JP2007511198A - Cable sheath removal device - Google Patents

Abstract

  The present invention essentially consists of a blade with a blade which is arranged immediately next to the centering scissors (8), operates independently of them in the radial direction and can rotate independently of them with respect to the axis of rotation. The present invention relates to a cable coating device having a centering device with several centering scissors (8), preferably exceeding at least two holders (23, 25, 26). The number and configuration of the centering scissors (8) with respect to the blade holder (23, 25, 26) with a blade are such that when the blade performs a rotary cutting operation, the blade holder (23, 25, 26) with an adjacent blade or A phase shift occurs in the interaction of the centering scissors (8). This has the effect of reducing or canceling the vibrations that occur in the cable being stripped, thus increasing the accuracy of the cut. Special shapes for the knife and centering scissors are disclosed along with control using a computer.

Description

  The present invention relates to a cable sheath removing device, which is at least two more than the number of blade holders with a blade, provided substantially adjacent to the blade holder, and independent of the blade holder in the radial direction. A centering device having several centering scissors is provided that operates and rotates independently of the blade holder relative to the axis of rotation.

  Such a configuration is disclosed in FIGS. 21 and 28 to 32 of the international patent application WO-A-9813907. There, a “rotary box” is described as a part of a continuous cable processing device. This rotary box is inserted into a cable sheath removing machine in order to perform a cable sheath removing process on the coaxial cable.

  In this known prior art (see FIG. 21 and FIGS. 28 to 32 of international patent application WO-A-9813907), the shaft of the hollow scissors is attached by a fixed sleeve, which is connected through a pin. Torque is transmitted to the gears on the helical flange meshed with the four centering scissors. The centering scissor opening is guided by a scissor opening guide that affects the movement of the centering scissor opening toward or away from each other. The two blades are guided by a blade guide that is coaxial with the axis of the scissor opening. The spindle carries the wedge-shaped member in the longitudinal direction. A cylindrical pin fixes the rotation of the wedge. The rotation of the second gear affects the axial movement of the wedge. This movement functions in a closing direction or an opening direction with respect to the blade holder with the blade.

  The use of the configuration of four centering scissors and two bladed blade holders has proven very successful and the achievable cutting quality is very good. Also, the same type of configuration has been used for many years for other structures by the applicant “MP 8015”. Since the known structure does not reach the desired accuracy at the lower limit of the cable diameter, thorough attempts have been made to improve the cutting accuracy. The inventor has, through extensive research, contrary to the previously asserted opinion, the centering scissors can center the cable, but especially with thin cables, the blades are centered in their blade holders. It has been found that the cable is deformed by two blades to form almost an ellipse, and tends to escape laterally from the blade (ellipse effect). In addition, extensive observations and discussions reveal the surprising vibrations that occur in the cut region of the cable, which arises from the rhythm of the repeated overlapping of the blade and centering scissors in a single alignment.

Japanese National Patent Publication No. 11-514835

  These new and creative discoveries improve the accuracy and eliminate the disadvantages of the first known configuration that has been identified. It has become.

  The first inventive step is that during rotary cutting, the phase shift has the effect of reducing or canceling the vibrations that occur in the uncovered cable, and the adjacent cutter holder or centering scissors By being influenced by the interaction, it includes adapting to the direction, number and configuration of the centering scissors in relation to the blade holder with the blade, thus increasing the accuracy of cutting.

  At the same time, the inventor has also confirmed for the first time the following: by grasping a cable with an inherently elastic outer covering, the cross-section of the cable at the time of centering, as opposed to being composed of two blades. Polygon deformation (polygon effect) occurs. This cross section is originally circular and becomes almost polygonal due to this deformation, and “corners” are formed in the gaps between the centering scissors. As a result of this formation, however, the cutting force generated in the blade holder with a blade also varies when the blade holder with the blade cuts the cable along its circumference. However, this variation in cutting force results in a pulsating, rhythmic load on the entire structure or parts of it, starting with the blade, first through the retainer, through the mounting, centering scissors, and through the cable. Then, it returns to the blade holder with the blade. According to a new discovery by the inventor, this pulsating load is particularly noticeable in the case of thin cables and corresponding small bladed tool holders, centering scissors and the surrounding mechanical structure. It should be noted that in this case the device has only a finite stiffness. However, the quality of cable stripping also depends on the wave, frequency and amplitude of the cutting force.

