KR20070017299A - Stripping device - Google Patents

Abstract

The present invention relates to a stripping device comprising a centering device having a plurality of centering jaws, wherein the number of centering jaws is in a immediately adjacent zone and acts independently of it in a radial direction, and is independently provided with a cutter rotatable about an axis of rotation. It relates to a stripping device that preferably exceeds two of the number of cutter holders.

Description

Stripping Device {STRIPPING DEVICE}

The present invention relates to a stripping device comprising a centering device having a plurality of centering jaws, wherein the number of centering jaws is in a immediately adjacent zone and acts independently of it in a radial direction, and is independently provided with a cutter rotatable about an axis of rotation. It relates to a stripping device that preferably exceeds two of the number of cutter holders.

Such a device is disclosed in FIGS. 21, 28, 29, 30, 31 and 32 of patent specification WO-A-9813907. In this patent, "Rotativbox" is described as a component of the endless cable processing apparatus. It is fed into the endless cable processor to facilitate the stripping process from coaxial cables.

In this published prior art (WO-A-9813907 FIGS. 21 and 28-32), a jaw shaft is attached to a rigid sleeve over the jaw shaft, which transmits the torque of the gear to the helical flange, which is a pin. Through the four centering encounters. The centering jaws are guided in the jaw guides, the jaw guides generating an inward or outward movement of the centering jaws. Two cutters are guided in the cutter guide coaxially to the jaw shaft. The spindle drives the wedge in the longitudinal direction. The cylinder pin secures the wedge so that it does not rotate. The rotation of the second gear serves to move the wedge axially. This movement moves the cutter holder with the cutter in the closed or open direction.

The use of a device consisting of two cutter holders with a cutter and four centering jaws has proven to be the best and the cutting quality achievable is very good. Similar devices have been in use for several years already in the other structures of the applicant "MP 8015". In the known structure, since the desired precision can no longer be achieved at the lower boundary of the cable diameter, intensive efforts have been made to improve the cutting precision. In a wide range of tests, Applicants believe that in very thin cables, the cutter is deformed from the cutter holder to centering as the cable is almost elliptical by both cutters, although the centering jaws can center the cable contrary to the present opinion. They found that they tend to work against them, and they tend to run off the cutter on the side (an Oval Effect). Surprisingly, long-term observations and considerations have shown that a tremendous vibration occurs in the cutting zone of the cable, which is continuously regenerated and is caused by cyclic motion caused by the simultaneous overlap of the cutter jaws and the centering jaws.

Based on this new inventive recognition, the object of the new invention is to improve the known device so that the precision is improved and to overcome the first recognized negative effects of the known device.

In the first inventive step, a phase shift occurs in the interlocking operation of a cutter holder with a cutter and a centering jaw, which phase shift acts to be suppressed or compensated for by increased vibration in the cable to be stripped and for this reason cutting precision Determining the number and placement of the centering jaws relative to the cutter holder with the cutter so that is increased.

The inventor first recognized the following. The tightening of the cable, which itself contains an elastic sheath, results in a polygonal deformation of the cable cross section as opposed to the two cutter devices when centering (polygon effect). It was originally circular and, through this transformation, became nearly polygonal, with "edges" formed between the centering jaws. However, this edge formation also changes the cutting force, which appears in the rotating cutter holder with the cutter as the cutter cuts the cable along the perimeter. On the other hand, however, this cutting force change creates a periodic load in the form of a pulse of the entire structure or component, which loads from the cutter, through the holder, the bearing section, the centering jaws, back through the cable, and again with the cutter. Is passed to. In this new discovery of the inventors such pulsed loads appear especially in cutter holders with thin cables and correspondingly shaped cutters, centering jaws and the mechanical structure around them. In this regard it should be taken into account that the device has only finite rigidity. However, the quality of the stripping section is also affected by the amplitude, frequency and waveform of the cutting force.

