EP0289638A1 - Presse, notamment pour fabriquer des articles pressés à dimensions exactes à partir de matières pulvérulentes, et procédé pour l'opération d'une telle presse - Google Patents

Presse, notamment pour fabriquer des articles pressés à dimensions exactes à partir de matières pulvérulentes, et procédé pour l'opération d'une telle presse Download PDF

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Publication number
EP0289638A1
EP0289638A1 EP87106634A EP87106634A EP0289638A1 EP 0289638 A1 EP0289638 A1 EP 0289638A1 EP 87106634 A EP87106634 A EP 87106634A EP 87106634 A EP87106634 A EP 87106634A EP 0289638 A1 EP0289638 A1 EP 0289638A1
Authority
EP
European Patent Office
Prior art keywords
press
axis
hydraulic
mechanical
press part
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP87106634A
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German (de)
English (en)
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EP0289638B1 (fr
Inventor
Thomas Dr. Ing. Gräbener
Theodor Dr rer pol. Gräbener
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grabener Pressensysteme & Co KG GmbH
Graebener Pressensysteme GmbH and Co KG
Original Assignee
Grabener Pressensysteme & Co KG GmbH
Graebener Pressensysteme GmbH and Co KG
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
Priority to ES87106634T priority Critical patent/ES2016945B3/es
Application filed by Grabener Pressensysteme & Co KG GmbH, Graebener Pressensysteme GmbH and Co KG filed Critical Grabener Pressensysteme & Co KG GmbH
Priority to EP87106634A priority patent/EP0289638B1/fr
Priority to AT87106634T priority patent/ATE55086T1/de
Priority to DE8787106634T priority patent/DE3764089D1/de
Priority to JP63109253A priority patent/JPS63286297A/ja
Priority to CA000566135A priority patent/CA1331266C/fr
Priority to US07/191,289 priority patent/US4917588A/en
Publication of EP0289638A1 publication Critical patent/EP0289638A1/fr
Application granted granted Critical
Publication of EP0289638B1 publication Critical patent/EP0289638B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B11/00—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses
    • B30B11/02—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses using a ram exerting pressure on the material in a moulding space
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/02—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by lever mechanism
    • B30B1/06—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by lever mechanism operated by cams, eccentrics, or cranks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure

Definitions

  • the invention relates to a press which can be used, in particular, for producing dimensionally stable compacts from powdery materials, but which is also suitable for other uses, for example in the fields of plastics pressing technology, deep-drawing technology and stamping technology.
  • the starting point of the invention is a mechanical press with a press frame, in which a press frame and a press table are provided, which are coupled to one another by a mechanical drive, primarily a toggle lever drive, and form a main press ram, which during press operation functions as a so-called main and leading axis is effective.
  • a mechanical drive primarily a toggle lever drive
  • Hydraulic automatic presses are already known for producing dimensionally stable compacts from powdery materials, which can also be used in the production of complex molded parts, in particular those with one or more graduated shapes (see DE-OS 3l 42 l26, for example).
  • the actual press tool works with its own press axis, to which a special hydraulic drive is assigned within the press, in such a way that each of these hydraulics drives relative to the press tool between its filling position and its pressing position have to go through another working path or be controlled.
  • the invention has for its object to provide a press of the type described at the outset, which not only ensures perfectly reproducible operation of all cooperating press axes, but can also be operated at relatively high stroke rates.
  • a further goal is a high level of dimensional stability of the entire press system with permanently high functional reliability.
  • a hydraulic press part with at least one additional press axis, but preferably several additional press axes, can be used in front of the main press ram between the press frame and press table, and in that case the working movement of each press axis of the hydraulic
  • the press part is path-dependent and time-dependent on the working movement of the main and leading axis of the mechanical press part consisting of the press frame and press table.
  • the press axis or press axes of the hydraulic press part can have determinable press paths different from the press axis of the mechanical press part, it is also achieved that the long stroke paths of the press system according to the invention can be derived from the mechanical press part with high stroke rates, while only the much smaller stroke distances have to be covered by the hydraulic press part and can therefore also be adapted to high stroke rates.
  • the mechanical press part not only determines the implementation of the large stroke distances at high stroke rates, but it also performs the control and control function for all hydraulically effected working movements in a particularly advantageous manner. An optimal level of reproducibility and operational safety is therefore achieved and at the same time the possibility of flexible movements is maintained by the hydraulic press part.
  • each press axis of the hydraulic press part is coupled or can be coupled to the main press axis via an electrical or electronic displacement encoder.
  • the press axes of the hydraulic press part with the interposition of a CNC path control via electronic travel ratio value indication units, can be freely programmably coupled to the displacement sensors assigned to the mechanical press part, in such a way that the translation or movement ratio of the hydraulic press part relative to the mechanical press part within predetermined limits, preferably continuously, can be varied while the press frame of the mechanical press part, which acts as the main and leading axis, moves in a fixed 360 ° travel-time curve.
  • the invention provides that the hydraulic cylinders of the various press axes of the hydraulic press part can each be pressurized with their own control loops and high-pressure pumps with pressure medium, and each control loop besides the displacement sensor also includes an associated displacement ratio value input.
  • each press axis of the hydraulic press part is operated independently of all other press axes of the same and can thus be influenced in direct dependence on the mechanical press part. This ensures trouble-free and effective control technology for the individual press axes of the hydraulic press part.
  • control pressure and back pressure for the hydraulic cylinder of the M press axes of the hydraulic press part can be selectively adjusted, the control pressure being adjustable up to 70 bar and the back pressure up to 350 bar.
  • the hydraulic cylinders for the Z-axis and the Y-axis can be controlled up to 350 bar via servo hydraulics.
  • the hydraulic cylinder of the M-axis is also optionally and additionally controllable up to 350 bar via servo-hydraulics.
  • the modular structure of a press according to the invention can also be favorably influenced in that the hydraulic press part - according to claim 8 - can be coupled to the press frame and the press table of the mechanical press part mechanically by means of clamping wedges, but easily detachable, so that an existing mechanical press can be passed through at any time Installation of the hydraulic press part can be tailored to different needs.
  • the hydraulic press part with all - preferably at least three - press axes forms a self-contained built-in adapter for the mechanical press part.
  • a compact and at the same time highly dimensionally stable structure for the hydraulic press part can be achieved according to the features of claim 10 in that the travels of the hydraulic cylinders for the individual press axes of the hydraulic press part correspond to only a fraction of the stroke of the press axis of the mechanical press part. In most cases, Ver comes for the hydraulic cylinder of the hydraulic press part travel distances of up to 20 mm, while the stroke for the press axes of the mechanical press part can be up to 120 mm.
  • the press axes of the hydraulic press part can usually be moved in the same direction as the direction of movement of the press axes of the mechanical press part, they can optionally also be moved in opposite directions if this should be expedient for the pressing process.
  • the mechanical press part e.g. the press table, according to claim l2
  • a press ram or press pulling ram E-press axis
  • a mechanical drive preferably a cam or cam drive
