EP0622873A2 - Stössel Antriebsmechanismus - Google Patents

Stössel Antriebsmechanismus Download PDF

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Publication number
EP0622873A2
EP0622873A2 EP94301841A EP94301841A EP0622873A2 EP 0622873 A2 EP0622873 A2 EP 0622873A2 EP 94301841 A EP94301841 A EP 94301841A EP 94301841 A EP94301841 A EP 94301841A EP 0622873 A2 EP0622873 A2 EP 0622873A2
Authority
EP
European Patent Office
Prior art keywords
ram
pin
link
drive
crimp height
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.)
Ceased
Application number
EP94301841A
Other languages
English (en)
French (fr)
Other versions
EP0622873A3 (de
Inventor
William Herbert Bair
Kenneth Foster Folk
David Anthony Skotek
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.)
Whitaker LLC
Original Assignee
Whitaker LLC
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 US08/053,875 external-priority patent/US5408860A/en
Application filed by Whitaker LLC filed Critical Whitaker LLC
Publication of EP0622873A2 publication Critical patent/EP0622873A2/de
Publication of EP0622873A3 publication Critical patent/EP0622873A3/de
Ceased legal-status Critical Current

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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
    • H01R43/00—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors
    • H01R43/04—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors for forming connections by deformation, e.g. crimping tool
    • H01R43/048—Crimping apparatus or processes
    • H01R43/0488—Crimping apparatus or processes with crimp height adjusting means
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
    • H01R43/00—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors
    • H01R43/04—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors for forming connections by deformation, e.g. crimping tool
    • H01R43/048—Crimping apparatus or processes

