EP3130809A1 - Gelenkhebelantrieb mit optimiertem wirkungsgrad - Google Patents

Gelenkhebelantrieb mit optimiertem wirkungsgrad Download PDF

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Publication number
EP3130809A1
EP3130809A1 EP16182930.4A EP16182930A EP3130809A1 EP 3130809 A1 EP3130809 A1 EP 3130809A1 EP 16182930 A EP16182930 A EP 16182930A EP 3130809 A1 EP3130809 A1 EP 3130809A1
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EP
European Patent Office
Prior art keywords
equal
rod
comprised
clamping
length
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.)
Granted
Application number
EP16182930.4A
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English (en)
French (fr)
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EP3130809B1 (de
Inventor
Roberto Bottacini
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.)
Pneumax SpA
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Pneumax SpA
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Publication date
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Publication of EP3130809A1 publication Critical patent/EP3130809A1/de
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Publication of EP3130809B1 publication Critical patent/EP3130809B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B5/00—Clamps
    • B25B5/06—Arrangements for positively actuating jaws
    • B25B5/12—Arrangements for positively actuating jaws using toggle links
    • B25B5/122—Arrangements for positively actuating jaws using toggle links with fluid drive

Definitions

  • the present invention relates to an articulated lever actuation unit with optimized efficiency.
  • the present invention relates to an actuation unit of the above optimized efficiency type in terms of energy consumption and overall dimensions.
  • Articulated lever actuation units such as locking unit and pivot units, are typically used for handling and/or clamping elements during sheet metal processing.
  • clamping units for keeping the metal sheets into position during mechanical processes (such as welding, crimping or other technique for joining metal sheets).
  • clamping units comprise a closing device able to cause the rotation of a clamping arm, connected to such a closing device, up to an exact operating angular position of closure and, once achieved, keep it in such a position, triggering an irreversibility mechanism able to guarantee the position even in the absence of control (for example, in the absence of air in the case of pneumatic control).
  • the stroke of the closing device which generally corresponds to a rotation of 135° of the clamping arm, is usually controlled through a pneumatic or electrical actuation, depending on the specific embodiment.
  • the closing device comprises a piston which acts on a toggle mechanism to which the clamping arm is in turn constrained.
  • the toggle mechanism consists of a connecting rod and a crank rod, where the connecting rod is pivoted at the ends thereof to the piston rod and to the crank rod, respectively, and the crank rod sets the clamping arm in rotation.
  • the connecting rod and the crank rod are typically made of multiple parts or as a single part, for example by means of a fork.
  • pneumatic actuation of the piston feeding of pressurized fluid, usually compressed air, is required for generating the thrust force required.
  • pressurized fluid usually compressed air
  • the generation of compressed air has a very low yield, typically less than 3%.
  • pneumatic actuations are generally characterized by high losses which lead to an increase in the consumption of compressed air, in addition to that strictly necessary for control. This source of energy is therefore particularly inefficient and expensive.
  • Actuation units designed to optimize air consumption are known in the art. They use complex pneumatic circuits that allow a partial air recovery. In this way, keeping the other features of the actuation unit unchanged, the pneumatic cylinder is able to operate and produce the same thrust force on the piston through a reduced supply of compressed air.
  • An example of a clamping unit that uses such a solution is described in patent EP 2016290 .
  • the problem underlying the present invention therefore is to devise an articulated lever actuation unit able to operate with a reduced energy supply while offering the same clamping moment, as well as having substantially identical overall dimensions.
