EP0375888B1 - Spindelpresse - Google Patents

Spindelpresse Download PDF

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Publication number
EP0375888B1
EP0375888B1 EP89120458A EP89120458A EP0375888B1 EP 0375888 B1 EP0375888 B1 EP 0375888B1 EP 89120458 A EP89120458 A EP 89120458A EP 89120458 A EP89120458 A EP 89120458A EP 0375888 B1 EP0375888 B1 EP 0375888B1
Authority
EP
European Patent Office
Prior art keywords
spindle
bearing
screw press
spindle nut
force
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.)
Expired - Lifetime
Application number
EP89120458A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0375888A2 (de
EP0375888A3 (en
Inventor
Karl Hermann Claasen
Günter Czwalinna
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.)
Beche and Grohs GmbH
Original Assignee
Beche and Grohs GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Beche and Grohs GmbH filed Critical Beche and Grohs GmbH
Publication of EP0375888A2 publication Critical patent/EP0375888A2/de
Publication of EP0375888A3 publication Critical patent/EP0375888A3/de
Application granted granted Critical
Publication of EP0375888B1 publication Critical patent/EP0375888B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • B30B1/18—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 screw means
    • B30B1/188—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 screw means driven by a continuously rotatable flywheel with a coupling arranged between the flywheel and the screw
    • 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
    • B30B1/18—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 screw means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0088—Lubricating means