Definitions

  • the present invention relates to a machine for crimping electrical terminals to conductors and, in particular, to a ram drive linkage for an automated terminal crimping machine and an adjustable pin for the ram drive linkage thereby allowing selection of the proper crimp height.
  • FIGs. 1 and 2 are side and front views, respectively, of one exemplary automatic crimping "T-terminating unit" Model No. 768793 which is commercially available from AMP, Incorporated.
  • Such presses include a reciprocating ram group 1 which is driven by an electric motor 3 through a torque multiplication mechanism 5.
  • Various crimping tool-heads may be secured to the underside of ram group 1, and the attached tool head is driven with the ram group into proximity with a continuous-feed applicator 8, which tenders the terminals to be crimped.
  • crank shaft is rotatably seated in the upper section of the press and runs to the front of the press.
  • An offset crank pin 2 protrudes forwardly from an end face of the crank shaft. The crank pin 2 is offset from the rotation axis of the crank shaft and orbits about the axis as the crank shaft is rotated.
  • the conventional automatic crimping presses are of a push link design wherein the crank pin 2 is directly coupled to a push link 6, which is in turn coupled to a ram 20 through a ball joint and socket 11.
  • the crank pin 2 compresses the push link 6 and ram 20 downwardly during 180° of its orbit to advance the entire ram group 1 and crimping tool head toward the applicator 8.
  • This illustrated press and its commercial counterparts do not allow convenient adjustment of the crimp height to compensate for such things as tooling wear, dimensional tolerances of replacement parts, and dimensional changes due to temperature variations.
  • the current configuration of the ram group 1 renders it difficult to incorporate a suitable retrofit adjustment feature.
  • the ram group 1 is reciprocated over a distance equal to a stroke length of the crank pin 2 which may be, for example, 1.625"
  • the terminals are crimped in a crimping zone which extends only over a final portion of the downward displacement of the ram group, i.e., the final 0.1" of the downward displacement.
  • Force required to displace the ram group 1 is relatively low except during actual crimping of the terminal, when forces on the order of several thousand pounds are required to deform the terminal.
  • a greater mechanical advantage of the ram drive could be achieved by extending the portion of rotation of the crank pin 2 during which actual crimping occurs, thereby reducing a size requirement for the motor 3.
  • the existing push link design tends to produce a majority of the downward ram displacement during the final 90° of downward rotation of the crank pin, as shown by a plot of ram displacement versus crank pin rotation in Figure 6.
  • the plot of ram displacement versus crank pin rotation can be altered by altering the length of the push link, but at best, the push link design can only be made to produce an equal displacement of the ram during the initial 90° of crank pin downward rotation and the final 90° of crank pin downward rotation, i.e., a pure sinusoidal motion.
  • the present invention accomplishes this by employing a tensioned linkage to pull the ram downward rather than compressive force on a push link.
  • the present invention also facilitates the OEM or retrofit addition of a crimp height adjustment feature.
  • a ram drive mechanism including a drive shaft having an offset drive member at one end which orbits about an axis of the drive shaft during rotation thereof. Means such as an electric motor are provided for rotating the crank shaft.
  • a ram is mounted for reciprocating motion in a first direction toward a crimping zone and in a second direction away from the crimping zone.
  • a drive link has one end pivotally connected to the drive member and an other end coupled to the ram for reciprocating the ram in accordance with the orbiting of the drive member.
  • the ram is arranged such that the one end of the drive link is disposed relatively further in the first direction than the other end of the drive link.
  • the drive link is in tension during the reciprocation of the ram toward the crimping zone.
  • This pull link arrangement increases the angle of crank shaft rotation that is available for moving the ram when the ram is in the crimping zone, thereby increasing force concentration on the ram in the crimping zone.
  • a portion of the ram defines a cavity bounded by walls, and the ram carries a link pin which extends through the cavity and is supported by opposite ones of the walls.
  • An aperture extends from the cavity through one of the opposite walls.
  • the drive member comprises a crank pin extending from the one end of the crank shaft through the aperture.
  • the drive link is disposed within the cavity, and the one end of the drive link defines a bore which receives the crank pin therein.
  • a ram drive mechanism for an automated terminal crimping machine comprising a crank shaft having an offset drive member at one end which orbits about an axis of the crank shaft during rotation thereof; means for rotating the crank shaft; a ram mounted for reciprocating motion in a first direction toward a crimping zone and in a second direction away from the crimping zone; and a drive link having one end pivotally connected to the drive member and an other end coupled to the ram for reciprocating the ram in accordance with the orbiting of the drive member the ram is arranged such that the one end of the drive link is disposed relatively further in the first direction than the other end of the drive link, whereby the drive link is in tension during the reciprocation of the ram toward the crimping zone.
  • the "T-terminating unit" Model No. 768793 of FIGS. 1 and 2 has an existing crimp height adjustment mechanism.
  • Crimp height refers to the vertical height of a terminal after it has been crimped in the press.
  • the crimp height is a function of the shut height of the press, i.e., a dimension between upper and lower crimping tooling when the ram 20 is at a lowermost extent of its stroke.