  • the object of the present invention is to devise an articulated lever actuation unit operable both with a pneumatic actuation and with an electric actuation, achieving a remarkable energy saving.
  • the invention therefore relates to an articulated lever actuation unit comprising a body, inside which a control piston is slidably associated to the body along a sliding axis, the control piston being connected or coupled to actuation means able to exert a thrust force P on the control piston, where
  • actuation units available on the market are made according to predetermined and by the industrial standards specifically defined "models" in terms of both clamping moment and actuation, which in the specific case of pneumatic actuation translates into "sizes" of the actuation cylinders.
  • a known model of clamping unit currently widespread on the market is actuated by means of a ⁇ 50 mm pneumatic cylinder, offering a clamping moment of a value comprised between 180 N m and 230 N m.
  • a further widespread model of clamping unit is actuated by means of a ⁇ 63 mm pneumatic cylinder, offering a clamping moment of a value comprised between 375 N m and 425 N m.
  • Such pneumatic cylinders when supplied at a pressure of 5 bar, generate a thrust force equal to 981.75 N and 1558.62 N, respectively, consuming a volume of compressed air at each cycle substantially proportional to the respective thrust force.
  • the Applicant has therefore identified a need to operate the articulated lever actuation unit through a lower thrust force, while keeping the clamping moment and the overall dimensions substantially unchanged in order to satisfy the industrial standards of the field.
  • k is calculated with respect to a position of the pivotable arm other than the closed position and has to be considered invariable with respect to the plurality of physical characteristics which determine the geometry of the actuating unit defined by the industrial standards since, in turn, these physical characteristics are considered to be predefined by the standards.
  • Such factor k has furthermore to be considered substantially invariable also with respect to the first rod length BA (also known as connecting rod) which just negligibly contributes to the generation of clamping moment at the output, by substantially working along the horizontal.
  • the Applicant has first noted that, in order to keep the clamping moment unchanged while reducing the thrust force P exerted on the piston by the (either pneumatic or electric) actuator to achieve energy saving, the length of the second rod needs to be increased.
  • the Applicant has, in fact, found that, near to such condition, such a proportionality factor is strongly influenced by the energy typically dissipated by the system, releasing the thrust force exerted on the articulated lever mechanism on contrast elements.
  • the contrast elements for example are the walls of the body against which the articulated lever mechanism rests during the movement caused by the translation of the piston rod, rather than the rods (connecting rod and crank) themselves. These elements are able, by deforming, to absorb part of the thrust force exerted on the same.
  • the Applicant has found that, advantageously, the dissipation incurred by the system is considerably lower in proportion for lower thrust forces, thereby allowing a same clamping moment to be obtained with crank lengths well lower than those theoretically calculated. This at the same time allows a considerable energy saving to be obtained while keeping the current overall dimensions unchanged.
  • the Applicant has unexpectedly found that the proportionality factor k that binds the clamping moment to the product between thrust force and length of the second lever is comprised between 6.8 and 10.0 for clamping moments comprised between 180 N m and 230 N m, allowing energy saving to be obtained while keeping the length of the second rod AO equal to or less than 32 mm and therefore not changing the current overall dimensions of the corresponding clamping units known to date, able to offer the same clamping moments.
  • the Applicant has surprisingly found that the proportionality factor k that binds the clamping moment to the product between thrust force and length of the second lever is comprised between 8.0 and 12.2 for a clamping moment comprised between 375 N m and 425 N m, allowing energy saving to be obtained while keeping the length of the second rod AO equal to or less than 35.5 mm and therefore not changing the current overall dimensions of the corresponding clamping units known to date, able to offer the same clamping moments.
