EP0676278A1 - Dispositif de réglage de la course pour presses ou poinçonneuses - Google Patents

Dispositif de réglage de la course pour presses ou poinçonneuses Download PDF

Info

Publication number: EP0676278A1
Authority: EP; European Patent Office
Prior art keywords: sliding sleeve; eccentric; eccentric shaft; section; eccentric bushing
Prior art date: 1994-04-08
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

EP95104720A

Other languages

German (de)

English (en)

Other versions

EP0676278B1 (fr

Inventor

Herbert Bilz

Jürgen Hennig

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.)

Otto Kaiser & Co KG GmbH

Original Assignee

Otto Kaiser & Co KG 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.)

1994-04-08

Filing date

1995-03-30

Publication date

1995-10-11

1995-03-30 Application filed by Otto Kaiser & Co KG GmbH filed Critical Otto Kaiser & Co KG GmbH

1995-10-11 Publication of EP0676278A1 publication Critical patent/EP0676278A1/fr

1999-03-03 Application granted granted Critical

1999-03-03 Publication of EP0676278B1 publication Critical patent/EP0676278B1/fr

2015-03-30 Anticipated expiration legal-status Critical

Status Expired - Lifetime legal-status Critical Current

Links

Images

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
- B30B1/26—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 cams, eccentrics, or cranks
- B30B1/263—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 cams, eccentrics, or cranks work stroke adjustment means

