EP0203322B1 - Dispositif pour compacter un matériau de moulage de fonderie à l'aide d'un gaz de compression - Google Patents

Dispositif pour compacter un matériau de moulage de fonderie à l'aide d'un gaz de compression Download PDF

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Publication number
EP0203322B1
EP0203322B1 EP86104663A EP86104663A EP0203322B1 EP 0203322 B1 EP0203322 B1 EP 0203322B1 EP 86104663 A EP86104663 A EP 86104663A EP 86104663 A EP86104663 A EP 86104663A EP 0203322 B1 EP0203322 B1 EP 0203322B1
Authority
EP
European Patent Office
Prior art keywords
pressure
medium cylinder
valve
piston
pressure medium
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
EP86104663A
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German (de)
English (en)
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EP0203322A1 (fr
Inventor
Norbert Damm
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.)
BMD Badische Maschinenfabrik Durlach GmbH
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BMD Badische Maschinenfabrik Durlach GmbH
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Application filed by BMD Badische Maschinenfabrik Durlach GmbH filed Critical BMD Badische Maschinenfabrik Durlach GmbH
Publication of EP0203322A1 publication Critical patent/EP0203322A1/fr
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Publication of EP0203322B1 publication Critical patent/EP0203322B1/fr
Expired legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22C—FOUNDRY MOULDING
    • B22C15/00—Moulding machines characterised by the compacting mechanism; Accessories therefor

