WO1996026827A1 - Presse a vis et son procede d'exploitation - Google Patents

Presse a vis et son procede d'exploitation Download PDF

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Publication number
WO1996026827A1
WO1996026827A1 PCT/DE1996/000316 DE9600316W WO9626827A1 WO 1996026827 A1 WO1996026827 A1 WO 1996026827A1 DE 9600316 W DE9600316 W DE 9600316W WO 9626827 A1 WO9626827 A1 WO 9626827A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
screw press
return
cylinder space
stroke
Prior art date
Application number
PCT/DE1996/000316
Other languages
German (de)
English (en)
Inventor
Hermann-Josef Trimborn
Original Assignee
Sms Eumuco 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 Eumuco Gmbh filed Critical Sms Eumuco Gmbh
Priority to DE59601226T priority Critical patent/DE59601226D1/de
Priority to EP96904709A priority patent/EP0812255B1/fr
Publication of WO1996026827A1 publication Critical patent/WO1996026827A1/fr

Links

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
    • B30B1/183—Braking mechanisms for the return movement of the press ram

Definitions

  • the invention relates to a method for operating a screw press with a rotatably mounted spindle, a flywheel rotating continuously in one direction of rotation, a pressure-actuated friction clutch, via the clutch disc of which the frictional connection between the spindle and the flywheel can be produced, and a return drive for the return stroke of the a displacement of the machine body up and down movable tool carriage, which is connected for weight compensation to air cylinders having a storage pressure chamber and a piston-side and a piston-side cylinder space, and a screw press for performing the method.
  • Such a clutch screw press has become known from DE 42 08 638 A.
  • the flywheel is continuously driven in the same direction by an electric motor via a flat belt.
  • the spindle is coupled to the flywheel with the hydraulically actuated friction clutch, while a braking unit opens with a slight delay.
  • This consists of several spring-loaded, pneumatically operated individual brakes, which grip a brake disc with clamping jaws, which is positively connected to the spindle via a torsion spring rod arranged in the hollow-bored spindle.
  • the torsion spring bar forms part of the reversing drive, which is designed there in the form of a torque storage drive which draws its energy from a storage device which is charged by the spindle in the course of the tappet and thus the slide downward movement.
  • the clutch disc which is positively attached to the spindle, is accelerated by the flywheel to synchronism and thus rotates non-positively with the flywheel.
  • the spindle turns out of the spindle nut, so that the tool slide is driven downwards until it hits the lower die with its upper die and deforms the forging material or the workpiece.
  • the pneumatic weight compensation of this screw press ensures that the tool slide and spindle nut are completely weight balanced and the tool slide can be kept 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 air cylinders arranged in the stands of the machine body of the screw press are pressurized and attached to the tool slide via their piston rods.
  • the forming energy required to deform the workpiece is supplied by the flywheel, which loses speed.
  • the forming process ends when a certain pressing or forging force has arisen between the upper and lower die. If this is at the end of the forming process, the clutch slips; namely when the pressing or forging force generates a torque on the coupling via the thread bevel which is greater than the set coupling torque.
  • the spindle accelerates the tool slide, and for the return stroke, this known spindle press supports all the stored energy from the torque storage drive, which is then released and used to accelerate the spindle along with the clutch disc and thus to return the slide to its starting position is exploited.
  • the stored energy of the press stand or machine body is available for the return stroke or for accelerating the spindle and clutch disc along with the block carrier.
  • the machine body is stretched proportionally to the forging force, ie it takes up work during the increase in force, which it releases again when the force drops.
  • the tool slide experiences an upward speed that, for example, 0.1 m / s during cake upsetting (soft upsetting, like descaling workpieces) and with a bounce maximum force, for example, can reach 1.2 m / s.
  • the tool slide thus driven by the uncontrolled reversing drive and by the rebound energy from the body suspension - in the case of the known press also supplemented by the energy stored in the course of the downward movement - requires a braking torque and a braking distance which, based on the energy to be braked from the impact impact with F must be interpreted.
  • Braking torque and braking distance therefore have a significant influence on the design and manufacturing costs of a screw press.