  The first countermeasure would be to increase the number of support points in centering. The amplitude of the pulsating load between the support points is thereby reduced, but more extensive equipment or more parts must be spent.

  However, the inventor also has a direction of force and the outer layer of the cable is not rounded (polygonal effect), resulting in periodic amplification fluctuations, whose amplitude is undesirably added to the mechanical structure and cut It was discovered that it could be a geometrical deformation (insufficient accuracy). Thus, it is a further object of the invention to find a structure in which the amplitude of the fluctuations of the undulating force of the blade holder with the blade cannot be amplified or accumulated, but rather has an offsetting effect. In this case, force pulsations should not occur as periodically as possible and should be able to be kept to a minimum value in preparation for the maximum value. This is achieved by the present invention with a plurality of tools, in particular by a bladed cutter holder that handles a range of cables with a higher cutting force caused by a polygonal effect that occurs consecutively rather than simultaneously. The effect of regenerating the region of vibration should be avoided at the same time that the lack of roundness in the processing area itself further excites the vibration. According to the present invention, the non-integer ratio of the number of centering scissors and bladed tool holders shifts the vibrations of the individual bladed tool holders at the mutual phase position, thereby amplifying. Suitable for avoiding overlapping.

  All these new or creative objectives are solved by a new configuration for the ratio of the centering scissors and the bladed tool holder according to the invention, which is five for three bladed tool holders. Centering scissors have been recognized as an economical and optimal ratio. The ratio of four to three has also been improved, but the force variation for the polygon effect is larger than the five centering scissors. A ratio of 6 to 3 can have a regenerative effect, and a ratio of 7 to 3 is already very complex with respect to scissor control. For example, the ratio of 7 to 4 is too many.

  Limiting the number of blade holders with blades to preferably three is consistent with the facts established on the basis of the risk of deviation due to errors arising from the shape of the blades, Furthermore, the risk that cutting of a plurality of blades is not accurately placed on the same surface is increased, so that the accuracy of the cutting surface can suffer quality loss for this reason, independent of what has been described above.

  At the same time, the inventor also compared with the conventional two-bladed blade holder (ellipse effect), the cable with three blades is additionally centered by the cutting force, the roundness of the cable by the cutting force, I found it less affected. With the discovery according to the invention, the absolute deformation of the ellipse is larger than that of the triangular shape. These additional effects likewise increase the quality of work of the device according to the invention (polygonal effects defeat the elliptical effect).

  According to the present invention, superposition is best avoided by using a fractional (decimal) ratio. The number of centering scissors must not be an integer multiple of the number of blade holders with blades. Six for three means that the three blades are in the same phase position with respect to the waveform of the cable, which means that confusing force pulsations are amplified. Being 5 out of 4 results in a continuous series of individual force pulsations, resulting in less overlap. Six out of four are not integers; however, the two blades are always in the same phase and the two are in exactly opposite phases. Overall, this ratio is thus too regular, and therefore the two force pulses are preferably avoided by the present invention because they are formed in synchrony and are not sufficiently offset from each other.

  Further developments of the invention are defined in the figures, figure descriptions and dependent claims.

  The reference list forms part of the present disclosure.

  The invention is described symbolically or by way of example in details with reference to the figures.

  The figures are interrelated and redundantly described. Similar components are indicated with similar reference numbers, and reference numbers with different indices indicate components with similar or similar functions.

  1-3 show a structure according to the present invention, in which the new “micro coax box” compared to the known “rotative box” has substantially no errors in thinner cables. Provides high precision coating removal.

  The first belt pulley 4 provided around the main shaft 5 which is a rigid body is controlled by a toothed belt driven by a motor. The first belt pulley 4 transmits the desired adjusted torque to each of the disc camshaft 24 / first helical flange 41 which engages with the centering scissors 8 and the pin via an adjustable safe friction clutch. . Since the centering scissor opening 8 is guided by the centering flange 7, the centering scissor opening slips toward or away from each other by the rotation of the disc camshaft 24 / first spiral flange 41. The desired torque or force of the centering scissors is achieved by adjusting the first nut 2 and introducing an initial tension to the spring 27.