  • the lower crimping tooling toward which the attached tool head is driven sits upon a precision adjustment base 12.
  • the precision adjustment base 12 may be offset vertically by turning adjustment knob 13, and changing the offset of the base 12 and lower crimping tooling results in a change in crimp height.
  • adjustment mechanism including adjustment base 12, knob 13, and all components in between are complex and precision machined parts.
  • the complexity of the mechanism renders it strictly OEM, and it cannot be offered as a retrofit feature. More importantly, the complexity unduly elevates the cost of the "T-terminating unit".
  • the mechanism lies beneath the work area and is susceptible to clogging by dirt and debris.
  • the present invention also provides an improved crimp height adjustment mechanism to be carried within a reciprocating ram of an automated terminal crimping machine as set forth herein for adjusting the crimp height thereof.
  • the crimp height adjustment mechanism of the present invention includes a cylindrical crimp height adjustment pin carried by the reciprocating ram of the crimping machine.
  • the crimp height adjustment pin has an eccentric intermediate section which is coupled in a bearing engagement with the drive linkage of the crimping machine.
  • a rotator is attached to the crimp height adjustment pin for allowing controlled rotation of the eccentric intermediate section. By controlling rotation of the eccentric intermediate section of the crimp height adjustment pin (via the rotator), the ram may be vertically offset to thereby adjust the crimp height of the machine.
  • the rotator may be a simple manual adjustment arm attached to the crimp height adjustment pin exteriorly of the ram for allowing leveraged rotation of the adjustment pin.
  • the rotator may be an automatic assembly such as a first rotary gear attached to the crimp height adjustment pin exteriorly of the ram, a shaft having a worm gear at one end for engagement with the first rotary gear, and an electric motor mounted independently of the ram and engaged with the other end of the shaft for imparting rotation thereto to thereby rotate the eccentric section of the pivot pin.
  • the invention provides for convenient "on-the-fly" adjustment of the crimp height of terminals crimped in the machine.
  • FIGS. 1 and 2 illustrate an existing automatic crimping "T-terminating unit" Model No. 768793 which is commercially available from AMP, Incorporated.
  • the press includes a ram group 1 including a reciprocating ram 20 which is driven by an electric motor 3 through a torque multiplication mechanism 5.
  • a crank shaft is rotatably seated in an upper section of the press for transferring motion from the torque multiplication mechanism 5 to the ram group 1.
  • Various crimping tool-heads may be secured to the underside of the ram 20, and the attached tool head is driven downward by the ram 20 into working proximity with a continuous-feed terminal applicator 8 which positions terminals to be crimped.
  • FIG. 3 is an exploded perspective view of the ram drive mechanism of the present invention incorporated in the automatic terminal crimping machine shown in FIGS. 1 and 2.
  • the crank shaft 10 in FIG. 3 extends to a front of the press, and drive member 2 protrudes forwardly from the end face of the crank shaft.
  • the drive member 2 is a crank pin which is offset from a rotation axis of the crank shaft and orbits about the axis as the crank shaft rotates.
  • other equivalent configurations for the drive member 2 such as an offset bore defined in the end face of the crank shaft 10, will be readily apparent to those skilled in the art, and the drive member 10 is intended to include all equivalent configurations without limitation to this embodiment.
  • the ram drive mechanism of the present invention includes a modified ram 20 which is formed as a hollow block with flanged edges 22 on either side. An interior of the hollow block defines a cavity 24.
  • the ram 20 is received within channel 16 defined between side rails 14 of the press.
  • the ram 20 is held captive within the channel 16 by a pair of gibs 30 which are secured to the side rails 14 of the press by threaded fasteners 32.
  • the edges 22 are slidably held behind the gibs 30 to permit vertical sliding movement of the ram 20.
  • a back wall 26 of the ram 20 defines an aperture 38, shown in FIG. 4, which provides an opening through which the crank pin 2 extends into the cavity 24.
  • the aperture 38 is sufficiently large to provide clearance for unobstructed orbiting of the crank pin 2 therein.
  • a drive link 40 comprises an integral member having a lower bore 42 at one end and an upper bore 44 at an other end.
  • the drive link 40 resides in the cavity 24 of the ram 20.
  • the crank pin 2 protrudes through the aperture 38 (Fig. 8) and is pivotally received in the lower bore 42 of the drive link 40. From the pivotal connection with the crank pin 2, the drive link 40 extends upwardly within the cavity 24.
  • the back wall 26 and front wall 28 of the ram 20 define through-bores 46, 48, respectively, at positions which correspond to the upper bore 44 of the drive link 40.
  • a link pin 50 is pivotally received in the upper bore 44 of the drive link 40 and is secured within the bores 46, 48 of the ram 20.
  • the link pin 50 provides a pivotal connection of the drive link 40 to the ram 20.
  • the ram drive linkage of the present invention includes a first, or lower, pivotal connection between the crank pin 2 and the drive link 40 via the crank pin 2 nesting in the lower bore 42, and a second, or upper, pivotal connection between the ram 20 and drive link 40 via the link pin 50 nesting in the upper bore 44.
  • crank shaft 10 In operation, rotation of the crank shaft 10 effects an orbiting motion of the crank pin 2 about a rotation axis of the crank shaft 10.
  • Each orbit of the crank pin 2 produces both a side-to-side displacement and a vertical displacement of the crank pin 2.