  • the invention has for its object to provide a method and a clutch screw press of the type mentioned with which the operation of the press can be improved, in particular the braking energy required for the tool slide during the return stroke can be reduced.
  • This object is achieved according to the invention by a method in that a weight compensation regulated as a function of the return stroke speed is formed and air displaced by the piston or the tool slide is throttled during the return stroke.
  • the invention makes use of the fact that by preventing the inflow of air and the throttling of the displaced air during lifting movements of the piston of the air cylinder or of the tool slide connected to the piston differ
  • Tool brake significantly reduce the braking energy required. This is particularly the case with a high return stroke or
  • Clutch screw press to reduce the maximum braking energy in the impact with F by up to 50%;
  • a return stroke speed of 1.2 m / s a pressure drop to 20% of the pressure can be achieved, which occurs in the rest position.
  • Braking therefore requires accordingly shorter distances, which makes it possible to keep the slide stroke and thus the overall height of the press correspondingly small, as a result of which considerable weight savings can be achieved.
  • An embodiment of a screw press for performing the method provides that the accumulator pressure chamber communicates with the piston-side cylinder space via at least one non-return and throttle element and the cylinder space above the piston is open.
  • the connection communicating with the cylinder space on the underside of the piston ensures in short-stroke presses that the maximum braking effect is achieved, namely immediately after bottom dead center.
  • An advantageous embodiment of the invention provides that in the case of a speed-compensated weight compensation for a short-stroke press, the accumulator pressure chamber is separated from the piston-side cylinder space by an intermediate wall provided with the at least one non-return and throttle element. Because the amount of air flowing in from the accumulator pressure chamber into the cylinder space on the piston side via the throttle element is reduced, the pressure there is reduced in accordance with the increase in volume or the lack of air.
  • the non-return element or elements, preferably non-return valves, and the or each throttle element, which in the simplest case are designed as bore holes, ensure, for example in the case of the short-stroke version, that when the pistons move downward, the air underneath the piston both the air and the non-return valve and is also pressed via the throttle elements from the piston-side cylinder space into the accumulator pressure chamber.
  • the air from the accumulator pressure chamber into the cylinder space on the piston side can only flow via the throttles or nozzles, ie bore holes.
  • the throttling of the air which consequently flows slowly from the higher-pressure storage pressure chamber into the piston-side cylinder space during the return stroke movement, causes one abrupt, high pressure drop, so that there is less withdrawal of the stored output energy from the weight compensation, whereby the energy to be braked and thus the braking distance is correspondingly smaller.
  • the usable drive energy of the weight compensation for the return stroke of the spindle and tool slide is reduced proportionally - distributed over the stroke - with the average pressure drop.
  • the accumulator pressure chamber be open to the cylinder space underneath the piston and the cylinder space above the piston is closed by a cover having at least one non-return element and a throttle element.
  • the accumulator pressure chamber is towards the piston-side cylinder space and the cylinder space above the piston is open and the displacement of the tool slide is connected to the free atmosphere via at least one non-return and throttling element, the outflowing air is throttled in the displacement above the slide, so that the pressure in this space increases during the upward stroke.
  • a force that reduces the braking energy thus acts on the top of the slide.
  • the throttles or nozzles can be easily provided with a type of flow control.
  • Fig. 1 is a speed-dependent weight balance clutch screw press in front view, shown in partial section;
  • Fig. 2 shows as a detail the air cylinder shown in Fig. 1 in the left half for speed-dependent weight compensation, shown enlarged;
  • FIG. 3 shows in detail an alternative embodiment of a throttle, which can be arranged in the area "X" circled in dash-dot lines in FIG. 2;
  • FIG. 5 a representation corresponding to FIG. 4 of a detail of a clutch screw press with a further embodiment of a speed-dependent weight compensation for long-stroke presses.