A countermeasure against this may be to increase the number of support points in the centering device. This would reduce the amplitude of the pulsed load between the supports, but it would increase the cost due to more various mechanisms or more components.

However, the inventors also found the following. Due to the concentricity of the cable layer (polygonal effect), periodic amplitude fluctuations can occur and this amplitude can be negatively transmitted to the mechanical structure, and there is a direction of force that can cause geometrical variations in the cutting plane (lack of precision). . It is therefore another object of the present invention to provide a structure in which the amplitude due to the change in the force of the waveform is compensated without being increased or increased in the cutter holder with the cutter. In this structure, the force pulses should not be as shocking as possible but can gradually increase to maximum and then to minimum. This is achieved in the present invention by machining the cable with a plurality of tools, in particular a cutter holder with a cutter, in succession, rather than simultaneously, with a greater force, which can occur in the polygonal effect. At the same time, the regenerative effect in the vibrator portion should be avoided, in which the vibration continues to occur on its own due to the concentricity of the preceding cut. The non-integer ratio between the cutter holder with the cutter and the centering jaw quantity is suitable for moving the vibrations of the individual cutter holders with the cutter to each other in the phase position and eliminating the superposition which is reinforced in the present invention.

All these new inventive objects are achieved in the present invention through a new proportional arrangement between the cutter holder with the cutter and the centering jaws, the economically optimal ratio being five centering jaws for three cutter holders with the cutter. Proved to be. The improvement of the ratio of 3 to 4 has already been achieved, but the force variation associated with the polygonal effect is greater than in the five centering encounters. The ratio of three sixs can produce a regenerative effect and the ratio of three sevens is very complicated with regard to the centering jaw drive. For example, the ratio of four to seven is more complicated.

Limiting the number of cutter holders with cutters to three is due to the fact according to the invention below. Multiple cutter holders with cutters with respect to tolerances in the cutter configuration may again increase the risk that the precision of the cutting surface may be degraded for these independent reasons, as the cutting surfaces of the plurality of cutters are not on the same surface. Let's do it.

In this regard, the inventor also found that the cable is centered through the additional cutting force of the three cutters compared to the two cutter holders with the conventional cutter (oval effect) and the concentricity of the cable is weaker affected by the cutting force. did. The absolute deformation of the ovoid is larger than in the triangle-like variant according to the recognition according to the invention. This additional effect likewise improves the working quality of the device according to the invention (polygonal effect over ovoidal effect).

Overlap is maximized through non-integer ratios in accordance with the present invention. The number of centering jaws shall not be an integer multiple of the number of cutter holders with cutters. Three to six means that there are three cutters in six phase positions for the cable waveform, i.e. the enhancement of the impaired force pulses. Four to five means sequential progression of individual force pulses, i.e. less overlap. 4 to 6 is not an integer ratio, but there are always two cutters in phase and two in exactly the opposite phase. Thus, on the whole, this ratio is so regular that two force pulses occur at the same time, which should preferably be avoided in accordance with the invention, since mutual compensation is not sufficiently formed.

Other forms of the invention are specified in the drawings, the description of the drawings and the dependent claims.

Reference numerals are components of the application.

The invention is described in detail illustratively and symbolically on the basis of the drawings.

The drawings are briefly and schematically described. Like numbers refer to like parts and parts with different indices refer to parts with the same or similar functions.

The drawings are as follows.

1 is a perspective view of the structure of the assembled state according to the present invention.

2 is an exploded perspective view of the structure according to the invention of FIG. 1.

3 is a cross-sectional view of the structure according to the invention of FIG. 1.

4 schematically shows the angle between adjacent centering jaws and between adjacent cutter holders with a cutter.

5 is a curve graph for case 1 (prior art).

6 is a curve graph for Case 2 (preferred embodiment of the invention).

7 is a perspective view of a special form of the assembled state of the structure according to the invention.