  • the Applicant has surprisingly found that the proportionality factor k that binds the clamping moment to the product between thrust force and length of the second lever is comprised between 6.8 and 11.4 for a clamping moment comprised between 830 N m and 880 N m, allowing energy saving to be obtained while keeping the length of the second rod AO equal to or less than 56.5 mm and therefore not changing the current overall dimensions of the corresponding clamping units known to date, able to offer the same clamping moments.
  • the Applicant has surprisingly found that the proportionality factor k that binds the clamping moment to the product between thrust force and length of the second lever is comprised between 8.0 and 13.8 for a clamping moment comprised between 115 N m and 145 N m, allowing energy saving to be obtained while keeping the length of the second rod AO equal to or less than 30.5 mm and therefore not changing the current overall dimensions of the corresponding clamping units known to date, able to offer the same clamping moments.
  • the Applicant has surprisingly succeeded in obtaining articulated lever actuation units able to provide, for equal overall dimensions, same clamping moments with an optimization of the energy saving of up to about 46%.
  • the optimization of the geometry of the articulated lever mechanism of the actuation unit with reference to the thrust force applied allows energy saving to be obtained also in the presence of an electric or combined pneumatic-manual or electric-manual actuation, it being possible to significantly reduce the thrust force required to generate the desired clamping moment without it being necessary to modify the current overall dimensions.
  • the present invention may have at least one of the following preferred features; the latter may in particular be combined with each other as desired to meet specific application requirements.
  • the length of the second rod ( AO ) is
  • the piston stroke is increased proportionally to the increase in the length of the second rod.
  • the actuation means are of the pneumatic type, comprising a pneumatic cylinder, the thrust force exerted by the pneumatic cylinder depending on the cylinder section and on the piston stroke.
  • the pneumatic cylinder is of the standard size type having section 0 equal to 40 mm and the second rod has a length AO equal to about 32 mm.
  • the piston stroke is equal to about 84.8 mm and the pneumatic cylinder is operated at about 5 bar.
  • the clamping moment M is comprised between 185 N m and 190 N m, even more preferably substantially equal to 186 N m.
  • the pneumatic cylinder is of the standard size type having section 0 equal to 50 mm and the second rod has a length AO equal to about 35 mm.
  • the piston stroke is equal to about 91.77 mm and the pneumatic cylinder is operated at about 5 bar.
  • the clamping moment M is comprised between 380 N m and 400 N m, even more preferably substantially equal to 390 N m.
  • the pneumatic cylinder is of the standard size type having section 0 equal to 63 mm and the second rod has a length AO equal to about 55 mm.
  • the piston stroke is equal to about 144.7 mm and the pneumatic cylinder is operated at about 5 bar.
  • the clamping moment M is comprised between 845 N m and 855 N m, even more preferably substantially equal to 850 N m.
  • the pneumatic cylinder is of the standard size type having section 0 equal to 32 mm and the second rod has a length AO equal to about 29 mm.
  • the piston stroke is equal to about 77 mm and the pneumatic cylinder is operated at about 5 bar.
  • the clamping moment M is comprised between 125 N m and 135 N m, even more preferably substantially equal to 130 N m.
  • the articulated lever actuation unit is a clamping unit.
  • the articulated lever actuation unit is a pivot unit.
  • an articulated lever actuation unit is shown according to the present invention, indicated overall with reference numeral 10, in particular a clamping unit.
  • the clamping unit 10 comprises a body 11 within which a control piston 12 is arranged, comprising a rod 12a which can slide within body 11 along a sliding axis A.