Definitions

  • the invention relates to a device for compressing foundry molding material by means of compressed gas, consisting of a pressure vessel forming a pre-pressure chamber for the compressed gas, a molding space arranged underneath from a molding box with a filling frame and a model plate with a model that closes the molding box below, onto which the molding material is compressed is loosely heaped up, and a large-area valve arranged between the pressure vessel and the mold space, the closure member of which is connected to a pressure medium cylinder as a drive, suddenly releases the valve opening in the pressure vessel, moves into the pre-pressure space and can be brought into the closed position by means of the pressure medium cylinder.
  • outlet pressure in the pressure vessel the higher these parameters must be, whereby outlet pressures that are in the range of the pressure of operational compressed air networks are aimed at, in order not to have to do too much construction work for the production of compressed gas on the one hand and for the control of the pressure on the other hand.
  • the device must have a closure member which on the one hand closes the largest possible cross section for overflowing the compressed gas and on the other hand has the lowest possible mass in order to release the cross section as quickly as possible.
  • opening drives which bring the closure member into the open position in a few milliseconds and thus release the cross section. The aforementioned requirements cannot be achieved with conventional valve designs.
  • the invention is therefore based on a known device according to EP-A-0 062 331, in which the closure member opens into the pre-pressure space and is moved from the closed to the open position and vice versa by means of a pressure medium cylinder, so that a dead space within the molding space is avoided can be.
  • EP-A-0 062 331 in which the closure member opens into the pre-pressure space and is moved from the closed to the open position and vice versa by means of a pressure medium cylinder, so that a dead space within the molding space is avoided can be.
  • the invention has for its object to develop the device described above so that a high opening speed for the closure member is achieved with less design effort and a gas pressure that is in the range of the network pressure of conventional compressed air networks.
  • the closure member is thus closed against the at least partially relieved pressure accumulator under the effect of the pressure from the hydraulic high pressure source.
  • the pressure accumulator is set to the working pressure while the high-pressure circuit on the opposite side of the piston is shut off brought, then the high-pressure side is opened, so that the hydraulic fluid runs out of the pressure medium cylinder at a speed> 10 m / s and the piston lifts the closure member abruptly under the high-pressure gas pressure, so that it opens in a few milliseconds against the working pressure in the pressure vessel.
  • this discharge speed must be> 10 m / s, that is to say in a range which is 10 times higher than the return oil speeds customary in hydraulics.
  • This significantly higher flow rate for the displacement volume can be achieved by the intermediate drain tank.
  • the piston speed itself can only have values in the range of approx. 5 m / sec. to reach.
  • Pressure cylinders are described in "Pneumatic controls", Vogelverlag 1973, pp. 70-75 and in “Introduction to pneumatics", published by Festo, Berkheim 1974/75, p. 89, the pistons of which are on one side by a hydraulic high pressure source and on the opposite side with gas pressure.
  • the pistons of which are on one side by a hydraulic high pressure source and on the opposite side with gas pressure.
  • these writings also give no indication of the additional drain tank according to the invention and the unusually high drainage speed of the pressure oil achieved thereby when the valve is opened.
  • the pressure medium cylinder has a small displacement volume of, for. B. 150 to 500 cm 3 .
  • the high-pressure-side outflow is decoupled from other high-pressure circuits and connected to the outflow tank via a line of relatively large cross-section, with the outflow tank expediently having a vent line.
  • the flow resistance for the expiring displacement volume is kept as low as possible
  • the decoupling from the other high-pressure circuit ensures that the amount of pressure medium to be displaced is small.
  • the drain tank gives the possibility to get a quick pressure reduction on the drain side.
  • the pressure accumulator the pressure of which acts on the stroke side of the piston, is in the closed position of the closure member, that is to say in the raised end position of the piston under a gas pressure between 20 and 50 bar, which is directly or indirectly, for. B. acts on the piston via a hydraulic cushion. From approx. 50 bar, the effect of a gas pressure cushion, which in principle is already present even at lower pressures, advantageously increases in the sense of an additional acceleration.
  • the final pressure is between 100 and 300 bar.
  • the ratio of the pressure accumulator volume to the displacement volume of the pressure medium cylinder is at least 5: 1, preferably 10: 1 to 15: 1.
  • the pressure accumulator consists of a cylinder filled with gas and closed by a movable piston, which is connected on the gas pressure side opposite to a hydraulic high pressure source, by means of which the gas pressure accumulator is brought to the final pressure necessary for the opening movement can.
  • the device according to the invention is further characterized by a throttle which becomes effective towards the end of the stroke movement of the piston of the pressure medium cylinder and ensures that the piston and thus the closure member are braked over a short distance.
  • the high pressure source is connected to the pressure medium cylinder via a control slide, a check valve and a ring line, and that the ring line is connected to the discharge tank via a controllable check valve.
  • the ring line has the largest possible cross section in order to allow the pressure medium to drain off quickly.