Definitions

the invention relates to a stroke adjustment device for eccentric presses or punches, with an eccentric shaft which is rotatably mounted in at least one bearing and has at least one eccentric pin on which an eccentric bush is mounted, with at least one connecting rod which is mounted on the eccentric bush, with a first external toothing section on the eccentric shaft, with a second external toothing section on the eccentric bushing, and with a sliding sleeve which, in an engaged position, connects the eccentric shaft and the eccentric bushing in a rotationally fixed manner and is detachably connected to one another by axial displacement of the sliding sleeve, the sliding sleeve always being non-rotatably connected to the eccentric bushing communicates.
Such a stroke adjustment device is known for example from DE-A-3112382.
the sliding sleeve is provided with internal toothing sections spaced apart from one another in the axial direction of the sliding sleeve, between which there is a toothing-free section.
one of the internal toothing sections engages with the first external toothing section and the other internal toothing section engages with the second external toothing section.
the eccentric bushing and the eccentric shaft are connected to one another in a rotationally fixed manner.
the sliding sleeve is axially displaced, the inner toothing section engaging with the first outer toothing section disengaging and the toothless section sliding over the first outer toothing section.
a recess made on the sliding sleeve comes with a, on a frame of Eccentric press attached pins in engagement, whereby the sliding sleeve is arranged against rotation with respect to the frame.
the lifting height of the eccentric press or punch can then be adjusted by turning the eccentric shaft relative to the eccentric bushing.
the object of the invention is therefore to design a stroke adjustment device of the type mentioned at the outset to be as space-saving as possible in order to achieve the least possible deflection of the eccentric shaft.
the stroke adjustment device is to be simplified and, in practice, designed to be less susceptible to faults.
the sliding sleeve has a coherent internal toothing section which, in the coupled position of the sliding sleeve, engages in sections with both the first external toothing section and the second external toothing section, and the eccentric shaft and the eccentric bushing are thereby connected to one another in a rotationally fixed manner, and that the sliding sleeve can be moved by the axial displacement into a decoupled position, in which the inner toothed portion of the sliding sleeve is disengaged from the outer toothed portion of the eccentric shaft and the eccentric shaft can thereby be rotated relative to the eccentric bushing, a locking device arranged on the sliding sleeve having a connecting rod on the connecting rod attached receptacle is connected in such a way that the connecting rod is rotationally fixed relative to the eccentric bushing, and that the second external toothing section of the eccentric bushing is in constant engagement with the internal toothing section of the sliding sleeve.
the first external toothing section on a component that is connected to the eccentric shaft in a rotationally fixed manner.
the locking device is designed as a projection
the receptacle is designed as a substantially radially extending to the eccentric shaft, elongated recess in which in the disengaged position of the sliding sleeve, the projection is received such that the projection when adjusting the eccentric shaft relative to Eccentric bushing slides in the recess, you get a simple one and inexpensive device with which in the disengaged position of the sliding sleeve, the eccentric sleeve and the connecting rod can be connected to one another in a rotationally fixed manner.
the sliding sleeve has a guide section and the component has a guide area, the sliding sleeve with its guide section for transferring the sliding sleeve from its engaged position to its disengaged position being axially displaceable and rotatable on the guide area is.
the guide section of the sliding sleeve is designed as an annular piston with at least one annular pressure surface running essentially perpendicular to the axial extension of the sliding sleeve and the guide region of the component is at least one essentially parallel to the pressure surface extending annular support surface, and that the pressure surface, the support surface, the guide surface and the guide region form a substantially toroidal pressure chamber, which can be enlarged and reduced in size by moving the sliding sleeve, and that connections are provided which are used for supplying and removing a medium in open the toroidal pressure chamber.
connections open out of the guide area and the medium can be fed to the toroidal pressure chamber via channels in the eccentric shaft.
Hydraulic liquids especially hydraulic oil, are particularly suitable as a medium.
Fig. 1 shows a schematic representation of an eccentric press 1 adjustable in lifting height with a frame 2, a press table 3, an eccentric shaft 4, a sliding sleeve 5, an eccentric bush 6 only partially visible in FIG. 1, and a rotatably mounted on the eccentric bush 6 Connecting rod 7 and a press ram 8 which is articulated on the connecting rod 7.
the eccentric shaft 4 is rotatably supported in bearings 9 and 10 of the frame 2.
the eccentric bush 6 is rotatably mounted on an eccentric pin 11 of the eccentric shaft 4.
the eccentric shaft 4 has a section 12 on which an annular Component 13 is rotatably attached to the eccentric pin 11.
the section 12 can be designed as a cylindrical or conical seat for the component 13.
the torque transmission between section 12 and component 13 takes place by means of a feather key, not shown, section 12 preferably being designed as a cylindrical seat.
the sliding sleeve 5 has a coherent internal toothing section 16. In an engaged position, this internal toothing section 16 is in sections engaged with both the first external toothing section 14 and the second external toothing section 15, as a result of which the eccentric bushing 6 is arranged in a rotationally fixed manner with respect to the eccentric shaft 4.
the sliding sleeve 5 is axially displaceable and can be moved by shifting from the engaged position into a decoupled position, in which the internal toothing section 16 of the sliding sleeve 5 is disengaged from the first external toothing section 14 of the eccentric shaft 4 and thereby the eccentric shaft 4 can be rotated relative to the eccentric bushing 6 is, as can be seen from Fig. 3.
the sliding sleeve 5 is transferred from its engaged position to its uncoupled position, the sliding sleeve 5 moves to the eccentric bushing 6.
FIG. 3 When the sliding sleeve 5 is transferred from its engaged position to its uncoupled position, the sliding sleeve 5 moves to the eccentric bushing
the sliding sleeve 5 has a guide section 19 with which the sliding sleeve 5 is displaceably guided on a guide region 20 of the component 13.
the sliding sleeve 5 is designed to be axially rotatable and displaceable relative to the guide region 20 or the component 13 as an annular piston 21 with an annular pressure surface 22 which extends essentially radially to the eccentric shaft 4.
the eccentric shaft 4 and thus the stroke movement are stopped.
the sliding sleeve 5 can be transferred from its engaged position to its uncoupled position by introducing hydraulic oil into the pressure chamber 24 via the channels 26 and the connections 25, the hydraulic fluid entering displacing the sliding sleeve in the direction of the eccentric bush 6.
the first external toothing section 14 and the internal toothing section 16 disengage, as a result of which the eccentric bushing 6 can be rotated relative to the eccentric pin 11.
the internal gear section 16 remains in constant engagement with the second external gear section 15 of the eccentric bushing 6.
the projection 17 engages in the recess 18 of the connecting rod 7.
the connecting rod 7 is fixed against rotation relative to the eccentric bushing 6. If the sliding sleeve 5 is now in its disengaged position, the eccentric shaft 4 can be rotated, the eccentric pin 11 moving relative to the eccentric bushing 6, and the lifting height can thereby be adjusted. Since a relative movement between the connecting rod 7 and the sliding sleeve 5 necessarily takes place when the lifting height is set, the depression 18 is designed in such a way that the projection 17 is displaceable therein. As soon as the desired lifting height is reached, the rotary movement of the eccentric shaft 4 is stopped.
the sliding sleeve 5 can be transferred back from its uncoupled position to its engaged position, the projection 17 and the recess 18 disengaging and the internal toothing section 16 again engaging with the first external toothing section 14.
the hydraulic oil emerges from the pressure chamber 24 via the connections 25 and the channels 26.
for. B. provide springs that bias the sliding sleeve 5 in its engaged position, or provide a second pressure chamber with connections and channels similar to the pressure chamber 24, which is arranged parallel to the pressure chamber 24, the second pressure chamber decreasing as the pressure chamber 24 increases and vice versa.
the solution described above is characterized by the fact that it can be made extremely compact, since no additional tooth-free section on the sliding sleeve 5 is required and the deflection of the eccentric shaft 4 can thus be reduced due to the compact design.
the simplified design enables a cost reduction in the manufacture of the sliding sleeve 5.

