• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention in question relates to crimpers for attaching a shrunken contact with a cable, the cable conductor and cable insulation are attachable to the crimped contact by means of crimping pliers arranged on a press conductor and the press conductor, which can be driven by a press motor . The invention relates in particular to the drive mechanisms of the press carriage with improved control of the press guide. In the drive mechanism of the press carriage of the invention in question, the rotational movement of the electric motor is converted to a linear displacement of the press carriage by a first cam mounted on a rotating cam shaft, a second cam disposed at one end of the press carriage, means for keep the second cam in contact with the first cam during rotation and wherein one of said cams is eccentric.
    公开号:BE1025451B1
    申请号:E20140646
    申请日:2014-08-28
    公开日:2019-03-01
    发明作者:Steven Aerts；Tom Gomme
    申请人:Exmore Group Nv；
    IPC主号:
    专利说明:

    CRIMPERS
    FIELD OF THE INVENTION
    The invention in question relates to crimpers for attaching a crimped contact with a cable, the cable guide and cable insulation are attachable to the crimped contact by means of crimping pliers arranged on a press guide and the press guide, which can be driven by a press motor . The invention relates in particular to the drive mechanisms of the press carriage with improved control of the press guide. In the drive mechanism of the press carriage of the invention in question, the rotational movement of the electric motor is converted to a linear displacement of the press carriage by a first cam mounted on a rotating cam shaft, a second cam disposed at one end of the press carriage, means for keep the second cam in contact with the first cam during rotation and wherein one of said cams is eccentric.
    BACKGROUND OF THE INVENTION
    Automatic crimping presses have long been used in the connector industry to perform super-fast mass termination of various cables, such as in the areas of electronics, telecommunications and automotive electronics. In the crimping process, the connection is produced by the applied pressure, the force-time curve generated by the press having to match the crimping profile required to generate an optimum crimp for a particular cable conductor and crimped contact. If the actual curve deviates from the intended curve, the crimp connection will show defects and must be separated from the production process.
    The drive mechanisms of the press carriage of conventional crimping presses, as shown for example in figures 1 and 2, are of a pressure coupling design, wherein a crank pin 2 is connected to the press carriage 20, either by means of a pressure coupling 6 and ball joint and socket 11 (Figure 1) or more directly via a drive coupling 40, which has a central connection to a coupling pin 50 (Figure 2), with the press carriage mounted on either side in a carriage guide 30.
    Since such arrangements, in which all parts are moved relative to each other and each of said connections and bearings can have play, it is not surprising that, depending on the bearing type, the effective forces, the properties of the lubricant in the bearings, the temperature , etc ..., the force-time curve of the press will be affected in a largely uncontrolled way. It is therefore desirable to provide improved shrinkers, whereby the negative effects due to the bearing play of the desired force curves or force time curves can be reduced.
    SUMMARY OF THE INVENTION
    2014/0646
    The shrinkers of the present invention address the aforementioned problem by involving a cam and cam roller in driving the vertical displacement of the press carriage. Via this configuration, it is, for example, easy to adjust the force time or force curves by changing the shape of the cam, whereby, for example, an increased force concentration is allowed below the driving stroke of the press carriage.
    It is thus an object of the present invention to provide a drive mechanism of a press carriage for an automated terminal crimping machine, comprising the following;
    - a camshaft with an eccentric cam, in particular an eccentric plate cam;
    - means for rotating the camshaft;
    - a press carriage consisting of a cam roller;
    - guide rails that slidably fit around the press carriage; and
    - means for keeping the cam roll in contact with the eccentric cam during rotation thereof.
    Various heads of crimping instruments can be attached to the underside of the press carriage and the attached instrument head is driven with the press carriage in a continuous input applicator that offers the terminal (s) to be crimped. As such, the press carriage of the press carriage drive mechanism, as described herein, in a further aspect comprises an applicator hook capable of providing crimping tools to different heads.
    As already mentioned hereinbefore and in converting the rotational movement of the eccentric cam into a linear displacement of the press carriage, the drive mechanism of the press carriage includes means for keeping the cam roll in contact with the eccentric cam during its rotation. In principle, any system capable of pulling or pushing the press carriage with the required force against the eccentric cam to prevent slipping of the cam roll can be used. In the illustrated prototypes, further described below, the means for maintaining the cam roller in contact with the eccentric cam comprises a spring, hereinafter referred to as the compression spring of the press carriage 7. It is therefore a further object of the invention in question. provide a drive mechanism of the press carriage for an automated terminal crimping machine, the means for maintaining the cam roll in contact with the eccentric cam during rotation consist of a compression spring of the press carriage 7.