Definitions

  • the invention relates to a screw press and a method for operating a screw press with the features of the preamble of claims 1 and 7 respectively.
  • Such screw presses are known in the prior art. Reference is only made, for example, to DE-A-34 31 306. Such screw presses are suitable for hot, semi-hot and cold forming. For example, the screw presses are used for the production of wheel hubs in the forging business, but also for cutlery production, for coin and dimensional embossing, calibration and for sheet metal forming, for example the production of flat drawn parts from thick sheets.
  • Screw presses of the type in question are generally constructed so that a flywheel is arranged above the spindle, which runs continuously.
  • the spindle can be connected to the flywheel via a clutch, for downward movement and for performing the working stroke of the ram.
  • Screw presses are also known in which the spindle is moved by an electric motor. After the forming process has been carried out, or more precisely shortly before the lower turning point is reached, the coupling between the spindle is used for the flywheel design and released the flywheel.
  • the spindle is coupled to the plunger via a spindle nut. Hydraulic cylinders act on the tappet, which, together with the spindle nut, move it back to the starting position. Due to the high acting forces there are considerable problems with regard to of the guides and bearings.
  • hydrodynamic lubrication has previously been provided on the running surfaces of the spindle nut and on the spindle track bearing running surfaces in known spindle presses.
  • hydrodynamic lubrication can only be achieved incompletely, since, due to the structural conditions, a permanent hydrodynamic lubricant film cannot be built up. To make matters worse, the treads are pressed almost constantly during operation. Due to incomplete lubrication, mixed friction occurs during the working stroke, i.e. in the phase of maximum load, which is associated with correspondingly high wear. Often, even during the pressure-free downward and upward movement of the plunger, a hydrodynamic lubricating film is missing or does not build up, so that mixed friction is also present in the depressurized operation.
  • the object of the invention is to provide a screw press and a method for operating a screw press of the types mentioned at the outset, in which there is significantly reduced wear in the guide or bearing areas without reducing the design safety reserves.
  • the invention is based on the knowledge that it would be structurally practically not feasible to provide a hydrostatic bearing which is effective over the entire stroke and the entire press force range of the screw press, but a hydrostatic bearing is also associated with considerable advantages if the hydrostatic state can only be maintained up to a certain proportion of the maximum force.
  • This proportion, up to which the hydrostatic conditions exist can be, for example, 1/2, 2/3 or more of the maximum force of the screw press, depending on the design of the screw press.
  • an actual mixed friction in the bearing or guide areas only results over a very small time range, which can be measured in a few milliseconds. This is accompanied by a considerable reduction in the frictional forces.
  • an actual mixed friction can only occur in a very short period of time, taking into account the time required for the lubricating gap to be compressed.
  • this mixed friction if it occurs, occurs only over a very small distance, since the relative movement of the spindle to the thrust bearing or to the Spindle nut is correspondingly extremely low in this very short time.
  • the design according to the invention also leads to further decisive advantages: the repeatability of the pressing force is significantly increased.
  • the maximum press force can be calculated more precisely.
  • the machine efficiency is increased; For example, the flywheel and the drive motor can also be made smaller in this way.
  • a restoring moment for the spindle also results immediately after the forming process has ended, after the hydrostatic bearing has collapsed in whole or in part.
  • the spindle decoupled from the flywheel is acted upon by the pressure of the hydrostatic bearing, for example 300 bar, which is present in the supporting flanks of the spindle nut. Due to the course of the supporting flanks of the spindle nut, there is also a force component in the horizontal direction which tries to move the spindle, since the spindle nut has reached its end position.
  • the pressure present in the hydrostatic bearing not only distances the flanks of the spindle nut and spindle again, but also causes a return torque with respect to the spindle decoupled from the flywheel.
  • the hydrostatic bearing is formed only between the supporting flanks of the spindle nut and the respective counter flanks of the spindle. If the hydrostatic bearing were formed on the loaded and the unloaded flank of a thread turn of the spindle, the counter pressure present on the unloaded side would not allow the flanks to be distanced again in the manner described.
  • a spindle press of the type in question here can also, as already mentioned, have an upper track bearing for the spindle.
  • the invention proposes to also design this thrust bearing as a hydrostatic bearing with a pressure setting corresponding to the spindle nut bearing. A practically wear-free run also results in the track bearing.
  • the lubricating film must also be in the thrust bearing (first) to be squeezed. This in turn has an advantageous effect with regard to the necessary total time and thus the remaining time for the state of actual mixed friction.
