EP0564840A1 - Presse à vis - Google Patents

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Publication number
EP0564840A1
EP0564840A1 EP93104016A EP93104016A EP0564840A1 EP 0564840 A1 EP0564840 A1 EP 0564840A1 EP 93104016 A EP93104016 A EP 93104016A EP 93104016 A EP93104016 A EP 93104016A EP 0564840 A1 EP0564840 A1 EP 0564840A1
Authority
EP
European Patent Office
Prior art keywords
spindle
screw press
press according
clutch
hydraulic motor
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
EP93104016A
Other languages
German (de)
English (en)
Other versions
EP0564840B1 (fr
Inventor
Horst Endter
Hermann-Josef Trimborn
Siegfried Braun
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.)
SMS Hasenclever GmbH
SMS Hasenclever Maschinenfabrik GmbH
Original Assignee
SMS Hasenclever GmbH
SMS Hasenclever Maschinenfabrik 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 SMS Hasenclever GmbH, SMS Hasenclever Maschinenfabrik GmbH filed Critical SMS Hasenclever GmbH
Publication of EP0564840A1 publication Critical patent/EP0564840A1/fr
Application granted granted Critical
Publication of EP0564840B1 publication Critical patent/EP0564840B1/fr
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

Definitions

  • the invention relates to a screw press with a rotatably mounted spindle, a flywheel which rotates continuously in one direction of rotation, a pressure-operated friction clutch, via the clutch disc of which the frictional connection of the spindle to the flywheel can be produced for the working stroke, and a reverse rotation drive for return stroke of the tool slide.
  • Such clutch screw presses have become known from DE-AS 28 372 53 and German utility model 84 25 198.0.
  • the flywheel is continuously driven in the same direction by a vertically arranged electric motor via a flat belt.
  • the spindle with the friction clutch is coupled to the flywheel, the clutch being hydraulically actuated via an annular piston. After coupling, the spindle turns. It drives the slide down until the upper die hits the lower die and deforms the forging material or the workpiece.
  • the flywheel provides the necessary forming energy, which loses speed.
  • the forming process ends when a certain pressing force has developed between the upper and lower die.
  • This can be preselected by adjusting the hydraulic pressure in the clutch because the oil pressure determines the transferable clutch torque and the torque is directly proportional to the pressing force. Now this preselected pressing force occurs towards the end of the forming process on, the clutch slips; then namely when the pressing force generates a torque on the spindle via the thread bevel which is greater than the set coupling torque.
  • a clutch valve is automatically opened so that the clutch opens; while the flywheel continues to rotate, the clutch disc, spindle and slide are decelerated to a standstill.
  • the spindle and the clutch disc are immediately accelerated in the opposite direction. Furthermore, the retraction cylinders are switched to high pressure before the lower reversal point is reached, so that the slide is driven upwards immediately after the shaping process has been completed. Shortly before the top dead center position, the slide and spindle are braked using the retraction cylinders and moved to the specified starting position from which the next stroke is initiated. In this position (braking position) the hydraulic valves to the return cylinders are closed and the clutch is opened. To initiate the stroke, the retraction cylinders must first be controlled to low pressure via the hydraulic valves and the clutch must be closed using hydraulic pressure. In the screw press known from the German utility model, a reverse rotation drive is proposed as an alternative to the return cylinders for the return stroke of the tool slide.
  • the invention has for its object to improve a clutch screw press of the type mentioned, in particular to increase the overall efficiency and in addition to reduce the manufacturing, assembly and operating costs and space requirements.
  • the tool slide for weight compensation is connected to air cylinders and the spindle is provided with a reverse rotation drive designed as a torque storage drive.
  • the invention is based on the knowledge that by a pneumatic weight compensation, as is known per se to avoid counterweights for a friction wheel spindle press from DE-PS 683 784, the tool slide can be kept virtually floating, so that only small surface pressures are present and hardly any weight has to be absorbed by the tooth flanks of the spindle.
  • the pneumatic weight compensation can therefore be combined according to the invention in a clutch screw press with a reverse rotation drive acting directly on the spindle in the form of a torque storage drive.
  • the spindle can advantageously be connected to a hydraulic motor and can thus be designed as a hydraulic torque storage drive.
  • the hydraulic motor that drives the spindle can - because the spindle is relatively light and no other frictional forces acting on the tooth flanks have to be overcome - be designed with a very low drive power. This reduces the space required accordingly, e.g. the hydraulics can easily be placed on the press stage, which considerably reduces the design effort because there is no need for complex, customer-specific or installation-specific pipelines, and at the same time the manufacturing costs are reduced and the assembly and commissioning times are shortened.