  • Rod 12a of piston 12 is connected to an articulated lever mechanism 13, specifically comprising a toggle mechanism consisting of a pair of rods 13a, 13b.
  • a first rod 13a also called connecting rod, is pivoted at the ends thereof to the piston rod 12a and to the second rod 13b, called crank rod 13b, respectively.
  • the crank rod 13b is rotatably connected to body 11 and, at the axis of revolution B thereof, it sets a clamping arm 14 in rotation.
  • the control piston 12 is coupled to a pneumatic cylinder 15 able to exert a thrust force P on the control piston when supplied with compressed air.
  • Figure 2 schematically shows the articulated lever mechanism 13 in a different configuration compared to the irreversibility condition shown in figure 1b .
  • rod AO corresponds to the crank rod 13b
  • rod AB corresponds to the connecting rod 13a
  • the third rod schematizes rod 12a of piston 12.
  • a known clamping unit was considered, characterized by the following parameters:
  • a clamping unit was implemented characterized by the following parameters:
  • the energy consumption of the clamping unit according to the embodiment of the present example in line with the invention therefore was 213.13 cm 3 , i.e. more than 30% lower than the consumption of the clamping unit of the prior art described in the comparative Example 1.
  • such an increase in length is not compatible with the requirement of keeping the overall dimensions of the starting clamping unit unchanged.
  • a clamping unit was implemented characterized by the following parameters:
  • the energy consumption of the clamping unit according to the embodiment of the present example in line with the invention therefore was 360.39 cm 3 i.e. more than 32% lower than the consumption of the clamping unit of the prior art described in the comparative Example 2.
  • crank rod it was sufficient to extend the crank rod by only 3.5 mm, obtaining the same torque equal to 390 N m with a pneumatic actuation carried out with a cylinder having section 0 equal to 50 mm.
  • such an increase in length is not compatible with the requirement of keeping the overall dimensions of the starting clamping unit unchanged.
  • a clamping unit was implemented characterized by the following parameters:
  • the energy consumption of the clamping unit according to the embodiment of the present example in line with the invention therefore was 123.85 cm 3 , i.e. more than 30% lower than the consumption of the clamping unit of the prior art described in the comparative Example 3.
  • such an increase in length is not compatible with the requirement of keeping the overall dimensions of the starting clamping unit unchanged.
  • a clamping unit was implemented characterized by the following parameters:
  • the energy consumption of the clamping unit according to the embodiment of the present example in line with the invention therefore was 902.13 cm 3 , i.e. more than 33% lower than the consumption of the clamping unit of the prior art described in the comparative Example 4.
  • the Applicant has also found that, in clamping units according to the industrial standards that provide an output clamping moment comprised between 375 N m and 425 N m, the length of the crank rod, amounting today to 31.5 mm, can be incremented by nevertheless remaining under or equal to 35.5 mm so as to keep the current overall dimensions unchanged.
  • the Applicant has also found that, in clamping units according to the industrial standards that provide an output clamping moment comprised between 115 N m and 145 N m, the length of the crank rod, amounting today to 26 mm, can be incremented by nevertheless remaining under or equal to 30.5 mm so as to keep the current overall dimensions unchanged.
  • the Applicant has also found that, in clamping units according to the industrial standards that provide an output clamping moment comprised between 830 N m and 880 N m, the length of the crank rod, amounting today to 50 mm, can be incremented by nevertheless remaining under or equal to 56.5 mm so as to keep the current overall dimensions unchanged.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Jigs For Machine Tools (AREA)
  • Transmission Devices (AREA)
EP16182930.4A 2015-08-13 2016-08-05 Gelenkhebelantrieb mit optimiertem wirkungsgrad Active EP3130809B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITUB2015A003120A ITUB20153120A1 (it) 2015-08-13 2015-08-13 Unita' di attuazione del tipo a leva articolata a efficienza ottimizzata