  • the invention proposes in a further embodiment that the bearing pockets in the spindle nut, which are designed for the hydrostatic structure of the lubricating film, are shaped as, for example, central longitudinal channels following the thread line. For example, in a screw press of the type in question four threads are formed, each with a pitch of 12 °.
  • the bearing pockets are designed as a channel over the entire length of a thread.
  • the storage pockets need only be formed on one side of the flank, since the load always occurs on the same side.
  • the bearing pocket which is thus designed as a thread line following a channel, is preferably arranged approximately in the middle of the supporting flanks of a spindle nut. At regular intervals, feed lines are connected through which the lubricant is pumped into the bearing pockets with the appropriate pressure.
  • the channel can be in one part or in several parts, that is to say segment-like.
  • the short-time overpressure is also applied as a function of the forming phase.
  • the short-term overpressure can be triggered by hitting the plunger of a screw press described here.
  • the required short-term overpressure is around 800 bar for a screw press with a nominal force of 1,600 t and the usual dimensions of the spindle and the spindle nut.
  • a screw press with a nominal force of 1,600 t can be loaded up to 2,500 t and in 10% of the strokes even up to 3,200 t.
  • the maximum achievable force is determined by the clutch starting to grind, which starts at around 3,800 t. If the screw press is only loaded up to 1,600 t, a pressure of about 500 bar is sufficient for the short-term overpressure.
  • the short-term overpressure is also important regardless of whether hydrostatic conditions are reached or maintained during the forming phase. Even if it is not possible to maintain or adjust hydrostatic conditions due to the short-term overpressure.
  • the short-term overpressure triggered shortly before the lower turning point of the tappet also serves to reliably and quickly restore hydrostatic conditions in the bearings immediately after the shaping process has ended and before the tappet starts to move back.
  • the short-term overpressure should not, however, serve to maintain ideal hydrostatic conditions or increase the value of the critical force in any case, even at maximum force. After relieving the tappet, the overpressure should if possible, lift off the counter surfaces as suddenly as possible.
  • the invention also proposes that the separate oil supply be pressurized by means of a hydraulic accumulator, to which a separate pump is assigned, and that the oil supply can be introduced into the hydrostatic bearing via a quick-opening hydraulic valve. There is therefore a separate system for generating this overpressure.
  • the accumulator is filled during a large part of the press play. To separate the running surfaces, the accumulator is connected to the storage pockets shortly before the lower turning point of the ram by the quick-opening hydraulic valve. To achieve the shortest possible pressure build-up time, it is advantageous to arrange the accumulator as close as possible to the running surface or the bearing flanks.
  • a screw press 1 with a plunger 2 which is used for carrying out by means of a spindle 3 a forming process is movable.
  • the lowered plunger 2 can be moved back into its starting position by means of hydraulic cylinders 4.
  • the spindle 3 can be coupled to a flywheel 7 via a coupling.
  • the force or energy for moving the ram during the forming process is taken from the flywheel 7.
  • the spindle 3 is mounted in a spindle nut 5, which is received in the plunger 2. Furthermore, the spindle 3 is supported by means of a thrust bearing 6. The spindle 3 with the spindle nut 5 and the plunger 2 are all received in a press frame 18.
  • the flywheel 7 rotates in the same direction. After or shortly before the end of the working stroke, the clutch 19 between the flywheel 7 and the spindle 3 is released and the upward movement of the tappet 3 is carried out by means of the hydraulic return lifting device (hydraulic cylinder 4) mentioned.
  • the spindle nut 5 and the thrust bearing 6 are designed as hydrostatic bearings in the spindle press 1 shown. This is shown in detail in FIG. 4, for example.
  • lubricant namely oil
  • the hydrostatic bearing is effective during the up and down stroke and also during the forming process, but here only up to a certain force F1 (see FIG. 3), which represents a fraction of the force Fmax.
  • F1 represents a fraction of the force Fmax.
  • the hydrostatic bearing is designed in such a way that the area and gap pressure are determined such that, up to a pressing force which corresponds to approximately half the maximum force, there is practically complete hydrostatic lubrication, ie the spacing of the flanks 10 of the spindle 3 and the flanks 11 the spindle nut 5 is practically unchanged.
  • the assigned bearing surfaces are not immediately in the mixed friction area. Rather, the gap height h initially decreases (see FIG. 4), in a very short time, but still in a substantial time in relation to the remaining forming time.
  • the procedure is such that a channel following the thread is formed, which is arranged approximately centrally on the flank 11 of the spindle nut 5.
  • the spindle nut itself can, for example, be four-course, each with a 12 ° pitch. It can also be advantageously provided that the channels are divided over the axial height of the nut. This is advantageous, for example, with regard to a rapid lifting of the flanks 10, 11 before or at the beginning of the return stroke. In this regard, a further separate configuration is also explained below.
  • the hydrostatic bearing in the spindle nut consists of a bearing pocket 8 with a width a and a (medium) height b.
  • the bearing pocket 8 is connected to an oil source under high pressure by means of a connecting line 9.