    An advantage of the current drive mechanism of the press carriage lies in the ease of adjusting the force time or force curves by simply changing the profile of the eccentric cam. In order to further increase the adaptability of the system without having to change the eccentric cam for any given cable guide and crimped contact, the press slide can further comprise an adjusting nut 10. Through the use of such adjusting nut it is possible to adjust the closing height of the crimping machine to to fit, depending on the cable guide and shrink contact / terminal. So included in one
    2014/0646 a further aspect is the press carriage, in the drive mechanism of the press carriage of the invention in question, an adjusting nut, preferably positioned between the press carriage and the applicator hook.
    Apparently, the means for rotating the camshaft usually consist of an electric motor, such as an AC motor driven by a frequency inverter. In a particular prototype, driven by a variable frequency inverter (VFD), also known as adjustable frequency inverter, variable speed drive, AC drive, micro drive or direct current drive. Such drive systems allow AC motor speed and torque to be controlled by varying the motor input frequency and voltage. It therefore offers the possibility of including a start / stop function to operate the crimpers without additional electrical components, thereby further simplifying the design of the press carriage drive mechanism with an associated increase in long-term reliability. Therefore, in one prototype of the invention in question, the means for driving the camshaft in the drive mechanism of the press carriage include an electric motor, in particular an AC electric motor driven by a variable frequency controller (VFD).
    In one prototype, the drive mechanisms of the press carriage are further characterized by comprising means for determining the closed height and / or of the body of the press carriage. In view of the possible presence of an adjusting nut, this closed height can differ from the closed height of the crimpers and be in accordance with the upper and lower position of the body of the press carriage. Consequently, in one prototype, the drive mechanism of the press carriage of the invention in question comprises means for determining the closed height of the body of the press carriage. In another prototype, the drive mechanism of the press carriage comprises means for determining the closed height of the body of the press carriage. In both of the prototypes mentioned, the means may, for example, consist of contact switches, but in view of the high frequencies at which these crimping machines can be used, it is desirable to have contactless means determine the position of the body of the press carriage. Within the prototypes explained, these means consist of inductive sensors, also known as proximity sensors, which detect metal objects without touching them. Via these sensors it is possible to determine the position of body of the press carriage and in combination with the VFD the press carriage can be stopped in the upper and / or lower position.
    The person skilled in the art is well aware of the camshaft bearings that can be used in the driving mechanism of the press carriage of the invention in question, such as for example ball bearings, ball bearings and needle bearings. In a particular prototype, the camshaft bearing is a needle bearing. Compared to a ball bearing, they have a higher load resistance, thereby contributing to the service life of the drive mechanism of the press carriage of the invention in question.
    The cam roller, making contact with the eccentric cam, is integrated with / or mounted on
    2014/0646 one end of the press carriage. In one prototype, the cam roller is cylindrical and fits around a cam roller bearing with bearing shaft. Just like the bearing axis of the eccentric cam, any known axle bearing can be used. In one prototype, the camshaft bearing axis also includes a needle bearing. In an alternative prototype, the cam roll is spherical and corresponds to a ball transfer unit integrated with or attached to one end of the press carriage.
    All known slide guides, such as cast iron slide blocks or bronze slide blocks with integrated carbon lubrication, can be used in the drive mechanism of the press slide of the invention in question. In a special prototype, the carriage guides are selected from cast iron or bronze sliding blocks with integrated carbon lubrication. In the prototype example, the carriage guides are bronze sliding blocks with integrated carbon lubrication.
    An important difference between the drive mechanism of the press carriage of the invention in question, when compared to the known crimping machines, is the fact that there is no cross connection (such as a pressure coupling or drive coupling) between the motor drive shaft and the press carriage. The press carriage is simply kept in contact with a rotating cam. If in each of the foregoing prototypes the camshaft comprises an eccentric cam and the press carriage comprises a cam roller, it will be clear to the skilled person that this order can be reversed whereby the eccentric cam is integrated / or mounted at one end of the press carriage and the cam roll is fitted around the camshaft. It is thus an object of the present invention to provide a drive mechanism of a press carriage for an automated terminal crimping machine, comprising the following;
    - a camshaft that offers space for a first cam;
    - means for rotating the said camshaft;
    - a press carriage comprising a second cam;
    - carriage guides transport guides that fit slidably around the press carriage; and
    - means for maintaining the second cam in contact with the first cam during rotation thereof and characterized in that at least one of said first or second cams is an eccentric cam.