  • the side-to-side component is absorbed by the drive link 40 which simply pivots back and forth in a pendulum motion. Hence, the side-to-side component generates no motion of the ram 20.
  • crank pin 2 The vertical displacement component of the crank pin 2 is translated directly into a vertical reciprocating motion of the ram 20.
  • the drive link 40 is compressed against the link pin 50, which in turn slides the ram 20 upwardly between the rails 30.
  • downward displacement of the crank pin 2 tensions the drive link 40 and pulls the ram 20 downwardly between the side rails 14. It is this downward reciprocation of the ram 20 which results in a crimping blow against a terminal supported on lower crimping tooling on a base of the press.
  • FIG. 6 graphically illustrates ram displacement as a function of crank shaft angle in a "T Terminator” press having the prior art push link design, and in a “G Terminator” press having a pull link ram drive mechanism according to the invention.
  • the "T Terminator” produces a ram displacement wherein a greater portion of the ram movement occurs in the final 90° of crank shaft rotation than in the initial 90° of crank shaft rotation.
  • the ram dwells in the "crimp zone", i.e., the final 0.1" of ram displacement, for approximately 28° of the crank shaft rotation.
  • the "G Terminator” produces approximately two-thirds of the ram downward displacement in the initial 90° of crank shaft rotation. Thereafter, the ram continues downward at a slower rate than the comparable ram on the "T Terminator".
  • the ram enters the crimp zone approximately 43° before bottom dead center of the crank shaft rotation, thereby providing an increased dwell time in the crimp zone and increased force transmission through the ram for acting against the terminal.
  • moving parts of the ram drive linkage are contained behind the ram 20 and are shielded thereby for the safety of the operator.
  • the use of the above-described ram drive linkage according to the present invention facilitates the use of a crimp height adjustment feature to compensate for tolerances in the tool heads, terminal pins, etc.
  • the crimp height can be easily adjusted by varying the vertical separation d between the first pivotal connection with the crank pin 2, and the second pivotal connection with the link pin 50.
  • the link pin 50 includes an eccentric, and the crimp height can be adjusted by rotatably adjusting the link pin 50 in the manner shown and described in conjunction with FIGS. 7-14.
  • the extent of the downward reciprocation is related to a distance D between an axis of the crimp height adjustment pin 50 and its point of bearing contact with the drive link 40 during the downward reciprocation.
  • the drive link 40 is in tension and the point of bearing contact between the adjustment pin 50 and the drive link 40 is on the upper side of the adjustment pin 50 (as viewed in FIG. 10) along an imaginary line 36 which intersects central axis 59 of the adjustment pin 50 and central axis 15 of the crank pin 2 as the crank pin 2 rotates.
  • the line 36 is vertical and the point of bearing contact is at a top point of the adjustment pin 50 (as viewed in FIG. 10).
  • the crimp height adjustment pin 50 of the present invention allows convenient adjustment of the distance D in the following manner.
  • FIG. 13 is an enlarged side view of the crimp height adjustment pin 50 showing details of its design.
  • the crimp height adjustment pin 50 defines a three-tier shaft having a first cylindrical section 51 of relatively small diameter, a second cylindrical section 52 of intermediate diameter, and a third cylindrical section 53 of larger diameter.
  • the third section 53 is coaxial with the first section 51 on the pin axis 59.
  • the intermediate section 52 has a central axis 55 which is parallel to and displaced from the pin axis 59.
  • the intermediate section 52 is eccentric with respect to the pin axis 59.
  • the axis 55 of the intermediate section 52 is displaced from the pin axis 59 by an eccentric dimension E which is .010 inch.
  • the crimp height adjustment pin 50 is disposed in the ram 20 such that the first section 51 is pivotally seated in the bore 46 in the back wall 26 of the ram 20, and the third section 53 is pivotally seated in the bore 48 in the front wall 28 of the ram 20. End face 66 of the intermediate section 52 bears against the back wall 26 and prevents travel of the pin 50 through the back wall of the ram.
  • the intermediate section 52 resides in the upper bore 44 of the drive link 40 within the cavity 24 of the ram 20.
  • the drive link 40 is held captive on the crimp height adjustment pin 50 between the front and back walls 28, 26 of the ram, the link 40 being in bearing contact with the intermediate section 52 of the pin 50.
  • a radial length of the intermediate section 52 defines the distance D. More specifically, the distance D is equal to a distance between the pin axis 59 (as defined by the coaxial first and third sections 51 and 53) and a point of bearing contact between the drive link 40 and the intermediate section 52. Since the intermediate section 52 is eccentric with respect to the pin axis 59, rotation of the pin 50 on its axis 59 produces a change in the distance D, thereby changing the shut height of the press and the crimp height of a terminal crimped therein. The intermediate section 52 may be selectively rotated by, for example, rotation of the entire pin 50 to thereby change the distance D between the axis 59 and the periphery of the intermediate section 52. Hence, the maximum downward extent of the ram 20 (and thus, the crimp height) may be altered by altering the angular orientation of the pin 50.
  • a grease fitting 83 is preferably provided to allow convenient lubrication.
  • the grease fitting 83 is attached to the crimp height adjustment pin 50 which has a central passageway 68 therethrough to allow injection of grease.
  • the grease flows along the passageway 68 and is expelled through a port 57 into a grease groove 56 around the periphery of the intermediate section 52, thereby providing lubrication for the upper pivotal connection of the drive link 40.
