EP1179394A2 - Dispositif motorisé de serrage autobloquant avec mécanisme à genouillère - Google Patents

Dispositif motorisé de serrage autobloquant avec mécanisme à genouillère Download PDF

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Publication number
EP1179394A2
EP1179394A2 EP01306592A EP01306592A EP1179394A2 EP 1179394 A2 EP1179394 A2 EP 1179394A2 EP 01306592 A EP01306592 A EP 01306592A EP 01306592 A EP01306592 A EP 01306592A EP 1179394 A2 EP1179394 A2 EP 1179394A2
Authority
EP
European Patent Office
Prior art keywords
link
roller
over
clamp
center
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.)
Withdrawn
Application number
EP01306592A
Other languages
German (de)
English (en)
Other versions
EP1179394A3 (fr
Inventor
Wayne D. Morroney
Timothy Wheeler
Jeffrey J. Dellach
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.)
Norgren Automotive Inc
Original Assignee
Norgren Automotive Inc
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
Priority claimed from US09/891,916 external-priority patent/US6557841B2/en
Application filed by Norgren Automotive Inc filed Critical Norgren Automotive Inc
Publication of EP1179394A2 publication Critical patent/EP1179394A2/fr
Publication of EP1179394A3 publication Critical patent/EP1179394A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • 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
    • B25B5/16—Details, e.g. jaws, jaw attachments

