EP0114170B1 - Protecteur de surcharge pour presses - Google Patents

Protecteur de surcharge pour presses Download PDF

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Publication number
EP0114170B1
EP0114170B1 EP83100561A EP83100561A EP0114170B1 EP 0114170 B1 EP0114170 B1 EP 0114170B1 EP 83100561 A EP83100561 A EP 83100561A EP 83100561 A EP83100561 A EP 83100561A EP 0114170 B1 EP0114170 B1 EP 0114170B1
Authority
EP
European Patent Office
Prior art keywords
pressure
overload
summation
piston
pressure balance
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
Application number
EP83100561A
Other languages
German (de)
English (en)
Other versions
EP0114170A1 (fr
Inventor
Werner Rupp
Johannes Koch
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.)
L Schuler GmbH
Original Assignee
L Schuler 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 L Schuler GmbH filed Critical L Schuler GmbH
Priority to EP83100561A priority Critical patent/EP0114170B1/fr
Priority to DE8383100561T priority patent/DE3367556D1/de
Priority to BR8400228A priority patent/BR8400228A/pt
Priority to JP59007423A priority patent/JPS59137199A/ja
Priority to US06/572,305 priority patent/US4492154A/en
Priority to ES529029A priority patent/ES529029A0/es
Publication of EP0114170A1 publication Critical patent/EP0114170A1/fr
Application granted granted Critical
Publication of EP0114170B1 publication Critical patent/EP0114170B1/fr
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/28—Arrangements for preventing distortion of, or damage to, presses or parts thereof
    • B30B15/281—Arrangements for preventing distortion of, or damage to, presses or parts thereof overload limiting devices
    • B30B15/284—Arrangements for preventing distortion of, or damage to, presses or parts thereof overload limiting devices releasing fluid from a fluid chamber subjected to overload pressure