  • Some of the grease is further communicated through a passageway 43 (FIG. 9) in the drive link 40 and is expelled at the lower bore 42, thereby providing lubrication for the lower pivotal connection of the drive link 40 with the crank pin 2, all from the front of the press.
  • a means for rotating the adjustment pin 50 is provided by rotator handle 80 which is attached to the adjustment pin 50 in front of the ram 20.
  • One end of the rotator handle 80 has a throughbore 84 (FIGS. 9 and 11) which receives stem 54 of the adjustment pin 50.
  • a setscrew 88 is engaged in cavity 74 (FIG. 13) in the stem 54 to lock the rotator handle 80 to the adjustment pin 50.
  • the rotator handle 80 allows manual rotation of the adjustment pin 50 in order to selectively position the eccentric intermediate portion 52 at various orientations for performing crimp height adjustments. Consequently, a machine operator may reorient the crimp height adjustment pin 50 to thereby change the maximum downward displacement achievable by the ram 20 (i.e., the crimp height).
  • the rotator handle 80 has a length which extends from the pin 50 to provide sufficient leverage for rotating the pin 50 so as to lift the ram 20 when an increased crimp height is desired.
  • the crimp height adjustment pin 50 is secured within ram 20 by a face plate 70 which is attached to the front wall 28 of the ram.
  • the face plate 70 has an aperture 76 through which the stem 54 of the adjustment pin 50 protrudes.
  • the aperture 76 has a smaller diameter than the third section 53, thus preventing withdrawal of the pin 50 through the front wall 28 when the face plate 70 is secured thereto.
  • the orbiting crank pin 2 of the crank shaft protrudes into ram 20 and is pivotally engaged within the lower bore 42 of the drive link 40.
  • the upper bore 44 of the drive link 40 encircles the intermediate section 52 of the crimp height adjustment pin 50. All vertical displacement of the crank pin 2 is conveyed directly through the drive link 40 to generate the vertical reciprocations of the ram 20.
  • the crank pin 2 tensions the drive link 40 and pulls the ram 20 downwardly within the rails 30.
  • This downward reciprocation of the ram 20 terminates in a crimping blow, and the extent of the downward reciprocation defines the crimp height.
  • the downward extent is a function of the distance D between the axis of the crimp height adjustment pin 50 and its point of bearing contact with the drive link 40.
  • the rotator handle 80 extends perpendicularly with respect to the crimp height adjustment pin 50 and along a front face of the ram 20.
  • a positive detent means for releasably holding the handle 80 in a selected angular orientation is provided by a detent pin 82 located at an end of the handle 80 which cooperates with a series of recesses 72 defined along an outer periphery of the face plate 70, the recesses 72 being arranged along the arcuate swing path of the detent pin 82.
  • a spring 86 in the end of handle 80 biases the detent pin 82 radially inwardly to keep the detent pin 82 within one of the recesses 72.
  • a finger grip portion 64 connected to the detent pin 82 is operable to move the detent pin radially outwardly to disengage the detent pin from the recesses so that the handle 80 can be selectively rotated to adjust the crimp height.
  • the detent pin 82 and the recesses 72 cooperate to provide a means for making precise incremental adjustments in crimp height and for retaining the selected crimp height until further adjustment is desired. Due to the configuration of the eccentric intermediate portion 52 of the pin 50, constant angular increments of rotation of the pin 50 result in varying incremental changes in crimp height. It is preferred that the detent means provide constant incremental changes in crimp height between each detent.
  • the recesses 72 are spaced at non-uniform distances along the arcuate swing path of the detent pin 82 such that moving the detent pin 82 between two adjacent ones of the recesses 72 effects a constant incremental change in crimp height which, in an embodiment preferred by applicants, is .0005 inch.
  • the handle 80 may be attached to the pin 50 such that the handle 80 extends in a direction which is angularly offset with respect to maximum eccentricity of the intermediate portion 52. It is preferred that the handle 80 be attached to the pin 50 such that when the handle 80 is disposed midway along its arcuate swing path as shown in FIG. 12, the press will produce a nominal crimp height midway between the maximim and minimum extremes of its adjustable range. As seen in FIG. 12, the apertures 72 are disposed over an approximately 130° range of the arcuate swing path of the handle 80. If desired, the arcuate swing path could be expanded to extend over a 180° range, thereby utilizing the entire range of crimp height adjustment available from the pin 50 having a fixed eccentric dimension E.
  • FIG. 15 illustrates an alternative embodiment for rotating the adjustment pin 50 in order to accomplish adjustment of the crimp height.
  • a first rotary gear 90 is attached to crimp height adjustment pin 50 exteriorly of the ram 20.
  • a pair of integral mounting brackets 92 are provided on the ram 20 adjacent the first rotary gear 90.
  • the mounting brackets 92 hold first worm gear 93 on shaft 94 in engagement with the first rotary gear 90.
  • the shaft 94 extends transversely with respect to the crimp height adjustment pin 50 and upward past the mounting brackets 92.
  • a second rotary gear 96 is mounted on an upper end of the shaft 94.
  • An actuating motor 98 seated within the terminal crimping press has a motor shaft connected to second worm gear 97 which engages the second rotary gear 96.
  • the motor 98 may be any conventional motor including a stepping motor, which would allow incremental angular adjustment of the adjustment pin 50. Operation of the motor 98 turns the shaft 94, which in turn rotates the first rotary gear 90 as well as the crimp height adjustment pin 50. Using the embodiment of FIG. 15, adjustment of the crimp height may be accomplished automatically.