Definitions

  • the present invention relates, in general, to rotary clamps for linear actuators, and, more particularly, to a rotary clamp having a linkage assembly that provides an over-center condition for providing high actuation and clamping forces without excessively wearing the components of the linkage assembly.
  • Rotary clamps are known of the type in which linear actuator reciprocating movement is adapted to be translated into angular rotary movement of a clamp arm.
  • the linear actuator may be powered by a fluid motor, and an additional linkage or other transmitting means converts the linear actuator motion into rotary clamp motion.
  • the clamp is in a released position, that is, the clamp arm is removed from the work supporting surface.
  • the clamp arm is pivotally moved into a clamping position to clamp a workpiece to a work supporting surface and hold and/or locate the workpiece against the work supporting surface.
  • a known design powers a linear actuator along a guide slot provided in a housing of the clamp.
  • the linear actuator is pivotally connected to a linkage assembly which in turn is pivotally connected to a lever arm of a shaft link.
  • the linear actuator provides reciprocal linear movement along the guide slot, thus driving the linkage assembly which converts the linear movement of the linear actuator into rotational movement of the shaft link.
  • a clamp arm is connected to the shaft link wherein the shaft link provides rotary motion to the clamp arm between a clamped position and an unclamped position.
  • the present invention overcomes the above-noted shortcomings by providing a rotary clamp that provides for an over-center linkage position without experiencing excessive wear to the rotary clamp.
  • the rotary clamp of the present invention provides a means for converting linear actuator motion between a first position and a second position into rotary clamp motion between an unclamped position and a clamped position, respectively.
  • the present invention also provides a means for preventing a first link of the converting means from reaching an over-center position and allowing a second link of the converting means to reach an over-center position in the clamped position thereby creating higher clamping and actuating forces without causing wear to the clamp.
  • a means for resisting movement of the converting means from said clamped position toward said unclamped position is also provided.
  • the converting means provides a linkage assembly connected to a linear actuator and a clamp arm.
  • the linkage assembly includes a first link pivotally connected to a second link, and a third link pivotally connected to the second link.
  • the preventing means provides a pin received by an aperture provided in the first link of the linkage assembly wherein a roller is coaxially connected to the pin.
  • the roller engages the third link of the linkage assembly when moving in and out of the clamped position, and the pin engages a wear surface in response to the roller engaging the third link to prohibit the first link from reaching the over-center position.
  • the resisting means provides a spring detent for engaging the roller and resisting movement of the rotary clamp from the clamped position to the unclamped position.
  • Figs. 1-8 illustrate a rotary clamp 10 as defined by the present invention.
  • the rotary clamp 10 is actuated by a fluid cylinder or linear actuator 12 having a piston 14 therein.
  • the piston 14 is connected to a piston rod 16 which extends outwardly from the linear actuator 12 and is received by a housing 18 of the rotary clamp 10.
  • the linear actuator 12 is preferably pneumatic, but the linear actuator 12 may also be hydraulic.
  • the linear actuator 12 provides linear reciprocating movement between a first position and a second position to the piston rod 16.
  • a means for converting the linear actuator motion between the first position and the second position to a rotary clamp motion between a clamped position and unclamped position, respectively, is connected to the piston rod 16 .
  • the converting means transfers the rotary clamp motion to a clamp arm 20 mounted outside and adjacent the housing 18 .
  • the housing 18 of the rotary clamp 10 is attached to one end of the linear actuator 12 and is formed by two halves 22 of the housing 18.
  • the two halves 22 of the housing 18 form a hollow portion for housing a pair of opposing plate-like structures 24 .
  • the plate-like structures 24 are fabricated from a high strength metallic material so as to support the clamping forces transmitted through the rotary clamp 10 .
  • the plate-like structures 24 combine with a pair of beam-like structures 26 to form an elongated guide slot 28 that extends longitudinally through the housing 18 of the rotary clamp 10 .
  • the two halves 22 of the housing 18 , the plate-like structures 24 , and the beam-like structures 26 are connected by dowel pins 30 that are press-fit through apertures 31 provided in the corresponding structures.
  • the one end of the housing 18 adjacent the linear actuator 12 is open to receive the free end of the piston rod 16 .
  • the housing 18 also includes a series of coaxial apertures 32 which extend through the two halves 22 of the housing 18 and through the plate-like structures 24 of the housing 18. These coaxial apertures 32 have a common axis 34 offset from and substantially perpendicular to a longitudinal axis 36 of the guide slots 28 .
  • an adjustable piston rod assembly 38 provides for linear telescopic adjustment of the piston rod 16 along its longitudinal axis.
  • the adjustable piston rod assembly 38 is the subject of a separate patent application under a common assignee, and because the adjustable piston rod assembly 38 is not a necessary feature of the present invention, the adjustable piston rod assembly 38 will not be discussed in detail here.
  • the necessary features of the adjustable piston rod assembly 38 for the present invention are that the adjustable piston rod assembly 38 provides an adjustable telescopic piston rod 16 and a rod end 42 .
  • the adjustable telescopic piston rod 16 provides a solid rod 46 that is telescopically received by a hollow shaft 50.
  • An adjustment mechanism 51 is connected to the end of the hollow shaft 50 and allows for telescopic adjustment of the rod 46 within the hollow shaft 50.
  • the adjustment mechanism 51 provides a small housing or block 52 which houses a spring biased cam 54.
  • the cam 54 provides a through aperture 56 for receiving the rod 46.