  The cutting force acts on the outer periphery of the cable sheath through the contact pressure of the centering scissor port 8. The centering scissors 8 are L-shaped in cross section so that they have a very compact design and nevertheless a wide range of centering or clamping for the cable to be uncoated. ) Provide a surface. Their ends protrude right up to the blade. Because they are L-shaped, they provide a free position for all types of guides.

  The second spiral flange 11 is adjusted coaxially with the first belt pulley 4 and supports the second belt pulley 6 on the two ball bearings 1. The second spiral flange 11 supports the head member 10 with a ball bearing 37. The second belt pulley 6 and the head member 10 are independent of each other and optionally driven in a differentiated manner by a toothed belt. The blade holders 23, 25, and 26 with blades are installed so as to be movable in the radial direction with respect to the blade flange 12 fixed to the head member 10. The relative movement between the second belt pulley 6 and the head member 10 is caused by the cylindrical pin 32 fixed to the blade holders 23, 25, and 26 and engaged with the second spiral flange 11. 25, 26 generate slips that approach or separate from each other, thus acting on them in a closing or opening direction. Other blade holder opening and closing devices known to those skilled in the art are also within the scope of the present invention. The relative movement is generated by the difference in speed when the second belt pulley 6 or the head member 10 is operated.

  FIG. 4 shows the uniformity of the angle formed between the adjacent blade holders 23, 25, 26 and the adjacent centering scissors 8 in each case, and the blade holding with the blade in each case. The non-uniform angles that can occur between the tools 23, 25, 26 and the centering scissors 8 are shown.

  5 and 6 show curves for the prior art and a preferred embodiment of the present invention, respectively, case 1 is a test using four centering scissors and two bladed tool holders. Case 2 is a test using five centering scissors and three bladed blade holders, and the radial deviation (Δr) of case 1 having fewer support points is smaller than that of case 2. Thus, the variation of the cutting force (ΔF; one curve of each blade) is also smaller in the second case. The scale of the ordinate (level) is arbitrary, while the abscissa (angle α) comprises one complete rotation (= 2π). The graph regarding the time of the cutting force is a cycle and is shown as a sine function in a simplified manner, but this does not affect the above or below description. In the analysis of vibration superposition, this assumption is made in the same way at points in the structure of interest, and vibration can be added by linear superposition. In places where this is not exactly correct, the same qualitative expression is applied, particularly in relation to the amplification of vibration at a certain stage.

These curves can be interpreted in detail as follows:
Case 1:
In the first curve, between 360 degrees, in particular in each case of two adjacent centering scissors (one rmax) and in each case adjacent to each of the four centering scissors. (One rmin) Double radial deviation is obtained 4 times. The equation is Δrmax (α): = p1 (αn1). The second curve is a graph of the force on the first blade between the same 360 degrees. At these points of greater radius, the resistance and hence the force will also be greater. Therefore, this curve is generated in synchronization with the first curve. The formula is ΔF1 (α): = q1 (αn1). The third curve shows a graph of the force on the second cutter between 360 degrees. Since this is offset by 180 degrees with respect to the first blade, it has the same force fluctuation characteristics as the first blade, and is simultaneous. The first and second pulsations are added, and the total amplitude of the curve is twice that of the second or third curve. The formula is ΔF2 (α): = ΔF1 (α).

Case 2:
In the first curve, between 360 degrees, in particular in each case of two adjacent centering scissors (one rmax) and in each case adjacent to each of the four centering scissors. (One rmin) Double radial deviation is obtained 5 times. Since the r deviation is necessarily smaller due to more application points of the centering system, the amplitude of the curve is smaller than the first curve of case 1. If the centering scissors are an infinite number, the r deviation will be zero. The equation is Δrmax (α): = p1 (αn2). The second curve is a graph of the force on the first blade between the same 360 degrees. At these points of greater radius, the resistance and hence the force will also be greater. Therefore, this curve is generated in synchronization with the first curve. Since the r deviation is smaller than in the first case, the difference in force development is also smaller than in the first case. The formula is ΔF1 (α): = q2 (αn2). The third curve shows a graph of the force on the second cutter between 360 degrees. Since this is offset by 120 degrees with respect to the first cutter, it has a similar force variation characteristic offset by 120 degrees with respect to the first cutter, and at the same time. The force variation curve is therefore offset with respect to the value of the second curve. The equation is ΔF2 (α): = q2sin [(α + 2π / 3)) n2]. The fourth curve is similar to the third curve in all respects. The first, second and third blade pulsations are added to zero, and the amplification in the summed curve is adjusted to zero, which is not only a quantitative decrease in force pulsations, but also a qualitative decrease But there is. Therefore, we cut the frequency of the first curve from the second part, but there is no force superposition through the blade. A similar effect can also occur in the four centering scissors and the three-blade scissors in the first curve of case 1 with a larger Δr amplitude. The equation is ΔF3 (α): = q2sin [(α + 4π / 3)) n2].