  • the flank 10 of the spindle 3 lifts up from the flank 11 of the spindle nut 5, namely up to the mentioned height h (which is exaggerated in the drawing).
  • the height h is dependent on the oil pressure in the bearing pocket 8 and the prevailing force in the spindle 3.
  • the bearing pocket 8 is further connected to the connecting line 9 by a feed line 20, which has a smaller diameter than the connecting line 9 and also a somewhat smaller diameter has as it corresponds to the width a of the storage pocket 8.
  • the dimensions are chosen so that the width a of the bearing pocket 8 to the width A of the effective flank surface of the flank 11 behaves as 1: 6.
  • the height b corresponds approximately to the width a, a channel base of the bearing pocket 8, as shown in the drawing, being rounded.
  • the diameter of the connecting line 20 is somewhat, for example 20%, smaller than the width a of the storage pocket 8, while the diameter of the feed line 9 is approximately twice as large as the diameter of the connecting line 20.
  • a relatively low pressure of, for example, 20 bar prevails in the bearing pocket 8 or in the hydraulic fluid located and emerging therein before the ram comes into contact with the workpiece. This pressure is sufficient to distance the flanks 10 and 11 from one another.
  • the pump which conveys the hydraulic fluid through the feed line 9 and the connecting line 20 into the bearing pocket 8 is, however, designed for a substantially higher back pressure, for example up to 300 bar. If the plunger 2 comes into contact with the workpiece in the further course of the working stroke, the counter pressure exerted by the spindle 3 increases and the pressure in the bearing pocket 8 increases accordingly. In the case of very short forming processes, the time period is far too short for the flanks to break through 10,11 distant layer of hydraulic fluid could come. With longer forming times, which are approximately 150 to 200 ⁇ s, the pressure in the hydrostatic bearing, according to current knowledge, definitely rises up to the back pressure of the pump which is mentioned as an example.
  • the connecting line 20 has a smaller diameter than the bearing pocket 8, on the one hand, and the feed line 9, on the other hand, it does not, or not essentially, acts as a throttle known per se for hydrostatic bearings in the prior art. Nevertheless, such a hydrostatic bearing can also be designed with a throttle in the manner known in the prior art. However, there is significant heating of the hydraulic fluid, which should be avoided as far as possible.
  • a configuration supports the use of relatively viscous oil, such as the hydrostatic bearing for the screw press in general.
  • a high oil viscosity is advantageous with respect to the time required to bring the flanks 10 and 11 into contact with one another when the critical force F1 is exceeded. For example, an oil viscosity of 460 cSt is used. This means that the toughness of the oil used here can be about 2 to 4 steps higher than the toughness of the oil used in known lubrications on screw presses.
  • FIG. 5 shows a circuit diagram with which the hydrostatic bearing can be acted upon with a short-term overpressure from a separate oil supply 12 shortly before the lower reversal point of the plunger 2 is reached.
  • this arrangement consists of a hydraulic accumulator 13 which interacts with a separate pump 14.
  • the hydraulic accumulator 13 is connected to the hydrostatic bearing via a separate line 15, in which quick-opening hydraulic valves 16 are arranged.
  • the hydraulic accumulator is included Lubricant filled, which is then under such a high pressure that the bearing or running surfaces of the spindle nut 5 and the thrust bearing 6 are almost suddenly distanced from each other at the beginning of the return stroke and the return stroke movement of the tappet can again run completely with hydrostatic lubrication.
  • the accumulator 13 is connected to the channels or bearing pockets 8 shortly before the lower turning point of the tappet 2 by the quick-opening hydraulic valves 16. It is advantageous to arrange the accumulator 13 as close as possible to the spindle nut or the track bearing in order to achieve the shortest possible pressure build-up time.
  • the accumulator 13 is filled during a large part of the press play.
  • 17 is also a pressure valve. It is understood that the pressure that can be applied briefly by the additional unit is considerably higher than the operating pressure of the hydrostatic bearing. With regard to the latter, an oil pressure of, for example, 300 bar is used.
  • the above-described device also serves, according to the invention, to act upon the hydrostatic bearing shortly before reaching the lower reversal point of the ram with a short-term overpressure of such a height that hydrostatic or at least quasi-hydrostatic conditions also exist during a maximum load on the bearing.
  • a short-term overpressure of such a height that hydrostatic or at least quasi-hydrostatic conditions also exist during a maximum load on the bearing.
  • work is carried out briefly with pressures of up to 800 bar or more, based on a nominal force of a screw press of 1,600 t.
  • the short-time overpressure is applied as a function of the forming phase.
  • the short-term overpressure can be triggered controlled by the current press force.
  • This measure can also be used as a hydrostatic bearing, as described in detail above, even without designing the bearing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Press Drives And Press Lines (AREA)
  • Materials For Medical Uses (AREA)
EP89120458A 1988-12-23 1989-11-06 Spindelpresse Expired - Lifetime EP0375888B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3843547 1988-12-23
DE3843547 1988-12-23
DE3928652 1989-08-30
DE3928652A DE3928652A1 (de) 1988-12-23 1989-08-30 Spindelpresse