  • the electrical or electronic position encoder for the control and regulation of the hydraulic press part is arranged or installed between the press frame and the press table of the mechanical press part, while there are further electrical or electronic position sensors selective layer detection are located on the different press axes of the hydraulic press part.
  • the path encoders can be queried, compared and compared with each other via the path encoders during each pressing process if readjusted proportionally, in direct dependence on the mechanical press part acting as the main and leading axis.
  • an essential feature of the invention according to claim l7 is that the Y-press axis can be switched on or acted upon for the opposite direction of movement or counter-press movement after reaching the press position or the bottom dead center of the X-press axis.
  • a method according to the invention for the operation of a press for producing dimensionally stable compacts from powdery materials is characterized essentially according to claim 18 by the fact that at least one hydraulic pressing movement is superimposed on the mechanical pressing movement and the hydraulic pressing movement is controlled and / or regulated in direct and exclusive dependence on the mechanical pressing movement.
  • Working accuracy and working speed in this mode of operation of a press depend exclusively on the mechanical press part and can be reproduced exactly at any time.
  • the speed of the hydraulic press movements is determined and / or influenced proportionally in a path-dependent manner by the speed of the mechanical press movements and as a result an optimal compaction of the powdery material within the press mold to the compact can be achieved.
  • a press according to the invention and the method for operating the same can be used when it comes to the production of compacts from powdery materials by the so-called double-die method, as is described on pages 854 to 856 in the "Handbook of Forming Technology” , published in l98l by Karl Hanser Verlag, Kunststoff.
  • a hydromechanical press system 1 which has a toggle press 2 as a mechanical press part.
  • This toggle press 2 has a press frame 3 which carries a press table 4 and in which a press frame 5 is guided so that it can be raised and lowered relative to the press table 4.
  • the press frame 5 is moved in the press frame 3 via a toggle lever system 6 which engages on the one hand via a joint 7 on the press frame 3 and on the other hand via a joint 8 on the press frame 5.
  • a push rod 10 is in drive connection, which can be formed, for example, by the crank pin of a crank drive 11, which is accommodated in the press frame 3, but is not shown in FIG. 1 for the sake of simplicity.
  • the push rod l0 is moved by the drive in a fixed 360 ° travel-time curve in such a way that the toggle lever system 6 continuously performs alternating movements between its extended position and a predetermined kink position and thus the press frame 5 relative to the press table 4 has a precisely defined one , relatively large stroke.
  • a hydraulic press part l2 is adapted, in which the actual pressing tool l3 is in turn integrated.
  • the main press ram of the hydromechanical press system 1 is formed by the cooperation of press table 4 and press frame 5 of the mechanical press part, i.e. the toggle press 2, and is the so-called main and leading axis - the so-called X-axis - for the entire hydromechanical press system 1 effective.
  • the hydraulic press part l2 of the hydromechanical press system l also forms at least one further, but preferably a plurality of further press axes within the hydromechanical press system l.
  • the hydraulic press part 12 is, for example, designed so that it has three additional press axes, namely the so-called M press axis, the so-called Z press axis and the so-called Y press axis.
  • the M press axis acts on the die l5 of the press tool l3 via hydraulic cylinder l4, while the Z press axis acts on a piston rod l7 in the tool l3 via a hydraulic cylinder l6 and the Y press axis acts on a top piston rod l9 in the press tool via a hydraulic cylinder l8 l3 acts.
  • the upper main press ram 20 and the lower main press ram 2l are actuated via the main press ram of the toggle press 2, which is formed by the press table 4 and the press frame 5 and is effective as a so-called X press axis; they therefore carry out the main pressing movement within the hydromechanical press system 1.
  • High-pressure pumps 22, 23, 24, which work separately from one another and are connected to a common liquid reservoir 25, are provided for the hydraulic cylinders 14, 16 and 18 of the hydraulic press part 12 to be pressurized with hydraulic fluid.
  • the forward and return flow of the hydraulic fluid to and from the hydraulic cylinders l4, l6 and l8 is controlled and regulated by means of servo valve systems 26, 27 and 28, which in turn can be influenced by associated electronic travel ratio value input units 29.
  • the electronic travel ratio value input units 29 are freely programmed via a CNC path control as a reference control scale for the X press axis.
  • the input of these displacement ratio value input units 29 lies in comparison with the electronic displacement transducer 30, which is assigned to the mechanical press part forming the main and leading axis for the hydromechanical press system 1, i.e. the toggle press 2, namely between its press table 4 and its press frame 5 is installed.
  • the relative press travel in relation to the main and leading axis the so-called X
  • the so-called X can be determined for each individual press axis of the hydraulic press part 12, that is to say for the M press axis, the Z press axis and the Y press axis - Press axis, specify.
  • valve systems 26 to 28 for the hydraulic cylinders l4, l6 and l8 of the M-press axis, the Z-press axis and the Y-press axis are then influenced via the position transducer 30 and the position ratio value input units 29 such that they adjust the one set in each case Corresponding proportional ratio control and / or regulation of the pressure fluid supply to the various hydraulic cylinders l4, l6 and l8 effect.
  • each individual hydraulic cylinder l4, l6 and l8 is additionally assigned its own electronic position transducer 3l, 32, 33, which is used for selective position sensing of these hydraulic cylinders l4, l6 and l8 and this is continuously sent to the travel ratio value input units 29 reports back.
  • Ratio value input units 29 influences the individual valve systems 26, 27 and 28 for exact compliance with the specified path conditions in the hydraulic press part l2.
