WO2010057559A1 - Dispositif amortisseur destiné à amortir la course de retour d'un piston de travail actionné par le coulisseau d'une presse - Google Patents

Dispositif amortisseur destiné à amortir la course de retour d'un piston de travail actionné par le coulisseau d'une presse Download PDF

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Publication number
WO2010057559A1
WO2010057559A1 PCT/EP2009/007615 EP2009007615W WO2010057559A1 WO 2010057559 A1 WO2010057559 A1 WO 2010057559A1 EP 2009007615 W EP2009007615 W EP 2009007615W WO 2010057559 A1 WO2010057559 A1 WO 2010057559A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure chamber
piston
working
damping device
cylinder
Prior art date
Application number
PCT/EP2009/007615
Other languages
German (de)
English (en)
Inventor
Werner Kuttruf
Original Assignee
Voith Patent 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 Voith Patent Gmbh filed Critical Voith Patent Gmbh
Publication of WO2010057559A1 publication Critical patent/WO2010057559A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
    • F16F9/066—Units characterised by the partition, baffle or like element
    • F16F9/067—Partitions of the piston type, e.g. sliding pistons

Definitions

  • Damping device for damping the return stroke of a convertible from a plunger of a press working piston
  • the invention relates to a damping device for damping the return stroke movement of a ram of a press from a top dead center OT in a bottom dead center UT traversable working piston.
  • damping devices are previously known from the prior art in many ways and are also known as feather pillows or die cushion.
  • the present invention has for its object to provide a damping device mentioned above, on the one hand has a comparatively simple structure and with the appropriate damping is still achievable.
  • the object of the invention is achieved by a
  • the working piston is thus arranged movably in a working cylinder and limits a fillable with hydraulic fluid lower working pressure chamber. Furthermore, a separating piston is provided with which the lower side of the lower working pressure chamber can be closed with respect to a hydraulic pressure chamber. The separating piston delimits, on the lower side facing away from the working piston, a gas pressure space which can be filled with gas pressure.
  • the damping device is designed so that when Moving the working piston from top dead center in the direction of bottom dead center hydraulic fluid is forced from the lower working pressure chamber in the hydraulic pressure chamber, whereby the separating piston moves towards the lower end position and thereby increases the gas pressure in the gas pressure chamber.
  • the arrangement is such that the separating piston is moved after reaching the bottom dead center of the working piston from its lower end position due to the pressure prevailing in the gas pressure chamber gas pressure and the return stroke of the press ram up and thereby closes the lower working pressure chamber path-dependent. Due to the path-dependent closing a damped return stroke of the working piston is achieved.
  • the pressure of the hydraulic fluid and, on the other hand, the gas pressure can always be monitored and controlled.
  • the device comes with comparatively small amounts of hydraulic fluid and comparatively small gas pressure chamber. Overall, a very high reliability.
  • Hydraulic fluid pressure is adjustable.
  • the bias of the damping device for adjusting the gas pressure, in particular, a gas pressure regulating valve which can be connected to a gas pressure source can be provided.
  • the working pressure is always controlled and monitored during operation of the damping device. In the rest position of the device, when no external forces act on the working piston, the working pressure in the gas pressure chamber is preferably greater than the base pressure in the hydraulic pressure chamber. This will ensures that the separating piston is moved to its upper end position.
  • At least one of the lower working pressure chamber leading to the hydraulic pressure chamber throttle opening is provided and that the separating piston in an intermediate position only the lower working pressure chamber and in its end position also closes the at least one throttle opening.
  • the damping takes place in a second stage.
  • the separating piston in the upward movement in the direction of the upper end position the at least one throttle opening travels depending on the path.
  • the separating piston can form a control edge, which reduces the open cross section of the throttle opening in its upward movement and ultimately closes.
  • the working piston defines an upper working pressure space which can be filled with hydraulic fluid, wherein the upper working pressure space is connected to the hydraulic pressure space via passage openings. It is advantageous if the effective piston surface, which limits the upper working pressure chamber, is smaller than the effective piston surface, which limits the lower pressure chamber. This ensures that at constant pressure of the working piston is moved to its top dead center or remains in this top dead center.
  • hydraulic pressure chamber and the gas pressure chamber are in each case closed pressure chambers are formed. Elaborate hydraulic accumulator or gas pressure accumulator account for this.
  • the separating piston comprises a control piston biased by means of a spring element in the direction of the lower working pressure chamber, the outer diameter of which essentially corresponds to the inner diameter of the working cylinder and which engages in the working cylinder for closing the lower working pressure chamber.
  • the diameter of the portion of the control piston, which faces the lower working pressure chamber advantageously corresponds to the diameter of the side of the working piston, which also limits the lower working pressure chamber.
  • the spring element can be designed as a helical spring, which is supported at one end on the separating piston and the other end on the control piston. Due to the provision of the spring element ensures that the control piston with respect to the separating piston assumes a predetermined position.
  • the at least one throttle opening is provided in the region of the lower end of the working cylinder and when the control piston in the upper end position of the separating piston closes the throttle opening.
  • the control piston may provide a control edge, which is heading for the movement of the separating piston or the control piston up to the throttle opening.
  • Hydraulic fluid from the lower working pressure chamber can flow into the upper working pressure chamber, and is moved on further movement of the working piston in the direction of bottom dead center of the control piston with separating piston down, so that the lower working pressure chamber is opened to the hydraulic pressure chamber.
  • the working piston can be moved from its top dead center almost without damping and without much resistance in the direction of bottom dead center.
  • the lower working pressure chamber is opened quickly towards the hydraulic pressure chamber.
  • the working piston is slidably disposed in a cylinder sleeve, the lower end side of the separating piston is closed. This results in not only a robust, but also a comparatively compact damper construction.
  • the cylinder sleeve can have passage openings for the passage of hydraulic fluid in the upper region. Consequently, hydraulic fluid can flow into the upper working pressure chamber via these passage openings when the working piston moves downwards.