    In a prototype, the first cam is an eccentric cam as described above and the second cam a cam roll as provided herein and including cylindrical and spherical cam rollers previously described herein. In another prototype, the first cam is a cam roll and the second cam an eccentric cam, as provided herein. In the aforementioned prototype, the cam roller mounted on the camshaft will be cylindrical and fit around a cam roller bearing.
    It is another object of the present invention to provide the use of a press carriage driving mechanism, as previously described herein, in a crimping machine. Especially in an automated terminal crimping machine. Thus, in a further object, the invention in question also provides a crimping machine, which is a drive mechanism of the invention in question
    2014/0646.
    BRIEF DESCRIPTION OF THE DRAWINGS
    With specific reference now to the images, it is emphasized that the details shown are a form of example and only for the purpose of illustrative discussion of the various references of the invention in question. They are the cause of providing what is believed to be the most useful and easy description of the principles and conceptual aspects of the invention. In this regard, no attempt is made to show structural details of the invention in more detail than is necessary for a fundamental understanding of the invention. The description is taken with the drawings, which make clear to those skilled in the art how the various forms of the invention can be embodied in practice.
    Fig. 1: Is a front view in perspective of a previously artificial crimper with a pressure coupling 6 and ball joint and socket 11 connection.
    Fig. 2: Is a front view of a previously artificial crimp with a drive coupling 40 and central coupling pin 50 connection.
    Fig. 3: Shows an exemplary displacement time curve (b) for an eccentric cam profile (a) used in a drive mechanism of a press carriage of the invention in question.
    Fig. 4: Is a front view of a press carriage drive with an eccentric cam 1 and cam roller 4 of the present invention.
    Fig. 5: a cross-sectional perspective view of a cam roller used in the drive mechanism of the press carriage of the invention in question and showing a cam roller needle bearing 15 with bearing shaft 5.
    Fig. 6: Prototype example of a press carriage 20, the body of the press carriage 12 comprises at one end an extension with an opening for placing the bearing axis 5.
    Fig. 7: Assembly view of a crimper, comprises a drive mechanism of the press carriage of the invention in question and shows the electric motor 14 with gearbox 24, the press frame with frame plate 16, the camshaft 3 with eccentric cam 1, the compression spring of the press carriage 7, the means for determining the closed height of the body of the press carriage 13, the guide guides 30 assembled from slide bearings 30a and slide plates 30b and the press carriage
    2014/0646 with a second cam 4 at one end and the applicator hook 9 with adjusting nut 10 at the other end.
    DETAILED DESCRIPTION OF THE INVENTION
    As already stated herein, it is an object of the present invention to provide a press carriage drive mechanism and corresponding crimpers with as little play as possible to ensure reliability and reproducibility of the force curve or force time curve during the shrink production process.
    Unlike the prior art crimping presses, in which the press carriage is driven by a pressure coupling design, the drive mechanism of the press carriage of the present invention is based on cam movements, which include one eccentric cam and a cam roller. Other details and advantages of the present invention will become apparent from the following description of such a press carriage driving mechanism. This description is only given by way of example and does not limit the invention. The reference numerals refer to the accompanying illustrations, which represent one of the possible prototypes of the invention in question.
    Figure 4 provides a representative drive mechanism of the press carriage of the invention in question. In said example, an eccentric plate cam 1 is mounted on the camshaft 3 driven by an electric motor 14. The eccentric cam converts the rotational movement of the motor into a linear displacement for the shrinkers, as shown in the example of displacement time curve of Figure 3. Between positions 1 to 4, the cam profile provides a rapid displacement of the press carriage to the vicinity of the product to be crimped. The actual shrinkage of the product takes place between positions 4 and 7. As can be seen from the example displacement time curve between the stated position, the rotation of the cam is translated into a small vertical displacement of the press carriage and even held at the same height between positions 5 and 6, as further detailed below. In other words, in order to increase and realize the desired pressing pressure, the pressing carriage is further lowered over a short distance between positions 4 and 5, by making the cam profile less eccentric with respect to the cam shaft between the stated positions. In the prototype example, the cam profile is only 1 mm eccentric between said positions, over a length of 90 °. The pressure is then maintained by a concentric movement of the cam between positions 5 and 6. The length between positions 5 and 6 accordingly allows to manage the retention time of the shrinking process. Compared to earlier art pressure coupling designs, longer retention times can be achieved through the
    2014/0646 drive mechanism of the press carriage of the invention in question. Such longer retention times may be desirable when shrinking more resilient materials. In such cases, the material may spring back with unwanted and partial reopening of the shrunken contact. Through the profile of the eccentric cam, complete control over the vertical displacement of the press carriage is ensured, whereby, among other things, a better optimization of the pressure retention time for a certain cable guide and shrunken contact is allowed. The further cam profile between positions 6 and 9 determines the displacement of the press carriage to its closed height position, where it is held for a certain time by a concentric movement of the cam between positions 9 and 10.