  • each of the electronic position transducers 30, 3l, 32 and 33 as well as the travel ratio value input units formed by a microprocessor and the CNC path control, because each individual press axis, i.e. the M press axis, the Z press axis and the Y press axis, works together with its own closed control loop, to which the controlled variable is specified by the displacement encoder on the main press ram of the mechanical press part, i.e. the X press axis of the toggle press 2.
  • valve systems 26, 27 and 28 for supplying hydraulic cylinders l4, l6 and l8 with hydraulic fluid are designed or constructed such that they are servo-controlled for the M-press axis, the Z-press axis and the Y-press axis of the hydraulic press part l2 can be set selectively, the control pressure should preferably be adjustable up to 350 bar.
  • the M-press axis can be selectively pressure-adjusted via a special valve unit in the flow with 70 bar control pressure and 350 bar back pressure.
  • the hydraulic cylinder l4 for the M press axis, the hydraulic cylinder l6 for the Z press axis and the hydraulic cylinder l8 for the Y press axis can be operated independently of one another with up to 50% of the nominal press force of the mechanical with the help of the associated valve system 26, 27, 28 Press part, so the toggle press 2, are applied with the result that optimal work results are obtained in the production of compacts from powdery materials.
  • the travel paths of the hydraulic cylinders l4, l6 and l8 for the M press axis, the Z press axis and the Y press axis of the hydraulic press part l2 are only a fraction of the stroke path for the X press axis of the mechanical press part , namely the toggle press 2, correspond.
  • the stroke of the main press ram forming the X-press axis between its top dead center and its bottom dead center should be at least 120 mm, while travel paths of about 20 mm have proven to be sufficient for the hydraulic cylinders l4, l6 and l8.
  • An important design feature also lies in the fact that the hydraulic cylinders l4, l6 and l8 assigned to the M-press axis, the Z-press axis and the Y-press axis of the hydraulic press part l2 can either be in the same or opposite direction to the direction of movement of the X-press axis on the toggle press 2 can be pressurized with hydraulic fluid.
  • the hydraulic cylinders l4, l6 and l8 are each designed in a double-acting design.
  • the individual press axes of the hydraulic press part 12, that is to say the M press axis, the Z press axis and the Y press axis, can optionally be locked against one another or relative to one another can be released so that the hydromechanical press system l can be easily adapted to the most varied of manufacturing conditions in its mode of operation.
  • the hydromechanical press system 1 For the operation of the hydromechanical press system 1, it is essential that its mechanical press movement can be superimposed on at least one hydraulic press movement and that each hydraulic press movement is controlled and / or regulated in direct and exclusive dependence on the mechanical press movement.
  • the speed of the hydraulic pressing movements is determined and / or influenced proportional to the path by the speed of the mechanical pressing movement, and consequently the compression of the powdery materials in the manufacture of dimensionally stable compacts is achieved in an optimal manner and the formation of relaxation cracks is effectively counteracted.
  • the basic structure of the mechanical press part that is, the toggle lever press 2
  • the toggle lever press 2 can be seen in a vertical section or in a side view
  • FIG. 4 the overall structure of the hydromechanical press system is seen from the front and partly in section is shown.
  • FIG. 5 in enlarged detail and in vertical section, only the hydraulic present part l2 can be seen, which in FIG. 4 is adapted into the toggle press 2.
  • the Fig. 2 of the drawing can be seen that the press frame 5 is in the press frame 3 relative to the press table 4 is raised and lowered and the press frame 5 receives its drive movement from the toggle lever system 6, the the connecting rod 10 designed as a connecting rod is moved via the crank mechanism 11.
  • the crank mechanism 11 is in constant drive connection with a flywheel drive with countershaft 34, which in turn is driven by an electric motor 35, which can be seen, for example, in FIG. 3.
  • a cam 37 is wedged onto the bearing journal 36 of the crankshaft of the crank mechanism 11, this cam 37 being easily exchangeable and can therefore be replaced if necessary.
  • the various cam disks 37 can have different curve shapes and can optionally also be provided with double curves.
  • a rocker 40 can cooperate either via a roller 38 or a roller 39, but in certain cases also simultaneously via both rollers 38 and 39, which is wedged onto a shaft 4l, which is mounted in the press frame 3 for limited angular rotation.
  • the shaft 4l on the other hand, carries a lever 42 which acts on a counterpressure or pull ram 43 which is guided in the press table 4 so that it can be raised and lowered.
  • the counterpressure or pull ram 43 forms a further press axis, the so-called G-press axis, within the hydromechanical press system 1, this G-press axis being moved in a rhythm predetermined by the respective cam plate 37 in direct mechanical dependence on the toggle press 2. 4, partly in section, the overall structure of the hydromechanical press system 1 with the toggle press 2 and the hydraulic one Press part l2 to see.
  • the press frame 5 can be raised and lowered and the press table 4 is supported in a stationary manner.
  • the hydraulic press part l2 which is designed as a self-contained built-in adapter, rests on the press table 4 and is mechanically positively but easily detachably coupled to it via clamping wedges 45.
  • the hydraulic press part 12 is also mechanically positively connected to the upper cross yoke 44 of the press frame 5 by means of corresponding clamping wedges 46 in an easily releasable coupling connection. The rapid installation and removal of the hydraulic press part l2 into and out of the toggle press 2 is therefore possible without problems in the front area thereof.
  • the hydraulic press part l2 has a die holder 47, in which the die l5 of the pressing tool l3, which is only shown in FIG. 1, can be received.
  • the die holder 47 is operatively connected via guide columns 48 to an upper die guide 49, which in turn is assigned to a punch support 50.