  • control slide in a first position Connects the pressure medium cylinder to the high pressure source and opens the control line of the controllable check valve so that it closes and in a second position connects the control line to the high pressure source, so that the check valve opens against the pressure in the branch line and connects the pressure medium cylinder to the drain tank.
  • the pressure accumulator is connected to the hydraulic high-pressure source via a control slide and that the control slide connects the pressure accumulator to the hydraulic source in a first position, so that the gas in the pressure accumulator and on the stroke side in the pressure medium cylinder with a simultaneously present high pressure the opposite side of the piston of the pressure medium cylinder is compressed to final pressure and connects in a second position to a drain tank.
  • a pressure vessel 5 - in the illustrated embodiment for receiving compressed air - which is connected via a connection 6 from a pressure accumulator or - at low admission pressure - is fed from the company's compressed air network.
  • the pressure vessel has a plate 7 which is provided with a plurality of openings 8 in a rust-like manner in the area above the molding space.
  • a frame 9 is flanged to the top of the bottom 7, to which in turn an exhaust air line with a valve 10 is connected.
  • the pressure vessel 5 with the frame 9 on the one hand and the model plate 1 with model 2, molding box 3 and filling frame 4 can be moved relative to one another in order to be able to fill the molding space with molding material to just below the bottom 7. Before the compression, these two assemblies are brought together and pressed tightly together at their interface.
  • valve plate 11 is seated on a guide rod 14, which at the same time forms the piston rod of a piston 15 of a pressure medium cylinder 16. This and the controller are described below with reference to FIG. 2:
  • the pressure medium cylinder 16 is arranged in a hydraulic circuit, the pressure source being designated by 17. This is, for example, a hydraulic pump that is fed from a tank 18.
  • the pressure medium passes from the pressure source 17 via a control slide 19 and a check valve 20 into the feed line 21, which opens into the working chamber 22 of the pressure medium cylinder 16 and also leads to a controllable check valve 23.
  • the pressure medium cylinder 16 has a gas pressure chamber 24 below the piston 15, which is connected to a gas pressure accumulator 25.
  • This gas pressure accumulator 25 is divided into a gas pressure chamber 27 and a hydraulic pressure chamber 28 by a movable piston 26.
  • the hydraulic pressure chamber 28 is connected via a control slide 29 to a high-pressure source 30, which is fed from the supply tank 18.
  • the piston 15 of the pressure medium cylinder 16 is extended on the hydraulic side with a piston rod 31 which extends through the working chamber 22.
  • This upper piston rod 31 carries a cylindrical shoulder 32 and a conically tapered shoulder 33 directly on the shoulder of the piston 15, which forms a throttle with the cylindrical constriction 34 during the upward stroke movement of the piston 15.
  • the hydraulic line 21 is connected to a branch line 35 which leads to the controllable check valve 23, the control line 36 of which can be connected to the pressure source 17 via the control slide 19.
  • the pressure medium chamber is connected via lines 21 and 35 to an outlet tank 37 and a vent line 38, which is depressurized.
  • the drain line 39 of the drain tank 37 opens into the hydraulic tank 18th
  • the gas pressure chamber 24 of the pressure medium cylinder 16 with an open connection to the gas pressure accumulator 25 receives a low pressure pre-filling of z. B. 30 to 40 bar.
  • the volume ratio of the gas pressure spaces 24 and 27 is approximately 1:10 to 1:15.
  • the gas pressure prefilling in 24 and 27 is slightly compressed.
  • the model plate 1 with the filled molding box 3 and filling frame 4 is clamped to the frame 9.
  • the gas pressure vessel 5 is filled to operating pressure via the pressure connection 6.
  • the valve 10 is in the closed position. After the shaping device 1, 3, 4 has been clamped to the frame 9, the control slide 29 is brought into the switching position "B". The hydraulic chamber 28 of the gas pressure accumulator 25 is thereby switched to the high pressure source 30. The gas pressure chambers 27 and 24 are compressed to an operating pressure of approx. 200 + 250 bar. At this time, the valve plate 11 is in a highly preloaded state, but is still blocked on the side of the pressure chamber 40.
  • valve plate 11 In order to suddenly release the pressure vessel 5 and to compress the molding material present in the molding box and filling frame, the valve plate 11 must be brought into the open position (left half of FIG. 1). For this purpose, the control slide 19 is switched to the "A" position. There is then the pressure of the pressure source 17 in the control line 36, so that the check valve 23 opens. The pressure medium runs out of the working space 22 under the action of the pressure accumulator 24 via the check valve 23 into the drain tank 37 via the relatively large discharge cross sections of the lines 21, 35. Towards the end of the lowering movement of the piston 15, the discharge cross section between the piston rod 31 and the constriction 34 is reduced by the conical extension 33 on the piston rod 31, so that the piston and thus the valve plate 11 are braked.
  • the pressure medium to be displaced runs out of the working space 22 at a speed of more than 10 m / s, preferably between 20 and 30 m / s.
  • the drain tank 37 can be vented via the line 38 between the work cycles, so that its contents can flow into the system tank 18.
  • valve plate 11 After compression of the molding material, the valve plate 11 is first brought into the closed position as above. The pressure chamber 40 created below the fixed base plate 7 is vented via the valve 10. After the separation of model and compact form, a new work cycle begins.