1, 2 and 3 show the structure according to the invention, ie a new type of "Micro Coax Box", which allows for stripping of significantly thinner cables with better precision than the known "Rotativbox".

The first belt pulley 4 arranged on the top of the rigid main shaft 5 is adjusted via a toothed belt driven by a motor. The first belt pulley 4 transmits the individually adjusted desired torque to the disc cam shaft 24 of the first helical flange 41 via an adjustable friction clutch, which spiral centering jaws (8) via a pin. ) Since the centering jaw 8 is guided in the centering flange 7, the rotation of the disc cam shaft 24 of the first helical flange 41 causes an inward or outward movement of the centering jaw 8. The desired torque, ie the respective force of the centering jaws, is achieved through the initial tension of the spring 27 by adjusting the first nut 2.

The braking force at this time determines the pressing force of the centering jaw 8 applied to the outer surface of the cable sheath. Since the centering jaws 8 are formed in an L-shaped cross section, the centering jaws enable a very compact structure and nevertheless provide a wide centering face or tightening face for the cable to be stripped. The end projects up to the side of the cutter. This centering jaw also provides a relaxation for the guide, where possible due to its L-shape.

A second helical flange 11 supporting the second belt pulley 6 is arranged in two ball bearings 1 coaxially with respect to the first belt pulley 4. The second helical flange 11 also supports the head body 10 via a ball bearing 37. Both the second belt pulley 6 and the head body 10 are driven independently of one another and in some cases differentially via toothed belts. The cutter holder including the cutters 23, 25, 26 is movably supported radially in the cutter flange 12 fixedly coupled to the head body 10. Relative between the second belt pulley 6 and the head body 10 via a cylinder pin 32 which is fixedly engaged with the cutter holder including the cutters 23, 225, 26 and engaged with the second spiral flange 11. The movement causes an inward movement and an outward movement of the cutter holder including the cutters 23, 25, 26, thereby moving the cutter holder in the closing direction or the opening direction. However, in the present invention, other closing or opening devices of cutter holders with cutters, which are known to the expert, may also be used. The relative movement is caused by the speed deviation in driving the second belt pulley 6 or the head body 10.

4 shows the uniformity of the angles observed between adjacent cutter holders with cutters 23, 25, 26 and between adjacent centering jaws 8 respectively and also with cutter holders with cutters 23, 25, 26. And uneven angular dimensions that may occur between and centering jaws 8, respectively.

5 and 6 are curve graphs for the prior art and curve graphs for the embodiments of the present invention, in which case 1 is the result of a test with two cutter jaws and four centering jaws with a cutter and case 2 shows a cutter. The result is a test with three cutter jaws and five centering jaws with the radius deviation (Δr) in case 1 with less support points than in case 2. Therefore, the cutting force change (ΔF: one curve for each cutter) in case 2 is also small. The scale of the y coordinate (level) is determined arbitrarily, while the x coordinate (angle α) contains one complete revolution (= 2π). The temporal course of the cutting force is shown as a sine function for cyclic and simplification, with the usual before and after results not shown. In the observation of vibration overlap, the assumption was made that a symmetrical pattern is applied to the corresponding position in the structure and that vibration is added through linear overlap. In locations where these assumptions do not apply correctly, the same statements are valid, although qualitative, especially with regard to the enhancement of vibration in phase.

The curve can be interpreted in detail as follows:

Case 1:

The first curve shows four double radius deviations over 360 °, more specifically between two adjacent centering jaws each (one r _max ) and at positions that are in contact with all four centering jaws each (one r _min). ).

The equation is: Δr _max (α): = p ₁ · sin (α · n ₁ )

In the second curve, the progression of the force generated in the first cutter is shown for the same 360 °. At the location where the radius is large, the resistance and thus the force are also large. Thus, this curve proceeds synchronously with the first curve.