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EP3130809A1 true EP3130809A1 (de) 2017-02-15
EP3130809B1 EP3130809B1 (de) 2023-08-02

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108857966A (zh) * 2017-05-15 2018-11-23 奥拉夫和安德烈德珂斯协会 用于使用在机动车工业的车身结构中的弯曲杠杆夹紧装置
IT202000003805A1 (it) * 2020-02-24 2021-08-24 Pneumax S P A Unita’ di attuazione del tipo a leva articolata o a camma ad azionamento elettrico
IT202000003784A1 (it) * 2020-02-24 2021-08-24 Pneumax S P A Unita’ di attuazione del tipo a leva articolata o a camma ad azionamento elettrico

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Publication number Priority date Publication date Assignee Title
EP0341155A1 (de) 1988-05-06 1989-11-08 Genus International Spannvorrichtung, um Platten oder Profilstähle gegeneinander zu spannen
DE29811331U1 (de) 1997-10-08 1998-10-08 Genus Technologies, Chatillon Vorrichtung zum Halten, Positionieren und Spannen
EP0894573A2 (de) * 1997-07-29 1999-02-03 Benteler Ag Bauteilspanner
EP0993932A2 (de) 1998-10-12 2000-04-19 STRIP's d.o.o. Podjetje za svetovanje trzenje in proizvodnjo Presse mit kniehebelantrieb
EP1088623A2 (de) 1999-10-01 2001-04-04 SMC Kabushiki Kaisha Elektrische Spannvorrichtung
EP1149665A2 (de) 2000-04-28 2001-10-31 SMC Kabushiki Kaisha Elektrische Aufspannvorrichtung
EP1179394A2 (de) 2000-08-03 2002-02-13 Norgren Automotive Inc. Selbsthemmende, angetriebene Spannvorrichtung mit Kniehebel-Mechanismus
US6416045B1 (en) 2000-07-25 2002-07-09 Norgren Automotive, Inc. Rotary clamp having predetermined adjustable clamping angles
DE10136057C1 (de) 2001-07-25 2002-10-02 Tuenkers Maschinenbau Gmbh Kniehebelspannvorrichtung
EP1262285A2 (de) 2001-04-30 2002-12-04 Btm Corporation Spannvorrichtung mit einstellbarem Hub
EP1310332A2 (de) * 2001-11-05 2003-05-14 Luciano Migliori Elektrisch betätigte Spannvorrichtung
DE102004007346B3 (de) 2003-11-04 2005-04-21 Tünkers Maschinenbau Gmbh Kniehebelspannvorrichtung - auch Spannwerkzeug wie Punktschweißvorrichtung mit Kniehebelgelenkanordnung, oder Clinchwerkzeug mit Kniehebelgelenkanordnung oder dergleichen -, zur Verwendung im Karosseriebau der Kfz-Industrie
EP1849559A1 (de) 2006-04-27 2007-10-31 UNIVER S.p.A. Positionierungs- und/oder Klemmvorrichtung mit einstellbarer Öffnungsposition des Arbeitsarms
EP2016290A1 (de) 2006-05-10 2009-01-21 TÜNKERS MASCHINENBAU GmbH Verfahren zum beaufschlagen eines arbeitszylinders, steuerung dafür, arbeitszylinder und verwendung desselben
EP1878539B1 (de) 2006-06-26 2009-04-15 UNIVER S.p.A. Klemm- und/oder Zentriervorrichtung für Werkstücke, mit manuell einstellbaren Arbeitspositionen
EP2055430B1 (de) 2007-10-29 2009-06-10 UNIVER S.p.A. Kniehebelspannvorrichtung
EP2177320A1 (de) * 2008-10-15 2010-04-21 UNIVER S.p.A. Irreversible Kniehebelantriebsvorrichtung
DE202015004786U1 (de) 2014-10-06 2015-08-14 Olaf Und André Tünkers Gbr (Vertretungsberechtigter Gesellschafter: Dipl.-Ing. Olaf Tünkers, 40885 Ratingen) Kniehebelspannvorrichtung, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0341155A1 (de) 1988-05-06 1989-11-08 Genus International Spannvorrichtung, um Platten oder Profilstähle gegeneinander zu spannen
EP0894573A2 (de) * 1997-07-29 1999-02-03 Benteler Ag Bauteilspanner