  • the screw press 1 shown in the exemplary embodiment according to 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 cooperates with a spindle 5 rotatably mounted in the machine body 2 in an axial bearing fastened to the upper crosshead, such that the tool slide 3, depending on the direction of rotation of the spindle 5 via the spindle nut 4, either for the working stroke in the direction of the lower die 7 arranged in the lower yoke 6 of the machine body 2 or removed therefrom.
  • 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 connected to the spindle 5 in a rotationally fixed manner 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 moved 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, i. 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 has a through bore, not shown, in which a spindle which projects far beyond the coupling disc 12 which is positively fixed on the spindle, projects 5 thus extending torsion spring rod 15 extending upwards.
  • a thickened head piece of the torsion spring rod 15 is rotatably mounted in a bearing bush which is located in a holding bridge 18 which carries a brake unit 16 and on which the hydraulic piston for pressing the clutch disc 12 against the flywheel 8 with a pressure distributor 17 which supplies a pressure medium.
  • the brake unit 16 is composed of a plurality of spring-loaded, pneumatically actuated individual brakes 19 which grip a brake disc 20 with clamping jaws, which is positively connected to the spindle 5 via the torsion spring bar 15.
  • the holding bridge 18 and thus also the braking unit 16 is secured against rotation by means of a torque support 22 fastened on the one hand to the holding bridge 18 and on the other hand to the stage 21.
  • a hydraulic motor 23 which also acts as a pump and which, as is known from the spindle press mentioned at the outset, is designed as a torque accumulator output for the return stroke of the tool slide 3.
  • the hydraulic units 24 required for supplying the hydraulic motor 23 and the rotary distributor 17 are arranged on the stage 21 of the screw press 1 and connected to the rotary distributor 17 or the hydraulic motor 23 via pressure medium hoses 25.
  • the design of the air cylinder 13 of the screw press 1 according to FIG. 1 for speed-dependent weight compensation is shown in detail in FIG. 2.
  • the air cylinder 13 - to which a second one is arranged symmetrically on the other press side - has a piston chamber 26a on the piston side and a cylinder chamber 26b on the piston side, which is followed by a storage pressure chamber 27, which can have any cross section.
  • the pressure chamber 27 is separated from the cylinder spaces 26a, 26b by an intermediate wall 28.
  • the piston rod 14, which can be moved up and down in the direction of the double arrow 29, is guided in seals 30 in the cylinder wall 28 and in a lower chamber wall of the accumulator pressure chamber 27.
  • the piston 31 arranged in the cylinder spaces 26a, 26b is drawn with solid lines in its lower position, ie the bottom dead center uT; the upper position, ie the top dead center oT is shown with dashed lines.
  • a plurality of non-return valves (or non-return flaps) 32 are arranged in the intermediate wall 28 , as shown symbolically, and at least one throttle element or a nozzle 33, as again symbolically indicated.
  • the throttle element 33 can in the simplest case be a bore hole 34 with an internal thread shown in FIG. 3, into which a screw plug 35 can be screwed for regulation.
  • the compressed air can flow in from the accumulator pressure chamber 27 so quickly that no significant pressure difference between Pl and P2 arises.
  • the air compensation cylinders 13 can develop their full effectiveness to compensate for the axially moving parts.
  • due to the throttling of the incoming compressed air ie the speed-dependent regulation of the weight balance, these are reduced so decisively that braking can be achieved despite the maximum impact force and the associated high upward speed.
  • a pressure build-up P occurs, specifically according to FIG. 4 in the piston-top side Cylinder space 126a. This is closed at the top by a cover 36, in which the at least one check valve 132 and the at least one nozzle or throttle 133 are arranged.
  • the piston-side cylinder space 126b of the air cylinder 113 is open to the accumulator pressure chamber 127.
  • the piston-side cylinder space 226a of the air cylinder 213 is open at the top, as in the short-stroke screw press shown in FIG. 1, and the accumulator pressure chamber closes below the piston-side cylinder space 226b
  • Cylinder chamber 226a - as is the case with FIG. 4 - which in the
  • Displacement 237 is throttled over the tool slide 3 flowing air.
  • At least one check valve 232 and at least one nozzle or throttle 233 are arranged in the displacement 237 of the tool slide 3, for example as shown in FIG.
  • Chamber housing 38 through which the displacement 237 with the outer, i.e. free atmosphere is connected.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Control Of Presses (AREA)