Claims (13)

1. Dispositif pour compacter du matériau de moulage à l'aide d'un gaz de compression, composé d'un réservoir sous pression pour le gaz de compression constituant une chambre de précompression, d'un volume de moulage disposé en dessous de celle-ci et comprenant un châssis de moulage avec hausse et une plaque- modèle avec modèle qui assure la fermeture inférieure du châssis de moule et sur laquelle le matériau de moulage est versé en vrac avant le compactage, et d'une vanne de grande section placée entre le réservoir sous pression et le volume de moulage, dont l'organe d'obturation est relié à un cylindre compresseur en tant que système d'entraînement, libère brusquement l'ouverture de la vanne dans le réservoir sous pression en se déplaçant vers l'intérieur de la chambre de précompression et peut être amené, au moyen du cylindre compresseur, dans la position de fermeture, caractérisé en ce que le piston (15) du cylindre compresseur (16) constitue, du côté montée, la fermeture mobile d'un accumulateur de pression (24, 25) alimenté en gaz et est raccordé, du côté opposé, à une source de haute pression hydraulique (17); et que l'écoulement (21) du côté haute pression est raccordé, par l'intermédiaire d'un collecteur supplémentaire (37), à un réservoir de fluide hydraulique (18) de telle façon que le fluide hydraulique s'échappe à une vitesse > 10 m/s, avec accélération simultanée du piston (15) et de l'organe d'obturation (11) dans la position d'ouverture soulevée sous l'action de la pression régnant dans l'accumulateur de pression (24, 25).
2. Dispositif selon la revendication 1, caractérisé en ce que le cylindre compresseur (16) présente, du côté haute pression, un faible volume de déplacement, par exemple entre 150 et 500 cm3.
3. Dispositif selon l'une des revendications 1 ou 2, caractérisé en ce que l'écoulement (21) du côté haute pression est découplé du reste du circuit de haute pression par l'intermédiaire d'éléments de commutation (20, 23) et relié au collecteur (37) par l'intermédiaire d'une conduite (21, 35) de grande section.
4. Dispositif selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le collecteur (37) comporte une conduite de purge (38).
5. Dispositif selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la pression de la source de haute pression (17) se situe entre 100 et 300 bars.
6. Dispositif selon l'une quelconque des revendications 1 à 5, caractérisé en ce que, dans la position de fermeture de l'organe d'obturation (11), l'accumulateur de pression (24, 25) est soumis à une pression d'alimentation comprise entre 20 et 50 bars.
7. Dispositif selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le rapport entre le volume de l'accumulateur de pression et le volume de déplacement du cylindre compresseur (16) est d'au moins 5 : 1, de préférence de 10 : 1 à 15 : 1.
8. Dispositif selon l'une quelconque des revendications 1 à 7, caractérisé en ce que l'accumulateur de pression (27) est constitué par un cylindre (25) rempli de gaz et fermé par un piston mobile (26), et raccordé, du côté opposé à l'application de la pression de gaz, à la source de haute pression hydraulique (30).
9. Dispositif selon l'une quelconque des revendications 1 à 8, caractérisé en ce qu'il comporte un dispositif d'étranglement (33, 34) qui devient efficace vers la fin du mouvement de montée du piston (15) du cylindre compresseur (16).
10. Dispositif selon la revendication 9, caractérisé en ce que le piston (15) comprend une tige de piston (31) dépassant dans le volume du cylindre (22) du côté haute pression, laquelle tige de piston présente à son tour une section à évasement conique (33) qui coopère avec un rétrécissement (34) dans ledit volume du cylindre.
11. Dispositif selon l'une quelconque des revendications 1 à 10, caractérisé en ce que la source de haute pression (17) communique, par l'intermédiaire d'une vanne-pilote (19), d'un clapet de retenue (20) et d'une conduite annulaire (21), avec le cylindre compresseur (16) et que la conduite annulaire (21) est raccordée au collecteur (37) par l'intermédiaire d'un clapet de retenue (23) pouvant être commandé dans le sens de l'ouverture.
12. Dispositif selon la revendication 11, caractérisé en ce que la vanne-pilote (19) établit, dans une première position, la liaison entre le cylindre compresseur (16) et la source de haute pression (17) et décharge la conduite de pilotage (36) du clapet de retenue (23) pouvant être commandé dans le sens de l'ouverture, et relie, dans une seconde position, la conduite de pilotage (36) à la source de haute pression (17) de sorte que le clapet de retenue (23) s'ouvre contre la pression dans la conduite circulaire (21) et relie le cylindre compresseur (16) au collecteur (37).
13. Dispositif selon l'une quelconque des revendications 1 à 12, caractérisé en ce que l'accumulateur de pression (27) est raccordé à la source de haute pression hydraulique (30) par l'intermédiaire d'une vanne-pilote (29) et que la vanne-pilote (29) établit, dans une première position, la liaison entre l'accumulateur de pression (27) et la source de haute pression (30) de sorte que le gaz dans l'accumulateur de pression et, du côté montée, dans le cylindre compresseur (16) est comprimé à la pression finale, avec application simultanée de la haute pression au côté opposé du piston (15) du cylindre compresseur (16), et relie, dans une seconde position, ledit accumulateur de pression à un écoulement.
EP86104663A 1985-05-25 1986-04-05 Dispositif pour compacter un matériau de moulage de fonderie à l'aide d'un gaz de compression Expired EP0203322B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853518980 DE3518980A1 (de) 1985-05-25 1985-05-25 Vorrichtung zum verdichten von giesserei-formstoff mittels druckgas
DE3518980 1985-05-25