  • Another punch support 52 rests on side supports 5l, which are anchored on the press table 4 via the clamping wedges 45.
  • a plunger extension 54 is vertically displaceable, which is in coupling connection with the counterpressure or pulling plunger 43 of the G-axis of the toggle press 2.
  • an auxiliary hydraulic cylinder l6a which, with its piston rod 17a, actuates the auxiliary axis of the hydraulic press part l2 formed therefrom. It is mainly used for core stamp movements (auxiliary movements).
  • a second auxiliary hydraulic cylinder 18 is provided in the punch support 50, which acts on the piston rod l9a and can be used as a second auxiliary axis for core punch movements and punch loading movements.
  • the hydraulic press part l2 achieves a high level of working accuracy with optimal operation, it is important that the position transducers 30 indicated in FIGS. 1 and 4 for the X axis, 31 for the M axis, 32 for the Z axis and 33 for the Y axis directly, ie are connected directly to the press table 4 and to the press frame 5 or to the cylinder housing and the piston rod.
  • the hydraulic press part l2 forms with all press axes, namely the M press axis, the Z press axis and the Y press axis and the associated hydraulic cylinders l4, l6 and l8, a self-contained installation adapter, in which the ram extension 54 for the counterpressure or pull ram 43 is also integrated.
  • the form-fitting coupling connection of the plunger extension 54 with the counterpressure plunger 43 takes place above the press table 4 of the toggle press 2 by means of a coupling part 55.
  • hydraulic cylinders l4, l6 and l8 are designed for the production of relatively short strokes, e.g. of 20 mm each, which correspond to only a fraction of the stroke of the toggle press 2, which between the top dead center and bottom dead center should be at least about 120 mm.
  • FIG. 6 of the drawing shows a working diagram of the hydraulic press system 1, as was explained in detail above with reference to FIGS. 1 to 5.
  • the angle range from 0 ° to 360 ° of a full rotation of the crank drive 11 serving to actuate the toggle lever system 6 is plotted in the diagram according to FIG. 6.
  • the stroke distance between the top dead center OT and the bottom dead center UT is displayed, which of the main press ram forming the X axis of the hydromechanical press system 1 and consisting of the press table 4 and the press frame 5 at a full rotation of the Crank drive ll will go through.
  • the sine curve indicated by a solid line is the movement curve of the main press ram or the X-axis of the toggle press 2.
  • the horizontal dash-dotted line indicates that the M-axis or die l5 is in its rest position in the pressing process shown remains.
  • the dotted line which runs along the sine curve shown in full lines, indicates the course of movement of the Y press axis during the pressing process, while the dashed line indicates the course of movement of the G press axis and the dash-dotted line the movement course of the Z. - Press axis reproduces.
  • the position l within the diagram represents the filling or feeding position of the pressing tool l3, in which it is loaded with the powdery materials.
  • Position 2 specifies the tool position in which the distribution of the filled materials is initiated.
  • Position 3 corresponds to the distribution position of tool l3, while position 4 indicates the pressing position and position 5 shows its ejection position.
  • the X press axis of the toggle press 2 forms the main and leading axis for the hydromechanical press system 1, ie the working movements of all press axes of the hydraulic press part, that is to say the M press axis, the Z press axis and the Y press axis These are determined by the X press axis, but they can be varied according to the different needs by means of the assigned path ratio value input units 29.
  • the working movements of the hydraulic press part 12 are then controlled and regulated by means of the valve systems 26, 27 and 28 in accordance with the specifications of the travel ratio value input units 29.
  • the working movements G-press axis are derived from the drive system of the toggle press 2, the cams 37 being designed as alternating curves which are given different outline shapes for the pull-off, ejection and counter-pressing techniques.
  • the path-time ratio for the movement of the main press ram of the toggle press 2 cannot be changed and therefore advantageously forms the basis for the main or leading axis of the hydromechanical press system 1.
  • the hydraulic press part l2 is preinstalled with respect to all of its hydraulic, electrical and electronic components so that it can be easily coupled and uncoupled by means of associated quick couplings for the energy supply and can be integrated into the control system of the toggle press 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Press Drives And Press Lines (AREA)
EP87106634A 1987-05-07 1987-05-07 Presse, notamment pour fabriquer des articles pressés à dimensions exactes à partir de matières pulvérulentes, et procédé pour l'opération d'une telle presse Expired - Lifetime EP0289638B1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP87106634A EP0289638B1 (fr) 1987-05-07 1987-05-07 Presse, notamment pour fabriquer des articles pressés à dimensions exactes à partir de matières pulvérulentes, et procédé pour l'opération d'une telle presse
AT87106634T ATE55086T1 (de) 1987-05-07 1987-05-07 Presse, insbesondere zum herstellen masshaltiger presslinge aus pulverfoermigen werkstoffen, und verfahren zum betrieb einer solchen presse.
DE8787106634T DE3764089D1 (de) 1987-05-07 1987-05-07 Presse, insbesondere zum herstellen masshaltiger presslinge aus pulverfoermigen werkstoffen, und verfahren zum betrieb einer solchen presse.
ES87106634T ES2016945B3 (es) 1987-05-07 1987-05-07 Prensa, especialmente para fabricacion de piezas prensadas con medida justa de sustancias pulverizadas y procedimiento para funcionamiento de tal prensa
JP63109253A JPS63286297A (ja) 1987-05-07 1988-05-06 プレス、特に粉末材料から寸法どおりのプレス成形品を製造するためのプレスおよびこのプレスの運転方法
CA000566135A CA1331266C (fr) 1987-05-07 1988-05-06 Presse pour le moulage d'articles a partir de materiaux pulverulents et entrainement
US07/191,289 US4917588A (en) 1987-05-07 1988-05-06 Press for molding articles from powdered materials and drive means therefor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP87106634A EP0289638B1 (fr) 1987-05-07 1987-05-07 Presse, notamment pour fabriquer des articles pressés à dimensions exactes à partir de matières pulvérulentes, et procédé pour l'opération d'une telle presse