Abstract

Cette presse à vis comprend une vis montée rotative (5), un volant (8) qui tourne sans interruption dans un sens de rotation, un accouplement à friction à commande hydraulique dont le disque d'accouplement (12) permet d'établir une liaison par friction entre la vis (5) et le volant (8) pour produire la course de travail, et un entraînement rotatif de redressement (15; 23) pour ramener en arrière le chariot porte-outil (3) animé d'un mouvement alternatif dans la cylindrée du corps de la machine. Le chariot porte-outil (3) est raccordé aux cylindres pneumatiques (13) qui équilibrent son poids et qui comprennent une chambre d'accumulation de pression (27), une chambre de cylindre (26a) du côté supérieur du piston et une chambre de cylindre (26b) du côté inférieur du piston. Afin d'améliorer le mode d'exploitation de cette presse à vis, notamment de réduire l'énergie requise pour freiner le chariot porte-outil (3) après la course de retour, l'équilibrage du poids est réglé en fonction de la vitesse du piston (31) pendant sa course de retour et l'air refoulé pendant la course de retour du piston (31) ou du chariot porte-outil (3) est étranglé.
PCT/DE1996/000316 1995-03-01 1996-02-24 Presse a vis et son procede d'exploitation WO1996026827A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE59601226T DE59601226D1 (de) 1995-03-01 1996-02-24 Spindelpresse und verfahren zum betreiben einer spindelpresse
EP96904709A EP0812255B1 (fr) 1995-03-01 1996-02-24 Presse a vis et son procede d'exploitation

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1995107056 DE19507056A1 (de) 1995-03-01 1995-03-01 Spindelpresse und Verfahren zum Betreiben einer Spindelpresse
DE19507056.9 1995-03-01

Publications (1)

Publication Number Publication Date
WO1996026827A1 true WO1996026827A1 (fr) 1996-09-06

Family

ID=7755301

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1996/000316 WO1996026827A1 (fr) 1995-03-01 1996-02-24 Presse a vis et son procede d'exploitation

Country Status (4)

Country Link
EP (1) EP0812255B1 (fr)
DE (2) DE19507056A1 (fr)
ES (1) ES2128159T3 (fr)
WO (1) WO1996026827A1 (fr)

Cited By (1)

* 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

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101966759B (zh) * 2010-10-12 2014-04-02 上海运良锻压机床有限公司 离合器电动螺旋压力机
CN105057533A (zh) * 2015-08-12 2015-11-18 曹立新 一种组合式锻压设备
CN105081191A (zh) * 2015-08-12 2015-11-25 曹立新 一种推力杆头的无飞边锻造方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH532466A (de) * 1972-03-30 1973-01-15 Hiller & Lutz Dämpfungszylinder für Friktionsspindelpressen
DE2758973B1 (de) * 1977-12-30 1979-03-29 Siempelkamp Gmbh & Co Spindelpresse
DE3613471A1 (de) * 1986-04-22 1987-10-29 Hasenclever Maschf Sms Spindelpresse zur herstellung von feuerfesten formsteinen
DE4208638A1 (de) * 1992-03-18 1993-10-07 Hasenclever Maschf Sms Spindelpresse

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH532466A (de) * 1972-03-30 1973-01-15 Hiller & Lutz Dämpfungszylinder für Friktionsspindelpressen
DE2758973B1 (de) * 1977-12-30 1979-03-29 Siempelkamp Gmbh & Co Spindelpresse
DE3613471A1 (de) * 1986-04-22 1987-10-29 Hasenclever Maschf Sms Spindelpresse zur herstellung von feuerfesten formsteinen
DE4208638A1 (de) * 1992-03-18 1993-10-07 Hasenclever Maschf Sms Spindelpresse

Cited By (2)

* 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

Also Published As

Publication number Publication date
ES2128159T3 (es) 1999-05-01
EP0812255A1 (fr) 1997-12-17
DE59601226D1 (de) 1999-03-11
DE19507056A1 (de) 1996-09-05
EP0812255B1 (fr) 1999-01-27

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