Definitions

  • the invention relates to an overload protection in step, transfer and the like. Presses of the type specified in the preamble of claim 1.
  • the ram nominal force to be protected by the total pressure compensator is selected to be smaller than the sum of the maximum forces of the overload stages, so that the press does not have to be dimensioned unnecessarily.
  • the sum of the tappet forces does not rule out that the working stages closer to a drive level are loaded to a maximum and the other working stages only weakly and vice versa. This requires an unnecessarily large dimensioning of the connecting rods, drive parts and stands.
  • DE-C-1288431 describes a measure for the overall protection of a press or step press in the event of an overload.
  • the press drive acts on various work stages, each of which is secured with its own overload protection, which switches off the press drive in the work stage if the limit load is exceeded.
  • the overload protection devices of the individual work stages are connected to a total overload protection device, which is therefore permanently loaded by all individual overload protection devices and whose switch-off value is set to a value that is less than the sum of the overload values of the individual overload protection devices. This device allows a high load on the drive levels and requires excessive dimensioning of the drive components.
  • DE-C-20 04 980 shows an essentially the same device for overall protection of a press or step press, each with a total overload protection for the work stages, one drive level of the ram.
  • the overload protection devices assigned to the working stages each have a pressure chamber that can be compressed under the working pressure in the working stage.
  • Each pressure chamber is in flow connection with a pressure chamber of the overload protection of the drive level, to which the work stage is assigned.
  • the switch-off value is exceeded, the pressure in the pressure chambers of the overload safety devices and the total overload safety devices is relieved via a common lockable drain line.
  • the distances of the individual work stages to the connecting rods are not taken into account and the device does not adequately protect the drive levels, as are the work stages further away from a drive level, which are not included in the associated overall overload protection, according to the Lever Act Contribute to the power at this level.
  • the connecting rods 1 engage in the drive levels 2 and 3 on the tappet 4.
  • the work stages are numbered 6, 7, 8, 9 in Fig. 1 and 10 in Fig. 2, and 83 in Fig. 3 for further arrangements.
  • Overload pressure compensators 11, 12, 13, 14 and 86 are used in the power flow between each working stage and the tappet.
  • the overload pressure compensators each have a pressure chamber 21, 22, 23, 24 and 84 and pistons 36, 37, 38, 39 and 85 immersed in them.
  • the pressure chambers 21 to 24 and 84 are with pressure chambers 26, 27, 28, .29 of a first total pressure compensator 16 and 81 and with pressure chambers 31, 32, 33, 34 one second total pressure compensator 17 or 82 in flow connection.
  • the pressure in the pressure chambers is preset, specifically from the pump unit 47 via the pressure switch 49 and the pressure limiting controller 48, the pressure supply line 52, check valves 53 and pressure lines 91 to 94 assigned to the individual systems.
  • the pretensioning pressure in the pressure chambers can be set.
  • Three pressure chambers are connected in parallel.
  • the pressure chamber 21 of the left overload pressure compensator 11, the pressure chamber 26 of the total pressure compensator 16 and the pressure chamber 31 of the total pressure compensator 17 form a pressure system.
  • the total pressure compensators 16 and 17 each have a pressure chamber 18 or 19, in which a pre-pressure is also set, which is generated by a pump unit 57 and is monitored or limited by the pressure switch 58 and the pressure limiting controller 59.
  • the pressure relief controls 54 and 61 relieve the pressure on the pressure areas, specifically whenever the pressure in an overload pressure compensator or in a total pressure compensator has exceeded a specified ratio to the preload pressure. This immediately stops the flow of power in the affected work stages.
  • the check valves 51 and 53 prevent the other pressure chambers from being relieved when one of the overload pressure compensators responds.
  • Each pressure compensator is assigned sensors 56, 62 which stop the press when the pressure compensator is triggered.
  • FIG. 2 shows with the work stage 10 an area lying outside the drive level (here 3), to be queried for tool and press ram or connecting rod safety, with an overload pressure compensator 14 which is offset by the distance 46 from the drive level 3.
  • the pressure chamber 29 communicating with the pressure chamber 24 acts with the piston 70 opposite to the other pressure chambers 26, 27, 28 of this total pressure compensator 81.
  • the pressure chamber 34, which is also connected in parallel, with the associated piston 74 of the total pressure compensator 82 has the same effect as the other pistons / pressure chambers 31, 32 , 33/71, 72, 73 of this total pressure compensator.
  • the calculation of the cross-sectional areas also of the piston 70 of the pressure balance 81 results as shown previously. Is the distance between the working levels 8 and.
  • the piston cross sections of the pistons 70 and 68 are of the same size.
  • their forces acting on the balance pressure compensator 81 do not cancel each other out because the pressures in the working stages do not have to be the same size during the press load.
  • a force thus moves the piston 20 into the pressure chamber 18, which is reduced by the cross section of the piston 70 multiplied by the pressure in the pressure chamber 29, for the total pressure compensator 81.
  • the piston cross-sectional calculation of the associated piston 74 of the total pressure compensator 82 is also calculated here from the distance 46 of the working stage 10 from the drive plane 2 and the cross section of the piston 39 of the overload pressure compensator 14.
  • the work stages 6 to 10 of the embodiments described above are connected, for example, to the pressure lines 91, 93, 94 and possibly further pressure lines Total pressure compensator 88 connected.
  • the sum pressure compensator can also be designed like the sum pressure compensators 16 or 81 of FIGS. 1 and 2, or replace them or the sum pressure compensators 17 and 82, specifically when the working stage 83 is located in the middle of the drive level 2.
  • the admission pressure in the pressure compensator 86 is set via the line 87 coming from the pump assembly 47 as well as the check valves and, as is also possible in the previous examples, by means of pressure limiting monitors.
  • the admission pressure is at the same time on the line 92, which leads into a section 64 which is shut off by the plungers 66 and 67 or the plungers 67 and 68 by the outlet line 63 leading to the outside.
  • the section 64 is always released when the total forces acting on the piston 89 via the plungers 66, 67 and 68 are greater than the force resulting from the pressure in the pressure chamber 90 with the projected area of the piston 89.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Presses (AREA)

Claims (4)