  • the hydraulic motor is connected on the one hand to a high-pressure accumulator and on the other hand to a low-pressure accumulator, such that its inlet line (“P" connection) is connected to the high-pressure accumulator and its working line (“A” connection) is connected to the low-pressure accumulator , can be achieved for energy storage from the high pressure side constantly in the upward direction on the spindle torque.
  • the hydraulic motor acts as a pump during the working stroke with which the spindle rotation simultaneously rotates the shaft of the hydraulic or retraction drive motor.
  • the hydraulic motor then sucks hydraulic fluid from the low-pressure accumulator into the high-pressure accumulator during the working stroke. This energy, which is thus transported from the flywheel main drive into the high-pressure accumulator, is immediately available for the return stroke of the slide after the clutch has opened.
  • a brake unit be assigned to the spindle. This can hold the spindle - despite the upward torque coming from the high pressure side - or the slide in the starting position at top dead center.
  • the brake unit does not increase the moment of inertia of the fixed part (flywheels that cannot be uncoupled), so that there are no adverse effects on the switching force and the pressure contact time.
  • a brake disc of the brake unit is positively connected to the spindle via a torsion spring rod
  • the hydraulic motor can advantageously be placed on the head end of the torsion spring bar, the energy of the torsion spring bar can be used as a torque storage drive for the retraction stroke of the slide; the brake disc acts as a flywheel, the rotational energy of which is stored in the torsion bar during the impact.
  • the mechanical torque storage drive that is achieved in this way and also acts as a rotary shock absorber and consists of the torsion spring rod and the brake disc (or flywheel), depending on the design of the torsion spring rod, allows the entire energy required for the return stroke of the slide to be used as spring energy produce.
  • the hydraulic torque storage drive consisting of the hydraulic motor, which also acts as a pump, and one high-pressure and one low-pressure accumulator each, would then no longer be required to retract the carriage. If necessary, it could only be used for set-up work or no longer needed to be designed as a storage drive.
  • a reversing valve be arranged in the feed lines from the hydraulic motor to the low-pressure or high-pressure accumulator.
  • the upward and downward movement can then be achieved by switching over the reversing valve designed as a multi-way valve by means of the hydraulic motor, in that the latter is driven from the high-pressure accumulator.
  • the torsion spring bar could also be shorter, it is recommended that it penetrate the spindle in the longitudinal direction, fixed to the spindle foot and supported at the top with a thickened head piece protruding from the spindle below the brake disc.
  • the result is a completely new design of a clutch screw press, in which the spindle is extended, so to speak, beyond the friction clutch, namely by the torsion spring rod projecting upwards.
  • This is fixed on the spindle foot, for example with a splined shaft inserted into a bushing inserted into the through bore of the spindle, and thus clamped at the bottom, while it can twist at the head end in the bearing and thus generate the spring energy.
  • the brake unit can be arranged on a rotary distributor of the friction clutch via a holding bridge.
  • the rotary distributor is hollow and supplies the clutch or its pressure piston with hydraulic fluid.
  • the brake unit can be secured against rotation using a torque arm that engages the holding bridge.
  • the screw press 1 shown in FIG. 1 has a multi-part machine body 2, in which a tool slide 3 is guided so that it can move up and down.
  • the tool slide 3 is connected to a spindle nut 4, which with a Machine body 2 cooperates in a spindle 5 rotatably mounted with the upper crosshead, so that the tool slide 3 moves depending on the direction of rotation of the spindle 5 via the spindle nut 4 either to the working stroke in the direction of the lower die 7 arranged in the lower yoke 6 of the machine body 2 or removed from it.
  • the spindle 5 is driven by a flywheel 8, which keeps a vertically arranged electric motor 9 in constant rotation via a drive belt 11.
  • a clutch disc 12 is used for the drive connection, which is non-rotatably connected to the spindle and is hydraulically actuated and frictionally coupled to the flywheel 8. This rotates the flywheel 8 and the spindle 5, and the tool slide 3 is struck with the upper die to perform a forging blow against the lower die 7.
  • Air cylinders 13 arranged in the stands of the machine body 2 of the screw press 1 are pressurized and fastened to the tool slide 3 via their piston rods 14, so that the axially moved mass, ie the tool slide 3 together with the spindle nut 4, is completely weight-balanced.
  • the air or weight compensation cylinders 13 are connected to pressure boilers housed in the side stands, so that no special piping is required.
  • the spindle 5 provided with a threaded section 15 for the spindle nut 4 is hollow-drilled, and through the through-bore 16 of the spindle extends a coupling disc 12 which extends far beyond the form-fittingly fixed on the spindle 5, the spindle 5 thus upwardly extending torsion spring rod 17.