    Apparently, the cam roller 4, also referred to as the radial follower in Figure 3a), will only translate the cam profile into the desired displacement when kept in contact with the eccentric cam during its rotation. After the means for keeping the cam roll in contact with the cam and the carriage guides of the press carriage, the cam profile also plays an important role in this regard. The ridge profile must have a solid profile with no abrupt changes in eccentricity. Such abrupt changes can lead to peak loads on the cam roll and / or in the release of the contact. A solid cam profile will not only contribute to good transfer, but also reduce wear on the cam and the cam roll.
    The cam roller 4, used in the prototype example of Figure 4, is a standard component sold for these purposes and built around a cam roller needle bearing 15 with bearing shaft 5. A perspective transverse view of such cam roller is provided in Figure 5. The outer ring of the bearing is thicker to allow direct contact with the ridge, without the need for an additional bearing housing. Furthermore, the convex shape of the outer ring prevents damage to the bearing in the case of small irregularities in the camshaft. Furthermore, the presence of the carrier shaft allows simple integration of the cam roller at one end of the press carriage. In the prototype example of Figure 6, the body of the press carriage 12 comprises at one end an extension 19 with an opening for placing the bearing shaft 5. In the prototype mentioned, the body of the press carriage will fit into a recess in the frame plate 16 of the crimpers and the press carriage flanges 17, together with the support guides 30, will hold the press carriage in position and allow for displaceable displacement of the press carriage in said recess. In the prototype example, the bearing guides are made of bronze sliding blocks with integrated carbon lubrication. Such a configuration is free of maintenance and has a low friction. Low resistance movement of the press carriage is indeed desirable as it further contributes to the smoothness of the operation and continuous contact of the cam roll with the eccentric cam.
    A spring 7 located in a provided cavity 17 of the body of the press carriage pushes
    2014/0646 the press carriage against the ridge. In the prototype example, a compression spring is used and selected to have sufficient compressive force to keep the cam roller in contact with the eccentric cam during its rotation and to prevent slipping of the cam roller during said movement. When selecting the spring, it is important that this spring has a certain pre-stress and that it never exceeds its minimum length. The force to be developed by the spring depends on the weight of the linear moving parts (the cam roller, the press carriage, the applicator hook, the adjusting nut, the applicator ...), the profile of the cam and the rotational speed of the cam. In the case in question, the speed at which the press carriage was moved from the lowest (closed height press carriage) to its highest (closed height press carriage) position was also taken into account, as this determines the inertia force required to lift the press carriage. from the lowest to the highest position.
    In the shrinking example of the invention in question, the weight of the linear moving parts is 4 kg. The vertical displacement of the press carriage ram between the lowest and highest position is 0.04 m / s and at operational time the press carriage needs 0.1333 s to make the stated displacement.
    Under such circumstances the upward acceleration is equal to;
    a = dv / td = 0.04 / 0.1333 = 0.3 m / s 2
    The inertia power is equal to;
    Fi = m * a = 4 kg * 0.3 m / s 2 = 1.2 N
    The gravity equals;
    Fg = m * g = 4 kg * 9.81 m / s 2 = 39.1 N
    Minimum force to be generated by the spring is equal to;
    Fi Fg = 1.2 N + 39.1 N = 40.3 N
    This minimum force is the force required to keep the cam roller in contact with the eccentric cam. The spring is best over-dimensioned to prevent slipping of the cam roll. In the prototype example, a spring was selected with a compressive force of 236.2N, with a residual compressive force of 135.8N in a fully stretched state.