  • the rod 46 provides a plurality of cylindrical recesses 58 for receiving a portion of the cam 54 that defines a smaller radius portion of the aperture 56 in the cam 54.
  • the cam 54 is accessed from outside the housing 18 of the rotary clamp 10 through an aperture 60 provided in the housing 52 of the rotary clamp 10 and an aperture 61 provided in the block 52 of the adjustment mechanism 51 .
  • the cam 54 pivots about pin 63, and upon applying a force against the cam 54, the cam 54 will yield against the bias of spring 62 to allow rod 46 to pass through a larger radius portion of aperture 56.
  • the rod 46 may then be telescopically moved relative to the hollow shaft 50.
  • the portion of the cam 54 that defines the smaller radius portion of aperture 56 engages one of the cylindrical recesses 58 of rod 46 to lock the telescopic piston rod 16 into a fixed position.
  • the rod end 42 is connected to the end of rod 46 of the telescopic piston rod 16.
  • the rod end 42 provides a pin 48 which extends through the lateral sides of the rod end 42.
  • the rod end 42 has a flat top surface which is sensed by a pair of proximity switches 44.
  • the proximity switches 44 send a signal to a controller (not shown) to electronically identify when the rotary clamp 10 is in the clamped or unclamped position.
  • the converting means provides a linkage assembly 17 having a pair of first links 64, a pair of second links 76, and a third link 82.
  • the first links or linkage members 64 are substantially parallel and oval and have three corresponding apertures 57, 68, 80 extending therethrough.
  • the first aperture 57 pivotally receives the ends of pins 48 wherein the ends of pin 48 are received by and slide along the elongated guide slot 28.
  • the second aperture 68 of linkage members 64 pivotally receives the ends of a pin 72 which is mounted within a roller 70.
  • the roller 70 includes an aperture for receiving pin 72 such that pin 72 is coaxially mounted along the center-line axis of roller 70.
  • the second aperture 68 in the linkage members 64 is substantially oblong or oval so that when the roller 70 engages the linkage assembly 17, as will be described in detail later, the pin 72 may move within the second apertures 68 thus allowing the roller 70 to move relative to the linkage member 64.
  • Roller bearings (not shown) may be utilized between pin 72 and the second aperture 68 of linkage members 64 to enhance the rolling of roller 70.
  • the ends of pin 72 are received by and slide along the elongated guide slot 28 created by the plate-like structure 24 and the beam-like structure 26.
  • the linkage members 64 are pivotally connected to the second links or toggle links 76 by the third aperture 80 of linkage members 64 pivotally receiving an integral post 78 from the toggle links 76 .
  • the toggle links 76 are substantially oval and directly oppose one another.
  • Each post 78 of the toggle links 76 is substantially cylindrical and extends outward from one end of the links 76 .
  • the links 76 are pivotally connected to a shaft link or third link 82.
  • the shaft link 82 includes an integral lever arm 84 having an aperture 86 extending therethrough.
  • Coaxial apertures 90 provided in toggle links 76 are aligned with the through aperture 86 in the lever arm 84 of the shaft link 82, and a pin 88 is inserted therethrough such that the toggle links 76 are pivotally mounted on opposite sides of the lever arm 84.
  • the shaft link 82 includes a pivot pin 92 that is integrally connected to the lever arm 84 .
  • the pivot pin 92 is substantially cylindrical and is rotatably disposed within the coaxial apertures 32 provided in the housing 18 of the rotary clamp 10 .
  • a pair of bushings 94 are seated within the coaxial apertures 32 in the housing 18 to act as a bearing surface for pivot pin 92 .
  • O-rings 95 are utilized to seal the bushings 94 to the housing 18 .
  • a substantially rectangular portion 96 of the pivot pin 92 extends through the coaxial apertures 32 and away from the housing 18 to allow the clamp arm 20 to be mounted thereto.
  • the end portion of the pivot pin 92 may be substantially cylindrical as seen in the alternative embodiment shown in FIG. 3, 4A and B.
  • the clamp arm 20 is fastened to the cylindrical pivot pin 92 through a plurality of fasteners.
  • the shaft link 82 provides a positive stop 98 integral with and extending from the lever arm 84.
  • the positive stop 98 engages a post 100 that is secured between the interior walls of the housing 18.
  • positive stop 98 has a substantially flat surface that engages post 100, but the positive stop 98 may also be formed as an arcuate surface therein to complement and receive the substantially circular shape of the post 100.
  • the positive stop 98 abuts the post 100 to limit the travel of the clamp arm 20 in the clamped position.
  • the rotary clamp 10 is designed not to open unexpectedly upon the loss of power and/or air pressure to the linear actuator 12 , it may be desirable to move the rotary clamp 10 to the unclamped position in order to release a workpiece (not shown) or reset the linkage assembly 17. Due to the position of the linkage assembly 17 when in the clamped position, the actuation force may be too great to manually move the rotary clamp 10 to the unclamped position without disassembling the rotary clamp 10 or the linear actuator 12.
  • the present invention provides a reciprocal member 102 that is slidably disposed within a slot 103 provided in the end wall of the housing 18.
  • the reciprocal member 102 has a substantially rectangular body with a pair of larger end portions extending within the housing 18 and beyond the length of the slot 103 so as to capture the reciprocal member 102 within the end wall of the housing 18.
  • the reciprocal member 102 is aligned with the mid-portion of links 76 so that the reciprocal member 102 is displaced by the links 76 when the rotary clamp 10 is in the clamped position. If power and/or air is lost to the rotary clamp 10 when in the clamped position, the reciprocal member 102 may be manually pushed to move the linkage assembly 17 toward the unclamped position.
  • the present invention provides a means for preventing the first link 64 of the linkage assembly 17 from reaching an over-center position while allowing the second link 76 of the linkage assembly 17 to reach an over-center position when in the clamped position.
  • the pin 72 may provide a flat surface to enhance the engagement with the wear surface of the beam-like structure. Further upward pressure is applied to the pin 72 against the beam-like structure 26 by having the roller 70 roll onto an inclined surface 104 provided on the lever arm 84 of the shaft link 82.