Publications (2)

Publication Number Publication Date
EP0203322A1 EP0203322A1 (fr) 1986-12-03
EP0203322B1 true EP0203322B1 (fr) 1988-11-23

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP86104663A Expired EP0203322B1 (fr) 1985-05-25 1986-04-05 Dispositif pour compacter un matériau de moulage de fonderie à l'aide d'un gaz de compression

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Country Link
US (1) US4846253A (fr)
EP (1) EP0203322B1 (fr)
JP (1) JP2553044B2 (fr)
DD (1) DD247161A5 (fr)
DE (2) DE3518980A1 (fr)
DK (1) DK241886A (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3836876C2 (de) * 1988-10-29 1994-06-09 Badische Maschf Gmbh Verfahren und Vorrichtung zum Verdichten von Gießerei-Formstoff
ES2012702A6 (es) * 1989-04-06 1990-04-01 Erana Agustin Arana Mejoras en maquinas de moldeo de cajas de arena por impacto de aire.
CH686412A5 (de) * 1992-03-10 1996-03-29 Fischer Georg Giessereianlagen Verfahren zum Verdichten von Formsand fuer Giessformen.

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU425719A1 (fr) * 1972-07-17 1974-04-30 институт машиностроени
SU521993A1 (ru) * 1974-04-02 1976-07-25 Краматорский Научно-Исследовательский И Проектно-Технологический Институт Машиностроения Импульсна головка
DE2727297C3 (de) * 1976-06-25 1980-07-10 Georg Fischer Ag, Schaffhausen (Schweiz) Verfahren und Einrichtung zum Herstellen von Gießereisandformen
SU793696A1 (ru) * 1979-03-19 1981-01-07 Краматорский Научно-Исследовательскийи Проектно-Технологический Институтмашиностроения Импульсна головка
WO1982003348A1 (fr) * 1981-04-02 1982-10-14 Koebel Alfons Procede et dispositif de compactage pneumatique de sable de moulage
EP0170765B1 (fr) * 1981-12-28 1988-08-31 BMD Badische Maschinenfabrik Durlach GmbH Dispositif pour comprimer du matériel de moulage pour fonderies
DE3243951A1 (de) * 1981-12-28 1983-07-07 BMD Badische Maschinenfabrik Durlach GmbH, 7500 Karlsruhe Verfahren und vorrichtung zum verdichten von giesserei-formstoff
CH657790A5 (de) * 1982-10-27 1986-09-30 Fischer Ag Georg Vorrichtung zum verdichten von koernigen formstoffen.
DE3321622A1 (de) * 1983-06-15 1984-12-20 BMD Badische Maschinenfabrik Durlach GmbH, 7500 Karlsruhe Vorrichtung zum verdichten von giesserei-formstoff
DE3321955A1 (de) * 1983-06-18 1984-12-20 BMD Badische Maschinenfabrik Durlach GmbH, 7500 Karlsruhe Vorrichtung zum verdichten von giesserei-formstoff mittels druckgas

Also Published As

Publication number Publication date
JP2553044B2 (ja) 1996-11-13
DE3661242D1 (en) 1988-12-29
EP0203322A1 (fr) 1986-12-03
DD247161A5 (de) 1987-07-01
US4846253A (en) 1989-07-11
DK241886A (da) 1986-11-26
DK241886D0 (da) 1986-05-23
DE3518980A1 (de) 1986-11-27
DE3518980C2 (fr) 1993-01-21
JPS61269959A (ja) 1986-11-29

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