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  • Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Press Drives And Press Lines (AREA)
  • Manufacturing Of Electrical Connectors (AREA)
EP94301841A 1993-04-26 1994-03-15 Stössel Antriebsmechanismus. Ceased EP0622873A3 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US5288193A 1993-04-26 1993-04-26
US53875 1993-04-26
US08/053,875 US5408860A (en) 1993-04-26 1993-04-26 Ram drive mechanism having a pivoted drive link
US52881 1993-04-26

Publications (2)

Publication Number Publication Date
EP0622873A2 true EP0622873A2 (de) 1994-11-02
EP0622873A3 EP0622873A3 (de) 1996-03-27

Family

ID=26731204

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94301841A Ceased EP0622873A3 (de) 1993-04-26 1994-03-15 Stössel Antriebsmechanismus.

Country Status (4)

Country Link
EP (1) EP0622873A3 (de)
JP (1) JPH076848A (de)
CN (2) CN1035221C (de)
BR (1) BR9401537A (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998002943A1 (en) * 1996-07-15 1998-01-22 The Whitaker Corporation Two stage press
WO1998024158A1 (en) * 1996-11-26 1998-06-04 The Whitaker Corporation Apparatus for terminating electrical wires
EP0889561A1 (de) * 1997-06-30 1999-01-07 komax Holding AG Krimpvorrichtung und Verfahren zu deren Betrieb
EP0889560A1 (de) * 1997-06-30 1999-01-07 komax Holding AG Verfahren und Vorrichtung zur Überführung von Kontakten zu einer Kontaktverarbeitungsstation
EP1383212A1 (de) * 2002-07-17 2004-01-21 Bernhard Schäfer Werkzeug- u. Sondermaschinen GmbH Verfahren und Vorrichtung zur Qualitätssicherung von Crimpverbindungen
EP2062724A3 (de) * 2007-11-23 2012-07-11 Schäfer Werkzeug- und Sondermaschinenbau GmbH Crimppresse mit einer um eine Achse rotierbaren Exzenterwelle
CN108480959A (zh) * 2018-05-07 2018-09-04 珠海大利刀具有限公司 一种齿轮驱动销自动压入机
CN112688141A (zh) * 2020-12-14 2021-04-20 无锡爱思通科技有限公司 一种闭合高度可调压接机