  • the aperture 68 in the linkage members 64 that receive pin 72 of the roller 70 are oblong so that the roller 70 can adjust to the angle of the inclined surface 104 while allowing the pin 72 to maintain its linear path along the elongated guide slot 28.
  • the inclined surface 104 provides a ramp by which the roller 70 may engage and roll onto when the rotary clamp 10 is moving in and out of the clamped position.
  • the inclined surface 104 is formed such that as the landing 104 moves away from the pivot pin 92 and toward the lever arm 84 , the landing 104 rises 5° to 6° relative to a horizontal axis 113, as indicated by 112 in Fig. 6.
  • the landing 104 then transforms to a slightly downward portion 114 that extends at a -1° angle relative to the horizontal axis 113 , as seen in Fig. 7. As the landing 104 moves toward the end of the lever arm 84 , the landing 104 begins to rise again at a 7° angle relative to the horizontal axis 113 , as shown by 116 in Fig. 8. The last raised portion 116 of the inclined surface 104 assures that the piston rod 16 will wedge the roller 70 between the inclined surface 104 and the wear surface of the beam-like structure 26 by driving the pin 72 into the beam-like structure 26 and rolling the roller 70 up the inclined surface 104 to provide the clamp 10 with a tight fit in the clamped position.
  • the landing 104 may also provide an additional raised portion of a 15° to 16° angle relative to the horizontal axis 113 at the end of the lever arm 84 to assure that the roller 70 will wedge the pin 72 into the wear surface of the beam-like structure 26 regardless of the wear on the roller 70.
  • the different angles on the inclined surface 104 assure that rotary clamp 10 will not become unclamped when the clamp 10 is backdriven. If the rotary clamp 10 is backdriven, such as in the case of loss of power and/or air or an attempt to manually open the clamp 10, the roller 70 may "relax" or roll down section 116 of the inclined surface 104 and stop and hold at section 114.
  • the upward angle of section 114 in combination with the angles of the linkage assembly 17, creates actuation forces that prohibit the clamp 10 from moving toward the unclamped position.
  • a means for resisting movement of the linkage assembly 17 is provided within the rotary clamp 10 to ensure that the roller 70 does not roll toward the unclamped position when power is lost to the rotary clamp 10 .
  • the means for resisting movement provides a back lock plunger 118 having a spring detent therein, as most clearly shown in Fig. 4A.
  • the back lock plunger 118 has an open-ended cylindrical body 120 disposed within an aperture provided in the downwardly declining portion 114 of the inclined surface 104 of the lever arm 84 of the shaft link 82 .
  • the cylindrical body 120 has a compression spring 122 and a spherical ball or roller 124 disposed therein.
  • the spherical roller 124 is partially disposed within the cylindrical body 120 as the compression spring 122 biases the spherical roller 124 toward the open end of the cylindrical body 120.
  • a lip or shoulder on the end of the cylindrical body 120 captures and holds the spherical roller 124 within the body 120.
  • the spherical roller 124 extends just above the inclined surface 114 of the lever arm 84 of the shaft link 82 to provide a bias against the roller 70 from moving toward the unclamped position. When enough force is applied to the roller 70 , the spherical roller 124 will yield to the compression spring 122 by receding within the cylindrical body 120 thereby allowing the roller 70 to pass over the back-lock plunger 118.
  • the means for resisting movement of the linkage assembly provides a spring roller guide 106 mounted to two of the dowel pins 30 utilized to connect the plates 24 and beams 26 to the housing 18 of the rotary clamp 10, as seen in Fig. 4B.
  • the spring roller guide 106 is a thin sheet of bent metal that is connected to and extends between the two dowel pins 30. The spring roller guide 106 engages the roller 70 so as to bias the roller 70 against the tapered landing 104 of the lever arm 84 when the roller 70 engages the spring roller guide 106.
  • the rotary clamp 10 starts in the unclamped position with the piston rod 16 fully retracted in the linear actuator 12 .
  • the linear actuator 12 When the linear actuator 12 is actuated, the piston rod 16 extends into the housing 18 of the rotary clamp 10 and drives the pins 72 along the elongated guide slot 28 of the housing 18 .
  • the linkage assembly 17 converts the linear actuator motion of the piston rod 16 into rotary motion of the clamp arm 20 toward the clamped position.
  • the roller 70 engages the first portion 112 of the inclined surface 104 of the lever arm 84 and begins to drive the pins 72 upward into the wear surfaces of beams 26 creating a wedging effect with the roller 70, as seen in Fig. 6.
  • the linkage angle ⁇ is before center and is effectively made with the pivotal axes 108, 109 of links 76 and a vertical axis 110 .
  • the piston rod 16 continues to drive the roller 70 along the second and third portions 114, 116 of the inclined surface 104 of the shaft link 82 , as seen in Figs. 7-8.
  • the toggle links 76 rest in an over-center position, that is, the pivotal axis 109 extends beyond the vertical axis 110 .
  • This over-center linkage angle is identified as ⁇ '.
  • the over-center positioning of the toggle links 76 may occur without wear to the linkage assembly 17 because pins 72 engage the wear surface of the beam-like structure 26, and roller 70 engages the inclined surface 104 of shaft link 82 to drive pins 72 into the wear surface of the beam-like structure 26. This relieves toggle links 76 from any actuation forces, and places the actuation forces on pins 72 and roller 70.
  • the center axis 111 of the roller 70 in relation to the pivoting axis 108 of link 76 provides an angle ⁇ that does not extend beyond the vertical axis 110 .
  • the linkage assembly 17 is allowed to obtain an over-center position without realizing the excessive force which typically leads to excessive wear in similar linkage assemblies.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jigs For Machine Tools (AREA)
EP01306592A 2000-08-03 2001-08-01 Dispositif motorisé de serrage autobloquant avec mécanisme à genouillère Withdrawn EP1179394A3 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US22255600P 2000-08-03 2000-08-03
US222556P 2000-08-03
US23760200P 2000-10-03 2000-10-03
US237602P 2000-10-03
US09/891,916 US6557841B2 (en) 2001-06-26 2001-06-26 Over-center power clamp toggle mechanism
US891916 2001-06-26