The equation is: ΔF ₁ (α): = q ₁ · sin (α · n ₁ )

In the third curve, the progress of the force occurring in the second cutter is shown for the same 360 °. Since this second cutter proceeds with a 180 ° deviation with respect to the first cutter, it exhibits the same force change characteristic as the first cutter for the same time. Since the pulses of the first cutter and the second cutter are added, the amplitude in the nougat curve is changed to a value corresponding to twice the second curve or the third curve.

The equation is: ΔF ₂ (α): = ΔF ₁ (α)

Case 2:

The first curve shows five double radius deviations over 360 °, more specifically between two adjacent centering jaws each (one r _max ) and at positions that are in contact with all four centering jaws each (one r _min). ). Since the r deviation is forcibly small at the plurality of contact points of the centering device, the amplitude of the curve is smaller than in the first curve of Case 1. Assuming that there are infinitely many centering encounters, the r deviation will be zero.

The equation is: Δr _max (α): = p ₂ · sin (α · n ₂ )

In the second curve, the progression of the force generated in the first cutter is shown for the same 360 °. At the location where the radius is large, the resistance and thus the force are also large. Thus, this curve proceeds synchronously with the first curve. Since the r deviation is smaller than in the first case, the occurrence deviation of the force is also smaller than in the first case.

The equation is: ΔF ₁ (α): = q ₂ · sin (α · n ₂ )

In the third curve, the progress of the force occurring in the second cutter is shown for the same 360 °. Since this 2nd cutter advances with a 120 degree deviation with respect to a 1st cutter, it shows the force change characteristic which has a 120 degree deviation with respect to a 1st cutter at the same time. The force change curve is thus displaced relative to that of the second curve.

The equation is: ΔF ₂ (α): = q ₂ · sin [(α + (2π / 3)) n ₂ ]

In the fourth curve all are similar to in the third curve. Since the pulses of the first, second and third cutters are added to zero, the amplitude is adjusted to zero in the nobel curve. That is, not only the quantitative decrease of the force pulse but also the qualitative decrease. That is, although cutting at the frequency of the 1st curve of a 2nd part, the overlap of the force by a cutter is not made. The same result can also be seen with four centering jaws and three cutter jaws, in which case the amplitude of Δr will be larger, as in the first curve of the first case.

The equation is: ΔF ₃ (α): = q ₂ · sin [(α + (4π / 3)) n ₂ ]

FIG. 7 shows the process in which the cable end is inserted into the working zone of the cutter holder comprising the cutters 23, 25, 26 from the side in its radial axis.

As described in the embodiments, the present invention mainly relates to a stripping device comprising a centering device having a plurality of centering jaws 8, wherein the number of centering jaws is in the immediately adjacent zone and independently acts in a radial direction. And preferably more than two cutter holders having cutters 23, 25, 26 rotatable about the axis of rotation independently thereof, and the number and arrangement of the centering jaws 8 A phase shift is generated in the interlocking motion of the cutter holder with the cutters 23, 25, and 26 and the centering jaw 8 during the rotary incision with respect to the cutter holder with the 26). Is suppressed or compensated for by increasing vibrations, thereby increasing the cutting precision. Special forms relating to cutter and centering jaws or processor controlled drives are likewise described.

As such, the invention may optionally be arranged and operated as an independent stripping device or as part of a continuous cable processing facility.

** Explanation of Reference Numbers

1 ball bearing

2 first nut

3 braking flange

4 first belt pulley

5 main shaft

6 2nd belt pulley

7 Centering Flange

8 Centering Encounters

9 centering cover

10 head body

11 second spiral flange

12 cutter flange

13 cutter cover

14 guide tube

15 grips

16 2nd nut

17 first spacer ring

18 2nd spacer ring

19 Brass pin (prevents damage from screw pin)

20 Brass Pin (Prevents Damage from Screw Pins)

21 Brass pin (prevents damage from screw pin)

22 bearing

First cutter holder with 23 cutter

24 disc camshaft

2nd cutter holder with 25 cutter

3rd cutter holder with cutter

27 springs

28 Screw pin (for fixing the second nut (16))

29 Screw pin (for fixing the braking flange (3))

30 thread pin (for fixing the belt pulley (6))