  FIG. 7 illustrates how the cable end is inserted into the working area of the bladed cutter holder (23, 25, 26) from the side in the radial direction of its axis.

  The present invention is essentially related to the embodiments, and thus the cable sheath removal device is located immediately next to the centering scissors and operates independently of them in the radial direction, with the rotation axis. On the other hand, it comprises a centering device having several centering scissors, exceeding the number of blade holders (23, 25, 26) with blades that can rotate independently of them, preferably at least two, During the rotary cutting operation, the direction, number and configuration of the centering scissors (8) associated with the bladed tool holder (23, 25, 26) are determined by the adjacent bladed tool holder (23, 25, 26) and the centering scissor opening (8), causing a phase shift and reducing or canceling the vibration generated in the cable to be covered, thus cutting accuracy. To increase. Detailed embodiments relating to the blade and centering scissors and to the computer controlled control system are also shown.

  The present invention can be optimally modified and operated as an independent cable sheathing device or as a continuous cable processing plant.

It is a perspective view about the structure after the assembly based on this invention. FIG. 2 is an exploded perspective view of the structure according to FIG. 1. It is sectional drawing of the structure which concerns on invention of FIG. It is the schematic of the angle between adjacent centering scissors mouths, and the angle between the adjacent blade holders with a blade. It is three curve diagrams in Case 1 (prior art). 4 is a diagram of four curves in case 2 (a preferred embodiment of the present invention). FIG. FIG. 6 is a perspective view of a specific embodiment of the assembled structure according to the present invention.

Explanation of symbols

  1 Ball bearing, 2 First nut, 3 Brake flange, 4 First belt pulley, 5 Main shaft, 6 Second belt pulley, 7 Centering flange, 8 Centering scissors, 9 Centering cover, 10 Head member, 11 First 2 spiral flange, 12 blade flange, 13 blade cover, 14 guide tube, 15 handle, 16 second nut, 17 first spacing ring, 18 second spacing ring, 19 brass pin (to avoid damage due to screw pin), 20 Brass pin (avoids damage due to screw pin), 21 Brass pin (avoids damage due to screw pin), 22 Bearing, 23 Cutter holder with first cutter, 24 Disc camshaft, 25 Cutter holder with second cutter, 26 3rd Blade holder with blade, 27 springs, 28 set screws (second nut 1 29 set screws (for fixing the brake flange 3), 30 set screws (for fixing the belt pulley 6), 32 cylindrical pins, 34 cylindrical pins, 35 flat head screws, 36 flat head screws, 37 Ball bearing, 39 Friction bearing, 40 Shear washer, 41 First spiral flange.

Claims (15)