  • the throttle opening is preferably arranged in the region of the lower end of the cylinder sleeve.
  • the throttle opening may extend substantially radially through the wall of the cylinder sleeve.
  • not only a throttle opening, but also a plurality of throttle openings may be provided.
  • the outer diameter of the control piston substantially corresponds to the inner diameter of the cylinder sleeve.
  • the separating piston is arranged displaceably in a cylinder housing, in which the cylinder sleeve is arranged.
  • the diameter of the separating piston is preferably greater than the diameter of the cylinder sleeve. Consequently, hydraulic fluid can flow between the inner wall of the cylinder housing and the outer wall of the cylinder sleeve.
  • Cylinder sleeve and cylinder housing are preferably arranged along a common central longitudinal axis, wherein, as already mentioned, the diameter of the control piston is smaller than the diameter of the separating piston.
  • the cylinder housing may be closed in the upper region with a cover element.
  • the cylinder sleeve can preferably be arranged on the cover element. Cover element and cylinder sleeve can form a common preassembled unit.
  • FIG. 1 shows a longitudinal section through an inventive damping device at top dead center
  • FIG. 2 shows the damping device according to FIG. 1 shortly after leaving top dead center
  • FIG. 3 shows the damping device according to FIG. 1 in a middle position
  • FIG. 4 shows the damping device according to FIG. 1 at bottom dead center
  • Figure 5 shows the damping device according to Figure 1 shortly before reaching the top dead center.
  • the damping device shown in the figures comprises a working piston 12, the upper end may be formed, for example, as a floating plate, which is taken down by a plunger of a press.
  • the working piston 12 is movable in a designed as a cylinder sleeve working cylinder 14 between a top dead center shown in Figure 1 and a bottom dead center shown in Figure 4.
  • the working piston 12 limits a filled with hydraulic fluid lower working pressure chamber 16.
  • throttle openings 18 are provided, via which after leaving the top dead center hydraulic fluid can flow from the lower working pressure chamber 16 to a hydraulic pressure chamber 20.
  • the damping device 10 further comprises a separating piston 22, in which a control piston 24 is arranged integrated.
  • the control piston 24 is biased by means of a spring element designed as a helical spring 26 in the direction of lower working pressure chamber 16.
  • the spring element 26 is supported at one end on the control piston 24 and at the other end on the separating piston 22.
  • the separating piston 22 and the control piston 24 closes at the top dead center of the working piston 12, as shown in Figure 1, the working piston 12 remote from the lower end face of the lower working pressure chamber 16.
  • the separating piston 22 together with the control piston 24 defines on the side facing away from the working piston 12 a gas pressure chamber 28th ,
  • the basic working pressure in the gas pressure chamber may be, for example, 30 bar or higher; the base pressure in the hydraulic pressure chamber at, for example, about 20 bar.
  • the guide diameter of the control piston 24 is equal to or slightly smaller than the inner diameter of the lower
  • the separating piston 22 is displaceably mounted in a cylinder housing 30. Between the outer wall of the working cylinder 14 and the inner wall of the cylinder housing 30, an annular gap 32 is present.
  • the central longitudinal axis of the working pressure chamber 16 corresponds to the central longitudinal axis of the cylinder housing 30.
  • passage openings 34 are provided, through which hydraulic fluid from the hydraulic pressure chamber 20 or the annular gap 32 can flow into an upper working pressure chamber 36 delimited by the working piston.
  • the control piston 24 is initially moved downwards in synchronism with the working piston 12. Due to the movement of the control piston 24, the throttle openings 18 are released from the control piston 24, whereby hydraulic fluid from the lower working chamber 16 via the annular gap 32 and the passage openings 34 flow into the upper working chamber 36.
  • the control piston 24 is moved out of the lower working space 16, as shown in FIG.
  • the lower working space 16 is thus opened downwards, wherein from the lower working space 16 hydraulic fluid can flow over a large area.
  • the separating piston 22 moves downward against the force resulting from the pressure in the gas pressure chamber 28 acting on the separating piston 22 until, as shown in FIG. 4, the working piston 16 reaches its bottom dead center.
  • the separating piston 22 is moved upward due to the upwardly pressing press ram and the pressure prevailing in the gas pressure chamber 28 gas pressure, which is greater than the pressure of the hydraulic fluid.
  • the working piston 12 is also moved upward toward top dead center, since the lower working pressure chamber 16 limiting surface of the piston 12 is greater than the upper working pressure chamber 36 limiting surface.
  • the control piston 24 closes, as shown in Figure 5, the lower end face of the lower working pressure chamber 16.
  • the return stroke of the working piston 12 is damped in a first stage.
  • the control piston 24 Upon further movement of the control piston 24 upwards this closes the throttle openings 18 depending on the distance. This results in a further damping of the return stroke of the working piston 12.
  • the upper edge of the control piston 24 serves as a control edge, with which the throttle openings 18 are controlled.
  • the cylinder housing 30 is closed in the upper region by a cover section 38, which may also be designed as a cover element. In the cover portion 38, a guide bore 40 is provided for the working piston 12.
  • the lid portion 38 may be formed integrally with the cylinder sleeve 14, for example. It is also conceivable that the lid portion 38 is formed as a genuine lid member to which the cylinder sleeve 14 is attached.
  • a leakage line 41 is provided, which leads from the upper working pressure chamber 36 toward the guide bore 40.
  • a leakage bore 42 " which corresponds to the leakage line 41 at the top dead center of the working piston, is introduced into the cover section 38.
  • the hydraulic pressure chamber 20 is connected to a hydraulic pressure source via a corresponding line 21 and pressure adjustment means (not shown) Hydraulic fluid can flow into the device 10 via the line 21 and leave the device 10 via the leakage bore 42. In this way, in particular heated hydraulic fluid can be removed from the device and fresh hydraulic fluid can be supplied to the system.
  • the gas pressure chamber 28 may be connected via a corresponding line 29 with a gas pressure control valve, not shown, via which the working pressure in the gas pressure chamber 28 is adjustable.
  • the illustrated in the figure embodiment of the invention has the following particular advantages: To adjust the bias of the damping device 10, only the gas pressure in the gas pressure chamber 28 is changed. A change in the pressure in the hydraulic pressure chamber 20 is not required. To the another provides the working piston 12 when hitting the plunger of the press a comparatively low resistance, so that arise for the press, or the workpiece to be produced, overall advantageous conditions. Furthermore, it is advantageous that a suitable damping of the return stroke movement of the working piston is achieved due to the path-dependent control of the working pressure chamber 16.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