  • This is fixed at its lower end via a splined shaft 18 in a spindle bushing 21 inserted into the spindle 5 from the foot end 19 (see FIG. 4).
  • the torsion spring rod 17 has a thickened head piece 22 which is rotatably mounted in a bearing bush 23.
  • the bearing bush 23 is located in a brake unit 24 carrying, on a hydraulic piston for pressing the clutch disc 12 to the flywheel 8 with a pressure medium supplying rotary distributor 25 (compare Figure 3) arranged holding bridge 26.
  • the brake unit 24 is composed of several spring-loaded, pneumatically operated individual brakes 27, which have clamping jaws 28 detect a brake disc 29, which is positively connected to the spindle 5 via the torsion spring bar 17.
  • the spindle 5 with the clutch disc 12 is decelerated to a standstill in accordance with the plastic deformation path of the workpiece and the elastic deformation of the machine parts and then immediately accelerated again in the opposite direction by the elastic spring energy of the machine parts.
  • the brake disc 29 is here delayed due to the attachment via the torsion spring bar 17 over a much larger angle of rotation, so that the rotational energy of the brake disk 29 is not available during the forming process, but is absorbed by the torsion spring bar 17.
  • the spindle 5 accelerates the tool slide 3 upwards, the entire spring energy of the torsion spring rod 17 is released and is available for the return stroke drive.
  • a hydraulic motor 33 which also acts as a pump and is connected to the upper end of the torsion spring rod 17 and thus the spindle 5, is connected via lines 34, 35 to a high-pressure accumulator 36 or low-pressure accumulator 37, as shown in the hydraulic diagram according to FIG. 4 becomes.
  • a high pressure pump 38 In the supply line 34 leading from the high pressure accumulator 36 to the hydraulic pump 33 there is a high pressure pump 38 and in the line 35 leading from the hydraulic motor 33 to the low pressure accumulator 37 there is a low pressure pump 39;
  • several check valves 41, pressure relief valves 42 and a reversing valve 43 designed as a multi-way valve are also provided, for example.
  • the hydraulic units 44 required to supply the hydraulic motor 33 and the rotary distributor 25 are arranged on the stage 32 of the screw press 1 and are connected to the rotary distributor 25 or the hydraulic motor 33 via pressure medium hoses 45.
  • the hydraulic motor 33 is connected by its line 34 to the high-pressure accumulator 36 and by its line 35 to the low-pressure accumulator 37, so that an upward torque is exerted on the spindle 5 and is held by the brake unit 24.
  • the friction clutch is closed by means of hydraulic pressure and thus the spindle 5 is coupled to the flywheel 8 via the clutch disc 12, while the braking unit 24 opens with a slight delay.
  • the clutch disc 12, which is positively fastened on the spindle 5, is accelerated by the flywheel 8 to synchronism via its friction blocks and thus rotates non-positively with the flywheel 8.
  • the spindle 5 rotates out of the spindle nut 4, i.e. the tool slide 3 is driven downwards until it hits the lower die 7 with its die.
  • the compressible force that can be generated is essentially controlled by the clutch torque and thus by the hydraulic pressure in the clutch cylinders.
  • the clutch begins to slip.
  • the clutch valve is opened automatically.
  • the friction clutch then opens; while the flywheel 8 continues to rotate, the spindle 5 and the clutch disc 12 are decelerated to a standstill. Due to the stored spring energy of the spindle 5 and the stand or the machine body 2 of the screw press 1, the spindle 5 and the clutch disc 12 are immediately accelerated again in the opposite direction after the forming process, ie to the right.
  • This effect and thus the return stroke of the tool slide 3 is - as has already been mentioned above - amplified by the energy stored in the torsion spring bar 17 in such a way that no special hydraulic retraction cylinder is required.
  • the hydraulic motor 33 Since the shaft of the hydraulic motor 33 mounted on the torsion spring rod 17 is simultaneously rotated with the rotation of the spindle 5 during the downward movement of the tool slide 3, the hydraulic motor 33 acts as a pump. Supported by the low-pressure pump 39, it pumps additional pressure medium into the high-pressure accumulator 38 during the working stroke. This energy is also immediately available after the friction clutch has opened and drives the spindle 5 in the opposite direction until the spring-loaded, pneumatically actuated brakes 27 of the brake unit 24 capture the brake disc 29 with the clamping jaws 28 and brake the spindle 5 with the tool slide 3 in the preselected position, namely the starting or starting position, from which the next working stroke can be initiated. In order to set up the screw press 1, the hydraulic motor 33 is driven from the high-pressure accumulator 36 by switching the reversing valve 43.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Control Of Presses (AREA)
EP93104016A 1992-03-18 1993-03-12 Presse à vis Expired - Lifetime EP0564840B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4208638A DE4208638C2 (de) 1992-03-18 1992-03-18 Kupplungs-Spindelpresse
DE4208638 1992-03-18