1. Dispositif de protection contre les surcharges pour presses à étages, presses-transfert ou presses analogues, comprenant des coulisseaux (4) commandés par des bielles (1) dans un premier plan de commande (2) et dans un second plan de commande (3) éloigné du premier, et agissant sur des postes de travail (6, 7, 8, 9, 10, 83), avec coordination à chaque poste de travail d'au moins une balance de pression de surcharge (11, 12, 13, 14, 86), présentant chacune une chambre de pression (21, 22, 23, 24, 84) raccordée à une chambre de pression (26, 27, 28, 29) d'une première balance de pression totalisatrice (16, 81, 88) ou à une chambre de pression (31, 32, 33, 34) d'une deuxième balance de pression totalisatrice (17, 82), la valeur de la protection globale contre les surcharges de chaque balance de pression totalisatrice (16, 17, 81,82,88) étant ajustée plus basse que la somme des valeurs des protections individuelles contre les surcharges des balances de pression de surcharge (11, 12, 13, 14, 86), caractérisé en ce que la première balance de pression totalisatrice (16, 81, 82) contient des chambres de pression (26, 27, 28, 29) dont le nombre correspond aux postes de travail (6, 7, 8, 9, 10, 83) et la deuxième balance de pression totalisatrice (17, 82) contient des chambres de pression (31, 32, 33, 34) dont le nombre correspond aux postes de travail (6, 7, 8, 9, 10, 83), que chaque chambre (21, 22, 23, 24, 84) de chaque balance de pression de surcharge (11, 12, 13, 14, 86) est raccordée à une chambre de pression (26, 27, 28, 29) de la première balance de pression totalisatrice (16, 81, 88) et à une chambre de pression (31, 32, 33, 34) de la deuxième balance de pression totalisatrice (17, 82) et que la section droite de chacun des pistons (66, 67, 68, 69, 70) chargés dans la première balance de pression totalisatrice (16, 81, 88) est proportionnelle au produit de la distance (41, 42, 43, 44, 46) du poste de travail raccordé (6, 7, 8, 9,10, 83) au second plan de commande (3) et la section de piston de la balance de pression de surcharge (21, 22, 23, 24, 84), et la section droite de chacun des pistons (71, 72, 73, 74) chargés dans la deuxième balance de pression totalisatrice (17, 82) est proportionnelle au produit de la distance (76, 77, 78, 79) du poste de travail raccordé (6, 7, 8, 9, 10, 83) au premier plan de commande (2) et de la section de piston de la balance de pression de surcharge (21, 22, 23, 24, 84).
2. Dispositif selon la revendication 1, comprenant au moins un poste de travail (10) situé à l'extérieur d'un des plans de commande (2, 3) d'un coulisseau (4) mais qui est également sollicité par ce coulisseau, caractérisé en ce que le piston (70) de la (première) balance de pression totalisatrice (81), raccordé à la balance de pression de surcharge (14) du poste de travail (10), dont le calcul de l'aire de section se rapporte au plan de commande (en l'occurrence le plan de commande 3) situé le plus près du poste de travail (10), est disposé pour agir en sens contraire aux autres pistons (66, 67, 68) chargés par les autres balances de pression de surcharge (6, 7, 8).
3. Dispositif selon la revendication 1, comprenant au moins un poste de travail (83) qui est au moins à peu près centré sur un plan de commande (3), caractérisé en ce que la canalisation de pression (87) sortant de la chambre de pression (84) de la balance de pression de surcharge (86) coordonnée au poste de travail (83) est raccordée, outre avec les moyens (47) d'établissement de la pression de départ dans la chambre de pression (84), avec un dispositif de détente (54) qui, au dépassement d'une pression limite, provoque la décharge en pression de la canalisation (87) et de la chambre de pression (84).
4. Dispositif selon la revendication 3, comprenant une canalisation de décharge (63) pour le fluide de pression qui, en cas d'arrêt de la presse, est libérée en même temps que les canalisations de pression (91, 93, 94) par le mouvement du piston totalisateur (89), caractérisé en ce que la canalisation de pression (87) sortant de la chambre de pression (84) de la balance de pression de surcharge (86) est raccordée à un tronçon (64) de la canalisation de décharge (63) susceptible d'être isolé par deux pistons voisins (67, 68).
EP83100561A 1983-01-22 1983-01-22 Protecteur de surcharge pour presses Expired EP0114170B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP83100561A EP0114170B1 (fr) 1983-01-22 1983-01-22 Protecteur de surcharge pour presses
DE8383100561T DE3367556D1 (en) 1983-01-22 1983-01-22 Overload protection device in presses
BR8400228A BR8400228A (pt) 1983-01-22 1984-01-19 Seguranca contra sobrecarga em prensas
JP59007423A JPS59137199A (ja) 1983-01-22 1984-01-20 プレスにおける過負荷安全装置
US06/572,305 US4492154A (en) 1983-01-22 1984-01-20 Overload protection in presses
ES529029A ES529029A0 (es) 1983-01-22 1984-01-20 Dispositivo de seguro contra sobrecargas en prensas de multiples etapas, de transferencia y similares