Publications (2)

Publication Number Publication Date
EP0289638A1 true EP0289638A1 (fr) 1988-11-09
EP0289638B1 EP0289638B1 (fr) 1990-08-01

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP87106634A Expired - Lifetime EP0289638B1 (fr) 1987-05-07 1987-05-07 Presse, notamment pour fabriquer des articles pressés à dimensions exactes à partir de matières pulvérulentes, et procédé pour l'opération d'une telle presse

Country Status (7)

Country Link
US (1) US4917588A (fr)
EP (1) EP0289638B1 (fr)
JP (1) JPS63286297A (fr)
AT (1) ATE55086T1 (fr)
CA (1) CA1331266C (fr)
DE (1) DE3764089D1 (fr)
ES (1) ES2016945B3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4923382A (en) * 1987-11-19 1990-05-08 Theodor Grabener Pressensysteme Gmbh & Co. Kg Press for producing precision parts from powdered material
EP0381089A2 (fr) * 1989-02-02 1990-08-08 Maschinenfabrik Lauffer GmbH & Co. KG Presse hydraulique
DE4114880A1 (de) * 1990-05-09 1991-11-14 Komage Gellner & Co Maschinenf Presse zum verpressen pulverfoermiger massen
DE4203401A1 (de) * 1991-05-02 1992-11-12 Yoshizuka Seiki Co Verfahren und vorrichtung zum steuern einer pulverformpresse
EP1852247A2 (fr) * 2006-05-02 2007-11-07 Fette GmbH Presse destinée à la fabrication de comprimés en matériau poudreux

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL193748C (nl) * 1991-02-26 2000-09-04 Boschman Tech Bv Spuitgietinrichting.
JP3330016B2 (ja) * 1996-04-11 2002-09-30 アイダエンジニアリング株式会社 スライドの下死点位置補正装置
US6571243B2 (en) 1997-11-21 2003-05-27 Amazon.Com, Inc. Method and apparatus for creating extractors, field information objects and inheritance hierarchies in a framework for retrieving semistructured information
DE10040606C2 (de) * 2000-08-16 2002-06-27 Parker Hannifin Gmbh Hydraulisches oder pneumatisches Montagegerät
US20050236727A1 (en) * 2004-04-23 2005-10-27 Niewels Joachim J Method and apparatus for mold component locking using active material elements
CN102963020A (zh) * 2012-11-28 2013-03-13 东莞市虹瑞机械五金有限公司 一种高速冲压机床滑块下死点位置的补偿调整方法

