematic representation of the clamping unit 1 of Figure 1 is shown again, wherein the locking mechanism 13 is in the locked state and the mold half 7 is dismantled or not yet mounted. To measure the sliding friction force, the movable platen 2 and the bars 6 locked therewith are moved at a constant speed (downwards). The motive force to be applied thereto by the hydraulic cylinders 8 is measured as described above. Furthermore, the weight forces of the movable platen and the spars 6 must be known. The sliding frictional force is then determined from the difference between the amounts of motive force and weight force.
    In the event that an offset force is generated for the printing mechanism 3 during the closing force build-up (see FIG. 3) with the rapid traverse mechanism 4, the embodiment of the measurement of sliding friction illustrated in FIG. 2 is advantageous, since exactly the sliding frictional force is determined also occurs during the production cycle (that is, when the locking mechanism is locked). • · • · · · · · e
    By the method according to the invention it is possible to carry out a regulation or control of the absolute value of the closing force. A corresponding control concept is shown in FIG. In this case, a balance of forces is initially set up from the amounts of the following forces acting on the platen: The first rapid traction FE1, which is determined by means of the first pressure sensors 9 in the first chambers 10 of the hydraulic cylinders 8 of the rapid traverse mechanism 4. The first pressure force FD1, which is determined by means of the first pressure sensors 9 in the first chambers 10 of the hydraulic cylinders 8 of the closing force mechanism 3. The second rapid traction FE2, which is determined by means of the second pressure sensors 11 in the second chambers 12 of the hydraulic cylinder 8 of the rapid traverse mechanism 4. - The second pressure force FD2, which is determined by means of the second pressure sensors 11 in the second chambers 12 of the hydraulic cylinder 8 of the closing force mechanism 3. - The weight force FB of the movable platen 2 together with the mold half 7, which is determined by means of the pressure sensors of the rapid traverse mechanism 4. - The weight FH of the spars 6, which is determined by means of the pressure sensors of the closing force mechanism 3. - The frictional force FR, using, depending on the situation, the sliding friction or static friction.
    The closing force-actual value FS-IST appearing as a result of the balance of forces is compared with a closing force desired value FS-SOLL specified by the operator. The result of this comparison is in turn the control or regulating device 5 formed in this case as a control device - fed. This influences an actuator 15, which in the above embodiment 9/16 Control valve for the hydraulic pressure in the second chambers 12 of the hydraulic cylinder 8 of the closing force mechanism 3 is.
    Of course, the pressures in the remaining chambers of the hydraulic cylinders 8 are subject to similar control or regulating mechanisms. In particular, the control for the first rapid traction force FE1 and the first pressure force FD1 can be designed so that at least one of these two forces is increased, should the pressure in the second chambers 12 of the hydraulic cylinders 8 of the closing force mechanism 3 fall below a certain threshold below which one exact control or regulation of the second pressure force FD2 is difficult.
    The presented control concept allows the regulation of an absolute closing force. This has the advantage that results from simulations or calculations can be used directly to set up the process. Test series to optimize the closing pressure profile can be completely avoided under certain circumstances. For the purposes of this invention, the movable platen 2 also includes any structures that help to support the closing force. An example of this would be the locking mechanism 13.
    Innsbruck, on August 20, 2013 10/16
    权利要求:
    Claims (8)
    [1]
    74211 32/32

    Claims 1. A method of operating a closing unit of a forming machine, wherein a movable platen (2) is controlled by a closing force mechanism (3) to apply a closing force, characterized in that a supporting force caused by the mass or at least one frictional force is at least one Holms (6), the movable platen (2) or the movable platen (2) together with a mold half (7) is measured and taken into account in the control or regulation of the closing force.
    [2]
    2. The method of claim 1 using a vertically closing closing unit (1), characterized in that the supporting force is measured by the at least one spar (6) or the movable platen (2) together with a mold half (7) from the closing force mechanism ( 3) or by a rapid traverse mechanism (4) of the clamping unit (1) is kept at a constant level and the force exerted by the closing force mechanism (3) or by the rapid traverse mechanism (4) is measured.