    With reference to Figure 7, all of the foregoing elements are further mounted on a frame plate 16, provided with the necessary elements, such as a recess 21 for placing the body of the press carriage, an opening 22 for placing the camshaft and camshaft bearing, bolt holes 25 for attaching further elements, such as the support guides 30, electric motor 14 and optional gearbox 24. To aid in correct mounting of the crimpers, the frame plate may further comprise one or more plug holes 23 to aid in positioning the frame plate with the rest of the frame. The skilled person is well aware
    2014/0646 of the size and material dimensions required for the frame. Elements which influence the frame characteristics of a crimper include the dimensions of the stripping unit, the applicator, the guideways of the stripping unit, the dimensions of the electric motor, the dimensions of the different bearings, the location and the dimensions of the recess around the recess. position the body of the press carriage, etc .... The precision when machining the previous elements on the crimper frame plate is of the utmost importance for accurate crimper performance. The crimpers will crimp cable guides and crimped contacts at high speeds, with high precision (allowable tolerance of 0.02 mm) and a crimping force of at least 2 tons. This requires a frame that can withstand said forces without bending. The slightest bends or other deformations of the frame result in a poor shrinking process and loss of goods. The skilled person is well aware of the material specifications that are necessary to withstand the aforementioned operating pressures. In the shrinking example, the frame was made accordingly from sheet steel with a thickness of about 20.0 mm.
    Together with the further details of the electric motor, the inductive sensors, the adjusting nut and applicator hook (supra), this description illustrates the inventions as defined in the following claims.
    权利要求:
    Claims (15)
    [1]
    CONCLUSIONS
    A drive mechanism of a press carriage for an automated terminal crimping machine, comprising;
    - a camshaft that offers space for a first cam;
    - means for rotating the said camshaft;
    - a press carriage comprising a second cam;
    - guide rails that slidably fit around the press carriage; and
    - means for keeping the second cam in contact with the first cam during rotation thereof, wherein at least one of said first or second cam is an eccentric cam.
    [2]
    The drive mechanism of the press carriage according to claim 1, wherein the first cam is an eccentric cam; in particular an eccentric plate cam and the second cam a cam roll.
    [3]
    The drive mechanism of the press carriage according to claim 1, wherein the first cam is a cam roller and the second cam an eccentric cam; in particular an eccentric plate cam.
    [4]
    The drive mechanism of the press carriage according to any of claims 2 or 3, wherein the cam roller is cylindrical or conical.
    [5]
    The drive mechanism of the press carriage according to claim 4, wherein the cam roller is cylindrical and fits around a cam roller bearing with bearing shaft.
    [6]
    The drive mechanism of the press carriage according to claim 4, wherein the cam roller is spherical and corresponds to a ball transfer unit.
    [7]
    The drive mechanism of the press carriage according to any of claims 1 to 6, wherein the second cam is integrated with / or mounted at one end of the press carriage.
    [8]
    The drive mechanism of the press carriage according to any of claims 1 to 7, wherein the press carriage further comprises an applicator hook.
    [9]
    The drive mechanism of the press carriage according to any of claims 1 to 8, wherein the press carriage further comprises an adjusting nut, preferably positioned between the body of the press carriage and the applicator hook.
    [10]
    The drive mechanism of the press carriage according to any one of claims 1 to 9, wherein the means for maintaining the second cam in contact with the first cam during rotation thereof consists of a spring.
    [11]
    The drive mechanism of the press carriage according to any one of claims 1 to 10, wherein
    2014/0646 the means for rotating the aforementioned camshaft consist of an electric motor; in particular an AC electric motor driven by a variable frequency controller (VFD).
    [12]
    The drive mechanism of the press carriage according to any of claims 1 to 11, further characterized by comprising means for determining the closed height of the body of the press carriage
    [13]
    The drive mechanism of the press carriage according to claim 12, wherein said means for determining the closed height of the body of the press carriage consists of inductive sensors.
    [14]
    Use of a press carriage driving mechanism, as defined in any one of claims 1 to 13, in a crimping machine; especially in an automated terminal crimping machine.
    [15]
    A crimping machine comprising a drive mechanism of a press carriage as defined in any one of claims 1 to 13.
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    同族专利:
    公开号 | 公开日
    EP2843779A1|2015-03-04|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    GB9819301D0|1998-09-05|1998-10-28|Mckechnie Uk Ltd|Improvements in presses|
    DE20204914U1|2002-03-27|2002-06-06|Madat Gmbh Automatisierungstec|Press with cam|
    WO2006022109A1|2004-08-24|2006-03-02|Murata Kogyo Kabushiki Kaisha|Harness manufacturing apparatus|
    DE102010060103B4|2010-10-21|2013-04-11|Schuler Pressen Gmbh & Co. Kg|Drawing press with dynamically optimized sheet metal holding|
    法律状态:
    2019-04-01| FG| Patent granted|Effective date: 20190301 |
    优先权:
    申请号 | 申请日 | 专利标题
    EP13182774.3A|EP2843779A1|2013-09-03|2013-09-03|Crimping press|
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