L'invention concerne un dispositif amortisseur destiné à amortir la course de retour d'un piston de travail pouvant être déplacé par un coulisseau d'une presse d'un point mort haut OT à un point mort bas UT. Le piston de travail est monté mobile dans un cylindre de travail et délimite une chambre de travail inférieure pouvant être remplie de liquide hydraulique. Le dispositif comprend un piston séparateur grâce auquel le côté inférieur de la chambre de travail inférieure peut être fermé par rapport à une chambre hydraulique et qui délimite par son côté inférieur, opposé au piston de travail, une chambre remplie de gaz. Lors du mouvement du piston de travail du point mort haut (OT) en direction du point mort bas (UT), du liquide hydraulique est refoulé à partir de la chambre de travail inférieure dans la chambre hydraulique, et le piston séparateur se déplace vers sa fin de course inférieure. Le piston séparateur, après avoir atteint sa fin de course inférieure, se déplace vers le haut et ferme ainsi la chambre de travail inférieure en fonction du déplacement.
PCT/EP2009/007615 2008-11-21 2009-10-24 Dispositif amortisseur destiné à amortir la course de retour d'un piston de travail actionné par le coulisseau d'une presse WO2010057559A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008058526.2 2008-11-21
DE200810058526 DE102008058526B4 (de) 2008-11-21 2008-11-21 Dämpfungseinrichtung zur Dämpfung der Rückhubbewegung eines von einem Stößel einer Presse überführbaren Arbeitskolbens