Landscapes

Engineering & Computer Science (AREA)
Mechanical Engineering (AREA)
Transmission Devices (AREA)
Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
Press Drives And Press Lines (AREA)
Chairs For Special Purposes, Such As Reclining Chairs (AREA)

EP95104720A 1994-04-08 1995-03-30 Dispositif de réglage de la course pour presses ou poinçonneuses Expired - Lifetime EP0676278B1 (fr)

Applications Claiming Priority (2)

Application Number	Priority Date	Filing Date	Title
DE4412198A DE4412198C1 (de)	1994-04-08	1994-04-08	Hubverstelleinrichtung für Exzenterpressen oder Stanzen
DE4412198		1994-04-08

Publications (2)

Publication Number	Publication Date
EP0676278A1 true EP0676278A1 (fr)	1995-10-11
EP0676278B1 EP0676278B1 (fr)	1999-03-03

Family

ID=6514964

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP95104720A Expired - Lifetime EP0676278B1 (fr)	1994-04-08	1995-03-30	Dispositif de réglage de la course pour presses ou poinçonneuses

Country Status (4)

Country	Link
EP (1)	EP0676278B1 (fr)
AT (1)	ATE177052T1 (fr)
DE (2)	DE4412198C1 (fr)
ES (1)	ES2129690T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CN102562983A (zh) *	2012-02-17	2012-07-11	济南铸造锻压机械研究所有限公司	曲柄连杆传动机构及冲床主传动***
CN104141755A (zh) *	2012-02-17	2014-11-12	济南铸造锻压机械研究所有限公司	能调整偏心距的曲柄连杆传动机构及冲床主传动***

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE19612954C1 (de) *	1996-04-01	1997-11-20	Kaiser Kg Otto	Hubverstelleinrichtung
DE19910965A1 (de) *	1999-03-12	2000-09-14	Mueller Weingarten Maschf	Presse mit einer Verriegelungseinrichtung für Pressenstößel
DE10227088B4 (de) *	2002-06-18	2005-04-14	Müller Weingarten AG	Pressenantrieb
EP1867468A1 (fr) *	2006-06-12	2007-12-19	Haulick + Roos GmbH	Dispositif de réglage de course ainsi qu'une presse, une presse de poinçonnage ou de formage muni d'un tel dispositif
CN102431207A (zh) *	2011-12-26	2012-05-02	江苏扬力集团有限公司	压力机行程量无级自动调节结构