    [3]
    3. The method according to claim 2, characterized in that the supporting force by means of a pressure sensor or a plurality of pressure sensors (9,11) in at least one hydraulic cylinder (8) of the closing force mechanism (3) or the rapid traverse mechanism (4) is determined.
    [4]
    4. The method according to claim 3, characterized in that the support force by means of a first pressure sensor (9) in a first chamber (10) of the at least one hydraulic cylinder (8) and a second pressure sensor (11) in a second chamber (12) of at least a hydraulic cylinder (8) is determined, wherein the value for the counterforce is determined from an effective piston area weighted difference in the measured values of the first pressure sensor and the second pressure sensor. 11/16 74211 32/32 t ··· ··% > «· · · · ··· · r. · · · «· ♦ · t · ···· ·· ·
    [5]
    5. The method according to any one of claims 1 to 4, characterized in that the at least one frictional force in the form of an adhesive force of the at least one spar (6) or the movable platen (2) is measured.
    [6]
    6. The method of claim 5 using a vertically closing closing unit (1), characterized in that for measuring the adhesive force, a weight of the at least one spar (6) or the movable platen (2) is measured that the at least one spar (6 ) or the movable platen (2) by the closing force mechanism (3) or a rapid traverse mechanism (4) of the clamping unit (1) is kept at a constant level, that a counterforce force exerted therefor by the closing force mechanism (3) or the rapid traverse mechanism (4) is measured and that the adhesion force is determined from the difference between the amounts of the counterforce and the weight force.
    [7]
    7. The method according to any one of claims 1 to 6, characterized in that the at least one frictional force in the form of a sliding frictional force of the at least one spar (6) or the movable platen (2) is measured.
    [8]
    8. The method of claim 7 using a vertically closing closing unit (1). characterized in that for determining the Gleitreibungskraft a weight of the at least one spar (6) or the movable platen (2) is measured, the at least one spar (6) or the movable platen (2) by means of the closing force mechanism (3) or by means of a Rapid traverse mechanism (4) is moved at a constant speed, wherein a movement force applied thereto by the closing force mechanism (3) or the rapid traverse mechanism (4) is measured and the sliding frictional force is determined from the difference in the weights and motive force amounts. Innsbruck, August 20, 2013 12/16
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    JPH0671753B2|1990-06-19|1994-09-14|株式会社日本製鋼所|Injection molding equipment|
    JPH06304984A|1993-04-23|1994-11-01|Mitsubishi Heavy Ind Ltd|Injection compression molding device|
    JP2000211001A|1999-01-27|2000-08-02|Meiki Co Ltd|Method for injection press molding and injection press molding machine|
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    US7753668B2|2007-01-24|2010-07-13|Husky Injection Molding Systems Ltd.|Platen assembly, molding system and method for platen orientation and alignment|
    CN203510597U|2013-08-29|2014-04-02|广州天沅橡胶制品有限公司|Host machine of bicolor liquid silicone rubber injection moulding machine|DE102017223822A1|2017-12-27|2019-06-27|Arburg Gmbh + Co. Kg|Mold-closing unit for an injection molding machine and method for locking a power transmission element|
    AT521382B1|2018-11-14|2020-01-15|Engel Austria Gmbh|Closing unit for a molding machine|
    CN109664455A|2018-12-27|2019-04-23|佛山市顺德区震旭塑料机械有限公司|A kind of injection molding machine with the secondary adjustment mold of inside groove|
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    ATA652/2013A|AT514317B1|2013-08-21|2013-08-21|Method for operating a closing unit|ATA652/2013A| AT514317B1|2013-08-21|2013-08-21|Method for operating a closing unit|
    DE201410012096| DE102014012096A1|2013-08-21|2014-08-13|Method for operating a closing unit|
    CN201410512461.7A| CN104416846B|2013-08-21|2014-08-21|For the method for the closed cell for running forming machine|
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