Publications (1)

Publication Number Publication Date
WO2010057559A1 true WO2010057559A1 (fr) 2010-05-27

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PCT/EP2009/007615 WO2010057559A1 (fr) 2008-11-21 2009-10-24 Dispositif amortisseur destiné à amortir la course de retour d'un piston de travail actionné par le coulisseau d'une presse

Country Status (2)

Country Link
DE (1) DE102008058526B4 (fr)
WO (1) WO2010057559A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108412945A (zh) * 2018-05-15 2018-08-17 贵州大学 弹簧与阻尼器一体式减震器
CN111230529A (zh) * 2020-03-18 2020-06-05 苏州宝优际科技股份有限公司 平衡夹具

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3019009A (en) 1957-08-07 1962-01-30 Reifurth Hans Hydraulic shock absorber
GB1012460A (en) * 1963-02-07 1965-12-08 Jerry Kirsch Constant speed reciprocable hydro-pneumatic retarding device
DE3309042A1 (de) 1983-03-14 1984-09-20 Volkswagenwerk Ag, 3180 Wolfsburg Hydropneumatischer einrohr-teleskopstossdaempfer fuer kraftfahrzeuge
DE3737967C2 (de) 1987-11-07 1995-02-23 Mueller Weingarten Maschf Pneumatische Zieheinrichtung für Pressen mit gesteuerter Stossdämpfung zwischen Druckwange und Druckzylinder der Zieheinrichtung
EP0715091A2 (fr) * 1994-12-03 1996-06-05 FICHTEL & SACHS AG Amortisseur de vibrations réglable
EP1754909A1 (fr) 2005-08-18 2007-02-21 Specialized Bicycle Components, Inc. Amortisseur sensible à la position
DE102006058630A1 (de) 2006-12-13 2008-06-19 Schuler Pressen Gmbh & Co. Kg Elektrohydraulischer Ziehkissenantrieb

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3234520A1 (de) * 1982-09-17 1984-03-22 G. Siempelkamp Gmbh & Co, 4150 Krefeld Spindelpresse
DE3416792A1 (de) * 1984-05-07 1985-11-07 Herion-Werke Kg, 7012 Fellbach Anordnung zur steuerung von ziehkissen
DE3602236A1 (de) * 1986-01-25 1987-07-30 Mueller Weingarten Maschf Pneumatische zieheinrichtung fuer einfach- oder doppeltwirkende pressen
DE3937167A1 (de) * 1989-11-08 1991-05-16 Hemscheidt Maschf Hermann Hydropneumatische kolbenzylindereinheit

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3019009A (en) 1957-08-07 1962-01-30 Reifurth Hans Hydraulic shock absorber
GB1012460A (en) * 1963-02-07 1965-12-08 Jerry Kirsch Constant speed reciprocable hydro-pneumatic retarding device
DE3309042A1 (de) 1983-03-14 1984-09-20 Volkswagenwerk Ag, 3180 Wolfsburg Hydropneumatischer einrohr-teleskopstossdaempfer fuer kraftfahrzeuge
DE3737967C2 (de) 1987-11-07 1995-02-23 Mueller Weingarten Maschf Pneumatische Zieheinrichtung für Pressen mit gesteuerter Stossdämpfung zwischen Druckwange und Druckzylinder der Zieheinrichtung
EP0715091A2 (fr) * 1994-12-03 1996-06-05 FICHTEL & SACHS AG Amortisseur de vibrations réglable
EP1754909A1 (fr) 2005-08-18 2007-02-21 Specialized Bicycle Components, Inc. Amortisseur sensible à la position
DE102006058630A1 (de) 2006-12-13 2008-06-19 Schuler Pressen Gmbh & Co. Kg Elektrohydraulischer Ziehkissenantrieb

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108412945A (zh) * 2018-05-15 2018-08-17 贵州大学 弹簧与阻尼器一体式减震器
CN111230529A (zh) * 2020-03-18 2020-06-05 苏州宝优际科技股份有限公司 平衡夹具

Also Published As

Publication number Publication date
DE102008058526B4 (de) 2011-07-07
DE102008058526A1 (de) 2010-05-27

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