Publications (2)

Publication Number Publication Date
EP1179394A2 true EP1179394A2 (fr) 2002-02-13
EP1179394A3 EP1179394A3 (fr) 2003-08-27

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Application Number Title Priority Date Filing Date
EP01306592A Withdrawn EP1179394A3 (fr) 2000-08-03 2001-08-01 Dispositif motorisé de serrage autobloquant avec mécanisme à genouillère

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EP (1) EP1179394A3 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20205994U1 (de) 2002-04-16 2002-08-08 DE-STA-CO Metallerzeugnisse GmbH, 61449 Steinbach Kniehebelspannvorrichtung
FR2839914A1 (fr) * 2002-03-08 2003-11-28 Tunkers Maschb Gmbh Dispositif de serrage pour un levier articule
EP1371452A3 (fr) * 2002-06-13 2004-03-03 DE-STA-CO Metallerzeugnisse GmbH Dispositif de serrage à genouillère
EP1382860A3 (fr) * 2002-07-15 2005-04-27 Delaware Capital Formation, Inc. Verrouillage pour un vérin
FR2871715A1 (fr) * 2004-06-22 2005-12-23 Robotic Sa Dispositif de serrage d'une piece de construction a usiner
DE102004056229A1 (de) * 2004-11-22 2006-05-24 Günter Neumann GmbH Kraftspanner
CN102666023A (zh) * 2009-10-09 2012-09-12 De-Sta-Co欧洲有限责任公司 夹紧设备
EP3130809A1 (fr) 2015-08-13 2017-02-15 Pneumax S.p.A. Unité d'actionnement d'efficacité optimisée du type de levier articulé

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0596808B1 (fr) * 1992-11-05 1996-02-28 Martin Breiter Tête de bridage
US5575462A (en) * 1994-08-17 1996-11-19 Blatt; John A. Rotary clamp for a linear actuator
US5884903A (en) * 1995-10-30 1999-03-23 Btm Corporation Powered clamp and gauging apparatus
DE19751950C1 (de) * 1997-11-24 1999-03-04 Isi International Sa Kniehebelspannvorrichtung, insbesondere zur Verwendung im Karosseriebau der Kfz-Industrie

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2839914A1 (fr) * 2002-03-08 2003-11-28 Tunkers Maschb Gmbh Dispositif de serrage pour un levier articule
DE20205994U1 (de) 2002-04-16 2002-08-08 DE-STA-CO Metallerzeugnisse GmbH, 61449 Steinbach Kniehebelspannvorrichtung
EP1371452A3 (fr) * 2002-06-13 2004-03-03 DE-STA-CO Metallerzeugnisse GmbH Dispositif de serrage à genouillère
EP1382860A3 (fr) * 2002-07-15 2005-04-27 Delaware Capital Formation, Inc. Verrouillage pour un vérin
FR2871715A1 (fr) * 2004-06-22 2005-12-23 Robotic Sa Dispositif de serrage d'une piece de construction a usiner
US7213804B2 (en) 2004-06-22 2007-05-08 Robotic Sa Chucking device of a part of construction to be machined
DE102004056229A1 (de) * 2004-11-22 2006-05-24 Günter Neumann GmbH Kraftspanner
CN102666023A (zh) * 2009-10-09 2012-09-12 De-Sta-Co欧洲有限责任公司 夹紧设备
CN102666023B (zh) * 2009-10-09 2015-03-11 De-Sta-Co欧洲有限责任公司 夹紧设备
EP3130809A1 (fr) 2015-08-13 2017-02-15 Pneumax S.p.A. Unité d'actionnement d'efficacité optimisée du type de levier articulé
EP3130809B1 (fr) 2015-08-13 2023-08-02 Pneumax S.p.A. Unité d'actionnement d'efficacité optimisée du type de levier articulé

Also Published As

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