A blade holder (23, 25, 26 with a blade) which is arranged immediately next to the centering scissors (8), operates independently of them in the radial direction, and can rotate independently of them with respect to the rotation axis. A centering device having several centering scissors (8) exceeding the number of), preferably a uniform first angle is formed between adjacent centering scissors (8); More preferably, in the cable sheath removing device formed between the adjacent bladed tool holders (23, 25, 26), the uniform second angle is:
The number of the centering scissors (8) and / or the number of blade holders with blades (23, 25, 26) is an odd number, and the first angle is not a perfect multiple of the second angle. A cable sheath removing device. A blade holder (23, 25, 26 with a blade) which is arranged immediately next to the centering scissors (8), operates independently of them in the radial direction, and can rotate independently of them with respect to the rotation axis. In a cable sheath removing device comprising a centering device having several centering scissors (8) exceeding the number of
During the rotary cutting operation, the direction, number and configuration of the centering scissors (8) associated with the bladed cutter holder (23, 25, 26) is reduced in vibrations generated in the cable being stripped. A cable sheath removing apparatus characterized by causing a phase shift in the interaction between a blade holding tool with a blade and a scissor opening for centering, which has an offset effect, and thus improves the accuracy of cutting.   3. The cable sheath removal device according to claim 1 or 2, wherein the number of centering scissors (8) exceeds the number of blade holders (23, 25, 26) with blades by at least two and / or The cable sheath removing device, characterized in that the number is not divisible by the common divisor.   The cable sheath removing device according to any one of claims 1 to 3, wherein at least one single centering scissor opening (8) holds a bladed knife with a blade in the axial direction of the cable, particularly when stopped. Cable sheath removal device characterized by being aligned with the tool (23, 25, 26).   5. A cable sheath removal device according to claim 1, wherein at least one single centering scissor opening (8) is a cable when viewed from the plane of the drawing, particularly when stopped. When the axis of rotation or the axis of rotation of the blade holder with the blade is perpendicular to the plane of the drawing, it is aligned with the blade holder with the blade (23, 25, 26) in the radial direction of the cable. A cable sheath removal device.   6. A cable sheath removing apparatus according to claim 1, wherein the centering scissor opening (8) is made rigid against torsion.   The cable sheath removing device according to any one of claims 1 to 6, wherein the centering scissor opening (8) is preferably a cutter holder (23, 25, 26) with a cutter with respect to the rotation axis. A cable sheath removing device, wherein the device is manufactured so as to be rotatable in a direction opposite to the direction of rotation.   The cable sheath removing device according to any one of claims 1 to 7, wherein the blade holder (23, 25, 26) with a blade is disposed between the centering device and an end of the cable to be sheathed. A cable sheath removing apparatus provided at a work position.   The cable sheath removing device according to any one of claims 1 to 8, wherein the position of the blade holder with the blade (23, 25, 26) can be specified, and the blade is similar to the centering scissors (8). The retainer (23, 25, 26) and other second centering, tensioning or gripping devices as well as additional further cable sheath removal stations are constructed, one cable end being a bladed knife A cable sheath removing device, which can be inserted into a work area of the holder (23, 25, 26) from a side surface in a radial direction with respect to an axis thereof.   The cable sheath removing device according to any one of claims 1 to 9, wherein the centering scissor opening (8) or the bladed cutter holder (23, 25, 26) is provided in one plane. A device for removing a cable sheath, characterized in that other points of the edge of the blade or other lines of the centering surface are associated with the respective diameter of the cable or are in contact with the cable.   11. The cable sheath removing device according to claim 1, wherein the centering scissor opening (8) has a recess for sliding along a contact line of each adjacent centering scissor opening (8). A cable sheath removing device characterized by having each.   It is a cable sheath removal apparatus of any one of Claims 1 thru | or 11, Comprising: The cutter holder (23, 25, 26) with a cutter is respectively in the adjacent cutter holder (23, 25, 26) with a cutter. A cable sheath removing apparatus having a recess for sliding along the cable.   The cable sheath removing device according to any one of claims 1 to 12, wherein the number of centering scissors (8) and the number of blade holders with blades (23, 25, 26) are common divisors. A cable sheath removing device characterized by the absence of   14. The cable sheath removing device according to any one of claims 1 to 13, wherein the blade holder with blades (23, 25, 26) can cut at least two different cable layers or have two different diameters. A first drive means for operating the blade holder with blades (23, 25, 26) to be insertable, so that at least two radially different positions are entered and stored, and at least An apparatus for removing a cable sheath, wherein electronic means are provided to control the first drive means. 15. The cable sheath removing device according to any one of claims 1 to 14, wherein the cable sheath removing device holds a bladed cutter holder (23, 25, 26) with a blade for cutting at least two cable layers. A blade flange (12) for moving the second drive means axially relative to the cable to at least two different pre-selectable positions with respect to the cable to remove at least two cable layers A cable sheath remover, characterized in that it is provided and has electronic means for storing at least two different axial positions and for monitoring at least the second drive means.