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ITMI20051149A1 (it) * 2005-06-17 2006-12-18 Mecal Srl Mazza di tipo perfezionato per dispositivi aggraffatura
CN101976792B (zh) * 2010-10-30 2012-07-04 苏州华旃航天电器有限公司 一种用于接触件上导线装配的压接治具
CN103855589A (zh) * 2012-11-28 2014-06-11 丹阳市飞越车辆附件有限公司 一种端子机的端子润滑装置
CN110247285B (zh) * 2019-07-10 2024-05-31 旭东机械(昆山)有限公司 一种自动压接装置

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US2426155A (en) * 1942-08-04 1947-08-19 Bliss E W Co Increment press
US4138904A (en) * 1977-07-20 1979-02-13 Verson Allsteel Press Company Link drive mechanism for mechanical presses
EP0378514A2 (de) * 1989-01-13 1990-07-18 Dieter Kurt Eich Anschlagpresse
EP0505026A2 (de) * 1991-03-19 1992-09-23 Aida Engineering Ltd. Stösselantriebsvorrichtung für eine Presse

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DE2231579C3 (de) * 1972-06-28 1981-10-01 Eumuco AG für Maschinenbau, 5090 Leverkusen Schmiedepresse, insbesondere Gesenkschmiedepresse

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2426155A (en) * 1942-08-04 1947-08-19 Bliss E W Co Increment press
US4138904A (en) * 1977-07-20 1979-02-13 Verson Allsteel Press Company Link drive mechanism for mechanical presses
EP0378514A2 (de) * 1989-01-13 1990-07-18 Dieter Kurt Eich Anschlagpresse
EP0505026A2 (de) * 1991-03-19 1992-09-23 Aida Engineering Ltd. Stösselantriebsvorrichtung für eine Presse

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998002943A1 (en) * 1996-07-15 1998-01-22 The Whitaker Corporation Two stage press
US6192733B1 (en) 1996-07-16 2001-02-27 Alden Owen Long Two stage press
WO1998024158A1 (en) * 1996-11-26 1998-06-04 The Whitaker Corporation Apparatus for terminating electrical wires
EP0889561A1 (de) * 1997-06-30 1999-01-07 komax Holding AG Krimpvorrichtung und Verfahren zu deren Betrieb
EP0889560A1 (de) * 1997-06-30 1999-01-07 komax Holding AG Verfahren und Vorrichtung zur Überführung von Kontakten zu einer Kontaktverarbeitungsstation
US6067828A (en) * 1997-06-30 2000-05-30 Komax Holding Ag Crimping apparatus
EP1383212A1 (de) * 2002-07-17 2004-01-21 Bernhard Schäfer Werkzeug- u. Sondermaschinen GmbH Verfahren und Vorrichtung zur Qualitätssicherung von Crimpverbindungen
EP2062724A3 (de) * 2007-11-23 2012-07-11 Schäfer Werkzeug- und Sondermaschinenbau GmbH Crimppresse mit einer um eine Achse rotierbaren Exzenterwelle
CN108480959A (zh) * 2018-05-07 2018-09-04 珠海大利刀具有限公司 一种齿轮驱动销自动压入机
CN112688141A (zh) * 2020-12-14 2021-04-20 无锡爱思通科技有限公司 一种闭合高度可调压接机

Also Published As

Publication number Publication date
CN1035221C (zh) 1997-06-18
CN1160298A (zh) 1997-09-24
EP0622873A3 (de) 1996-03-27
CN1094542A (zh) 1994-11-02
BR9401537A (pt) 1994-11-22
JPH076848A (ja) 1995-01-10

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