Citations (4)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
FR2479740A1 (fr) *	1980-04-02	1981-10-09	Strasbourg Sa Forges	Dispositif automatique de changement de course du coulisseau dans une presse mecanique a course variable
DE8127545U1 (de) *	1981-09-19	1983-04-14	Maschinenfabrik Weingarten Ag, 7987 Weingarten	Vollautomatische Verstellung des Stösselhubes bei Doppelständerpressen mit zwei auf Exzenterbüchsen einer Exzenterwelle hintereinander angeordneten Pleuel
DE8407274U1 (de) *	1984-03-09	1990-07-12	Haulick + Roos Werkzeugmaschinen GmbH, 7530 Pforzheim	Vorrichtung zum Verändern des Stößelhubes an einer Exzenterpresse
US5109766A (en) *	1990-10-31	1992-05-05	The Minster Machine Company	Adjustable stroke punch press

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE3112382C2 (de) *	1981-03-28	1983-11-24	RWM-Raster-Werkzeugmaschinen GmbH, 7136 Ötisheim	Hubverstelleinrichtung für Exzenterpressen oder -stanzen
DD239376A1 (de) *	1985-04-16	1986-09-24	Warnke Umformtech Veb K	Vorrichtung zur hubverstellung an exzenterpressen

1994
- 1994-04-08 DE DE4412198A patent/DE4412198C1/de not_active Expired - Lifetime
1995
- 1995-03-30 EP EP95104720A patent/EP0676278B1/fr not_active Expired - Lifetime
- 1995-03-30 AT AT95104720T patent/ATE177052T1/de not_active IP Right Cessation
- 1995-03-30 ES ES95104720T patent/ES2129690T3/es not_active Expired - Lifetime
- 1995-03-30 DE DE59505156T patent/DE59505156D1/de not_active Expired - Lifetime

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
FR2479740A1 (fr) *	1980-04-02	1981-10-09	Strasbourg Sa Forges	Dispositif automatique de changement de course du coulisseau dans une presse mecanique a course variable
DE8127545U1 (de) *	1981-09-19	1983-04-14	Maschinenfabrik Weingarten Ag, 7987 Weingarten	Vollautomatische Verstellung des Stösselhubes bei Doppelständerpressen mit zwei auf Exzenterbüchsen einer Exzenterwelle hintereinander angeordneten Pleuel
DE8407274U1 (de) *	1984-03-09	1990-07-12	Haulick + Roos Werkzeugmaschinen GmbH, 7530 Pforzheim	Vorrichtung zum Verändern des Stößelhubes an einer Exzenterpresse
US5109766A (en) *	1990-10-31	1992-05-05	The Minster Machine Company	Adjustable stroke punch press
US5109766B1 (en) *	1990-10-31	1994-03-22	Minster Machine Co	Adjustable stroke punch press

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CN102562983A (zh) *	2012-02-17	2012-07-11	济南铸造锻压机械研究所有限公司	曲柄连杆传动机构及冲床主传动***
CN104141755A (zh) *	2012-02-17	2014-11-12	济南铸造锻压机械研究所有限公司	能调整偏心距的曲柄连杆传动机构及冲床主传动***
CN102562983B (zh) *	2012-02-17	2014-12-24	济南铸造锻压机械研究所有限公司	曲柄连杆传动机构及数控转塔冲床主传动***

Also Published As

Publication number	Publication date
EP0676278B1 (fr)	1999-03-03
DE59505156D1 (de)	1999-04-08
ES2129690T3 (es)	1999-06-16
ATE177052T1 (de)	1999-03-15
DE4412198C1 (de)	1995-05-04

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