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP83100561A EP0114170B1 (fr) 1983-01-22 1983-01-22 Protecteur de surcharge pour presses

Publications (2)

Publication Number Publication Date
EP0114170A1 EP0114170A1 (fr) 1984-08-01
EP0114170B1 true EP0114170B1 (fr) 1986-11-12

Family

ID=8190252

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83100561A Expired EP0114170B1 (fr) 1983-01-22 1983-01-22 Protecteur de surcharge pour presses

Country Status (6)

Country Link
US (1) US4492154A (fr)
EP (1) EP0114170B1 (fr)
JP (1) JPS59137199A (fr)
BR (1) BR8400228A (fr)
DE (1) DE3367556D1 (fr)
ES (1) ES529029A0 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013210807A1 (de) 2013-06-10 2014-12-11 Gräbener Pressensysteme GmbH & Co. KG Überlast-Löseeinrichtung in einer Servopresse

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62151300A (ja) * 1985-12-26 1987-07-06 Komatsu Ltd プレス機械の過荷重保護装置
DE4036470A1 (de) * 1990-11-15 1992-05-21 Mueller Weingarten Maschf Ueberlastsicherung fuer eine mechanisch angetriebene presse
DE4110761C1 (fr) * 1991-04-03 1992-04-02 Harald Perchtoldsdorf At Engel
CA2154875A1 (fr) * 1993-02-02 1994-08-18 Karl Schlecht Methode de refoulement d'une substance epaisse contenant des metaux dechiquetes ou des materiaux solides du meme genre
US5638748A (en) * 1996-01-25 1997-06-17 The Minster Machine Company Hydraulic overload proportional valving system for a mechanical press
DE19847890C1 (de) * 1998-10-16 2000-02-10 Siempelkamp Gmbh & Co Taktpresse, insbesondere Ein- oder Mehretagenpresse
JP6554217B2 (ja) * 2018-08-09 2019-07-31 コマツ産機株式会社 制御システム、プレス機械、及びプレス機械の制御方法

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1288431B (de) * 1965-12-10 1969-01-30 Weingarten Ag Maschf Gesamt-UEberlastsicherung einer Presse
FR2075436A5 (fr) * 1970-02-04 1971-10-08 Weingarten Ag Maschf
DE2828315A1 (de) * 1978-06-28 1980-01-10 Paul Chrubasik Abstuetzeinrichtung fuer einen pressentisch

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013210807A1 (de) 2013-06-10 2014-12-11 Gräbener Pressensysteme GmbH & Co. KG Überlast-Löseeinrichtung in einer Servopresse
EP2813357A1 (fr) 2013-06-10 2014-12-17 Gräbener Pressensysteme GmbH & Co. KG Déclencheur de surcharge dans une servopresse

Also Published As

Publication number Publication date
ES8501670A1 (es) 1984-12-01
US4492154A (en) 1985-01-08
DE3367556D1 (en) 1987-01-02
EP0114170A1 (fr) 1984-08-01
JPS59137199A (ja) 1984-08-07
BR8400228A (pt) 1984-08-28
ES529029A0 (es) 1984-12-01

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