Publications (2)

Publication Number Publication Date
EP0564840A1 true EP0564840A1 (fr) 1993-10-13
EP0564840B1 EP0564840B1 (fr) 1996-06-19

Family

ID=6454348

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93104016A Expired - Lifetime EP0564840B1 (fr) 1992-03-18 1993-03-12 Presse à vis

Country Status (2)

Country Link
EP (1) EP0564840B1 (fr)
DE (2) DE4208638C2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2340778A (en) * 1998-08-26 2000-03-01 Minster Machine Co Rotary member for mechanical press
CN102581149A (zh) * 2012-02-23 2012-07-18 西安交通大学 一种伺服电机飞轮储能式无铆钉连接装置及其连接方法
CN107234202A (zh) * 2017-06-13 2017-10-10 贾元友 离合器与电动复合传动式带有下死点气动螺旋压力机

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19507056A1 (de) * 1995-03-01 1996-09-05 Hasenclever Maschf Sms Spindelpresse und Verfahren zum Betreiben einer Spindelpresse
DE19507055C2 (de) * 1995-03-01 1999-03-04 Hasenclever Maschf Sms Spindelpresse

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE683784C (de) * 1934-12-06 1939-11-15 Ferdinand John Reibradspindelpresse
DE3423643A1 (de) * 1984-06-27 1986-01-02 Werner 4005 Meerbusch Bothe Spindelpresse
DE3613471A1 (de) * 1986-04-22 1987-10-29 Hasenclever Maschf Sms Spindelpresse zur herstellung von feuerfesten formsteinen
DE3841852A1 (de) * 1988-12-13 1989-07-27 Franek Johann Dipl Ing Fh Antriebsanordnung fuer eine spindelpresse

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE900525C (de) * 1936-07-08 1953-12-28 Weingarten Ag Maschf Spindelpresse
DE1134890B (de) * 1956-12-29 1962-08-16 Metallwaren Und Maschinenfabri Bandbremse fuer Friktionsspindelpressen
US3020833A (en) * 1957-05-09 1962-02-13 Banning Ag J Screw press which is operated by hydraulic means
DE1502282A1 (de) * 1963-11-08 1969-03-06 Hasenclever Ag Maschf Spindelpressen mit hydraulischem Antrieb
DE1904723A1 (de) * 1969-01-31 1970-09-03 Novopress Gmbh Einscheiben-Spindelpresse
DE2758973C2 (de) * 1977-12-30 1979-11-22 G. Siempelkamp Gmbh & Co, 4150 Krefeld Spindelpresse
DE2837253C2 (de) * 1978-08-25 1981-09-24 Maschinenfabrik Hasenclever GmbH, 4000 Düsseldorf Spindelpresse
DE3234520A1 (de) * 1982-09-17 1984-03-22 G. Siempelkamp Gmbh & Co, 4150 Krefeld Spindelpresse
DE8425198U1 (de) * 1984-08-25 1985-12-19 SMS Hasenclever Maschinenfabrik GmbH, 4000 Düsseldorf Spindelpresse

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE683784C (de) * 1934-12-06 1939-11-15 Ferdinand John Reibradspindelpresse
DE3423643A1 (de) * 1984-06-27 1986-01-02 Werner 4005 Meerbusch Bothe Spindelpresse
DE3613471A1 (de) * 1986-04-22 1987-10-29 Hasenclever Maschf Sms Spindelpresse zur herstellung von feuerfesten formsteinen
DE3841852A1 (de) * 1988-12-13 1989-07-27 Franek Johann Dipl Ing Fh Antriebsanordnung fuer eine spindelpresse

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2340778A (en) * 1998-08-26 2000-03-01 Minster Machine Co Rotary member for mechanical press
GB2340778B (en) * 1998-08-26 2002-12-04 Minster Machine Co Rotary member for mechanical press
CN102581149A (zh) * 2012-02-23 2012-07-18 西安交通大学 一种伺服电机飞轮储能式无铆钉连接装置及其连接方法
CN102581149B (zh) * 2012-02-23 2014-08-20 西安交通大学 一种伺服电机飞轮储能式无铆钉连接装置及其连接方法
CN107234202A (zh) * 2017-06-13 2017-10-10 贾元友 离合器与电动复合传动式带有下死点气动螺旋压力机
CN107234202B (zh) * 2017-06-13 2019-03-01 贾元友 离合器与电动复合传动式带有下死点气动螺旋压力机

Also Published As

Publication number Publication date
EP0564840B1 (fr) 1996-06-19
DE4208638A1 (de) 1993-10-07
DE4208638C2 (de) 1996-07-11
DE59302974D1 (de) 1996-07-25

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