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US2572953A (en) * 1948-08-19 1951-10-30 Baldwin Lima Hamilton Corp Floating press head
DE867514C (de) * 1951-10-28 1953-02-19 Erwin Stegemann Plattenpresse
US2825092A (en) * 1954-11-17 1958-03-04 Bliss E W Co Briquetting press
US3545045A (en) * 1968-09-04 1970-12-08 Paul Vinson Powder compacting subpress
EP0224096A2 (fr) * 1985-11-22 1987-06-03 Erich Netzsch GmbH & Co. Holding KG Presse pour fabriquer des objets formés à partir de matières pulvérulentes ou en forme de granulés

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US4363612A (en) * 1979-03-29 1982-12-14 Ulrich Walchhutter Flywheel and screw press for producing ceramic articles
DE2924704A1 (de) * 1979-06-19 1981-01-15 Dorst Keramikmasch Einrichtung zur festlegung der hoehe von pressteilen an einer presse, insbesondere zum pressen von pressteilen aus pulverfoermigem ausgangsmaterial
US4373889A (en) * 1981-02-13 1983-02-15 Crossley Machine Company, Inc. Hydraulic press assembly
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US4447198A (en) * 1982-10-26 1984-05-08 Wehr Corporation Hydraulic refractory press including product thickness or density control means
US4439129A (en) * 1982-10-26 1984-03-27 Wehr Corporation Hydraulic refractory press including floating upper and lower plunger assemblies
DE8337753U1 (de) * 1983-12-31 1985-04-11 Hoesch Ag, 4600 Dortmund Hydraulische presse zum verpressen von mit glasfasern verstaerkten kunststoffmatten
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Publication number Priority date Publication date Assignee Title
US2572953A (en) * 1948-08-19 1951-10-30 Baldwin Lima Hamilton Corp Floating press head
DE867514C (de) * 1951-10-28 1953-02-19 Erwin Stegemann Plattenpresse
US2825092A (en) * 1954-11-17 1958-03-04 Bliss E W Co Briquetting press
US3545045A (en) * 1968-09-04 1970-12-08 Paul Vinson Powder compacting subpress
EP0224096A2 (fr) * 1985-11-22 1987-06-03 Erich Netzsch GmbH & Co. Holding KG Presse pour fabriquer des objets formés à partir de matières pulvérulentes ou en forme de granulés

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4923382A (en) * 1987-11-19 1990-05-08 Theodor Grabener Pressensysteme Gmbh & Co. Kg Press for producing precision parts from powdered material
EP0381089A2 (fr) * 1989-02-02 1990-08-08 Maschinenfabrik Lauffer GmbH & Co. KG Presse hydraulique
EP0381089A3 (fr) * 1989-02-02 1991-05-15 Maschinenfabrik Lauffer GmbH & Co. KG Presse hydraulique
DE4114880A1 (de) * 1990-05-09 1991-11-14 Komage Gellner & Co Maschinenf Presse zum verpressen pulverfoermiger massen
DE4203401A1 (de) * 1991-05-02 1992-11-12 Yoshizuka Seiki Co Verfahren und vorrichtung zum steuern einer pulverformpresse
EP1852247A2 (fr) * 2006-05-02 2007-11-07 Fette GmbH Presse destinée à la fabrication de comprimés en matériau poudreux
DE102006020213A1 (de) * 2006-05-02 2007-11-08 Fette Gmbh Presse zur Herstellung von Preßlingen aus Pulvermaterial
DE102006020213B4 (de) * 2006-05-02 2009-09-10 Fette Gmbh Presse zur Herstellung von Preßlingen aus Pulvermaterial
EP1852247A3 (fr) * 2006-05-02 2010-07-07 Fette GmbH Presse destinée à la fabrication de comprimés en matériau poudreux

Also Published As

Publication number Publication date
CA1331266C (fr) 1994-08-09
EP0289638B1 (fr) 1990-08-01
ES2016945B3 (es) 1990-12-16
ATE55086T1 (de) 1990-08-15
US4917588A (en) 1990-04-17
DE3764089D1 (de) 1990-09-06
JPS63286297A (ja) 1988-11-22

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