Publications (3)

Publication Number Publication Date
EP0375888A2 EP0375888A2 (de) 1990-07-04
EP0375888A3 EP0375888A3 (en) 1990-07-18
EP0375888B1 true EP0375888B1 (de) 1994-07-27

Family

ID=25875570

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89120458A Expired - Lifetime EP0375888B1 (de) 1988-12-23 1989-11-06 Spindelpresse

Country Status (8)

Country Link
EP (1) EP0375888B1 (enrdf_load_stackoverflow)
JP (1) JPH02224891A (enrdf_load_stackoverflow)
AT (1) ATE109042T1 (enrdf_load_stackoverflow)
BR (1) BR8906693A (enrdf_load_stackoverflow)
CZ (1) CZ280160B6 (enrdf_load_stackoverflow)
DE (2) DE3928652A1 (enrdf_load_stackoverflow)
ES (1) ES2057060T3 (enrdf_load_stackoverflow)
RU (1) RU1831430C (enrdf_load_stackoverflow)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4028886A1 (de) * 1990-09-12 1992-03-19 Beche & Grohs Gmbh Spindelpresse
DE4039911C2 (de) * 1990-12-14 1997-04-03 Langenstein & Schemann Gmbh Lagerung einer Spindel-Schwungrad-Einheit einer Spindelpresse
US6189444B1 (en) 1998-01-07 2001-02-20 GEBR. SCHMIDT FABRIK FüR FEINMECHANIK Press having a dosing system
DE19705461C2 (de) 1997-02-13 1999-11-25 Schmidt Feinmech Presse mit Dosieranlage
US6095298A (en) * 1998-05-07 2000-08-01 The Minster Machine Company Wet clutch/brake for a mechanical press
CN101474879B (zh) * 2009-01-20 2011-05-04 山东理工大学 螺旋压力机的驱动装置
CN102357635A (zh) * 2011-08-16 2012-02-22 王一多 一种电动螺旋压力机

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT191741B (de) * 1955-03-24 1957-09-10 Haemmerle Ag Spindelpresse
US3640590A (en) * 1968-08-13 1972-02-08 Koning Maschf P Means utilizing compressed air for confining a pressurized oil film between relatively movable bearing surfaces
DE2851551A1 (de) * 1978-11-29 1980-06-04 Weingarten Ag Maschf Spindelschlagpresse
DE3121588A1 (de) * 1981-05-30 1982-12-16 G. Siempelkamp Gmbh & Co, 4150 Krefeld "umformpresse, insbes. spindelpresse"
DE3431306A1 (de) * 1984-08-25 1986-03-06 SMS Hasenclever Maschinenfabrik GmbH, 4000 Düsseldorf Spindelpresse
IT1220486B (it) * 1988-05-31 1990-06-15 Roberto Camossi Sistema di insonorizzazione particolarmente per presse a vite

Also Published As

Publication number Publication date
EP0375888A2 (de) 1990-07-04
DE3928652C2 (enrdf_load_stackoverflow) 1992-04-02
JPH02224891A (ja) 1990-09-06
EP0375888A3 (en) 1990-07-18
DE3928652A1 (de) 1990-06-28
CS8907059A2 (en) 1991-12-17
ATE109042T1 (de) 1994-08-15
RU1831430C (ru) 1993-07-30
DE58908105D1 (de) 1994-09-01
ES2057060T3 (es) 1994-10-16
CZ280160B6 (cs) 1995-11-15
BR8906693A (pt) 1990-09-11

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