DE29811331U1 (de) 1997-10-08 1998-10-08 Genus Technologies, Chatillon Vorrichtung zum Halten, Positionieren und Spannen
EP0993932A2 (de) 1998-10-12 2000-04-19 STRIP's d.o.o. Podjetje za svetovanje trzenje in proizvodnjo Presse mit kniehebelantrieb
EP1088623A2 (de) 1999-10-01 2001-04-04 SMC Kabushiki Kaisha Elektrische Spannvorrichtung
EP1149665A2 (de) 2000-04-28 2001-10-31 SMC Kabushiki Kaisha Elektrische Aufspannvorrichtung
US6416045B1 (en) 2000-07-25 2002-07-09 Norgren Automotive, Inc. Rotary clamp having predetermined adjustable clamping angles
EP1179394A2 (de) 2000-08-03 2002-02-13 Norgren Automotive Inc. Selbsthemmende, angetriebene Spannvorrichtung mit Kniehebel-Mechanismus
EP1262285A2 (de) 2001-04-30 2002-12-04 Btm Corporation Spannvorrichtung mit einstellbarem Hub
DE10136057C1 (de) 2001-07-25 2002-10-02 Tuenkers Maschinenbau Gmbh Kniehebelspannvorrichtung
EP1310332A2 (de) * 2001-11-05 2003-05-14 Luciano Migliori Elektrisch betätigte Spannvorrichtung
DE102004007346B3 (de) 2003-11-04 2005-04-21 Tünkers Maschinenbau Gmbh Kniehebelspannvorrichtung - auch Spannwerkzeug wie Punktschweißvorrichtung mit Kniehebelgelenkanordnung, oder Clinchwerkzeug mit Kniehebelgelenkanordnung oder dergleichen -, zur Verwendung im Karosseriebau der Kfz-Industrie
EP1849559A1 (de) 2006-04-27 2007-10-31 UNIVER S.p.A. Positionierungs- und/oder Klemmvorrichtung mit einstellbarer Öffnungsposition des Arbeitsarms
EP2016290A1 (de) 2006-05-10 2009-01-21 TÜNKERS MASCHINENBAU GmbH Verfahren zum beaufschlagen eines arbeitszylinders, steuerung dafür, arbeitszylinder und verwendung desselben
EP1878539B1 (de) 2006-06-26 2009-04-15 UNIVER S.p.A. Klemm- und/oder Zentriervorrichtung für Werkstücke, mit manuell einstellbaren Arbeitspositionen
EP2055430B1 (de) 2007-10-29 2009-06-10 UNIVER S.p.A. Kniehebelspannvorrichtung
EP2177320A1 (de) * 2008-10-15 2010-04-21 UNIVER S.p.A. Irreversible Kniehebelantriebsvorrichtung
DE202015004786U1 (de) 2014-10-06 2015-08-14 Olaf Und André Tünkers Gbr (Vertretungsberechtigter Gesellschafter: Dipl.-Ing. Olaf Tünkers, 40885 Ratingen) Kniehebelspannvorrichtung, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie
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WO2016055138A1 (de) 2014-10-06 2016-04-14 Olaf Und Andre Tünkers Gbr Kniehebelspannvorrichtung, insbesondere zur verwendung im karosseriebau der kfz-industrie

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TUNKERS®: "Universalspanner U/U2 63, 80 BR5 A40", DATENBLATT, 26 June 2020 (2020-06-26), XP055961325

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108857966A (zh) * 2017-05-15 2018-11-23 奥拉夫和安德烈德珂斯协会 用于使用在机动车工业的车身结构中的弯曲杠杆夹紧装置
CN108857966B (zh) * 2017-05-15 2021-04-30 奥拉夫和安德烈德珂斯协会 用于使用在机动车工业的车身结构中的弯曲杠杆夹紧装置
IT202000003805A1 (it) * 2020-02-24 2021-08-24 Pneumax S P A Unita’ di attuazione del tipo a leva articolata o a camma ad azionamento elettrico
IT202000003784A1 (it) * 2020-02-24 2021-08-24 Pneumax S P A Unita’ di attuazione del tipo a leva articolata o a camma ad azionamento elettrico
WO2021171189A1 (en) * 2020-02-24 2021-09-02 Pneumax S.P.A. Electrically operated actuating unit of the articulated lever or cam type

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EP3130809B1 (de) 2023-08-02
ITUB20153120A1 (it) 2017-02-13

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