32 cylinder pin

34 cylinder pin

35 hex bolt

36 hex bolt

37 ball bearing

39 friction bearing

40 washer disc

41 first spiral flange

Claims (15)

A stripping device comprising a centering device having a plurality of centering jaws (8), The number of centering jaws is in the immediately adjacent zone and acts independently in the radial direction, and independently of that exceeds the number of cutter holders with cutters 23, 25, 26 which are rotatable about an axis of rotation, preferably adjacent In a stripping apparatus in which a first angle is formed in a uniform form between the centering jaws 8 and more preferably a second angle in a uniform form is formed between adjacent cutter holders with the cutters 23, 25, 26. In Stripping device characterized in that the number of centering jaws (8) and / or the number of cutter holders with cutters (23, 25, 26) is not an integer and the first angle is not an integer multiple of the second angle. A stripping device comprising a centering device having a plurality of centering jaws (8), In the stripping apparatus, the number of centering jaws is in the immediate adjacent zone and acts independently in the radial direction and independently exceeds the number of cutter holders with cutters 23, 25, 26 rotatable about the axis of rotation. , The number and arrangement of the centering jaws 8 depend on the cutter holder with the cutters 23, 25, and 26 interlocking the cutter holder with the cutters 23, 25, and 26 with the centering jaws 8 when making a rotary incision. A stripping device, characterized in that it generates a phase shift in operation, the phase shift being suppressed or compensated for by increasing vibration in the cable to be stripped, thereby increasing cutting accuracy. The method according to claim 1 or 2, wherein the number of centering jaws (8) is at least two more than the number of cutter holders with cutters (23, 25, 26) and / or the number can be divided by a common divisor. Stripping device characterized in that there is no. 4. The method according to claim 1, wherein at least one centering jaw 8 is aligned axially with the cutter holder with cutters 23, 25, 26, in particular at rest. Stripping device. 5. The apparatus according to claim 1, wherein when viewed from the drawing plane when the axis of the cable or the axis of rotation of the cutter holder with the cutter is perpendicular to the plane of the drawing, in particular in the resting state Stripping device, characterized in that one centering jaw (8) is aligned in a cable radial direction with the cutter holder with cutters (23, 25, 26). The stripping device according to claim 1, wherein the centering jaws are formed to be rotationally rigid. 7. The centering jaw (8) according to any one of the preceding claims, wherein the centering jaw (8) is rotated about an axis of rotation, preferably in a direction opposite to the direction of rotation of the cutter holder with cutters (23, 25, 26). Stripping apparatus, characterized in that formed possible. 8. Stripping device according to any one of the preceding claims, characterized in that the cutter holder with cutters (23, 25, 26) is arranged in an operating position between the centering device and the cable end to be stripped. 9. The specific position or positions of the cutter holder with the cutters 23, 25, 26 can be determined, the cable end being radially with respect to the axis thereof from the side. Cutter holder and centering jaw 8 with cutters 23, 25, 26 and possibly other second centering devices, tightening devices, so that they can be inserted into the working zone of the cutter holder with 23, 25, 26, or A stripping device, characterized in that a fixing device or possibly other stripping system is formed. 10. The cutter holder according to claim 1, wherein the cutter holders with the centering jaws 8 or the cutters 23, 25, 26 are each placed in one plane and at different points on the cutter edge or at the centering face. Stripping device, characterized in that different lines are assigned to each diameter of the cable or are in tangential contact with the cable. The stripping device according to claim 1, wherein each centering jaw comprises a groove for guiding a contact line of each adjacent centering jaw. 12. A cutter according to any one of the preceding claims, wherein each cutter holder with cutters (23, 25, 26) guides the contact line of each adjacent cutter holder with cutters (23, 25, 26). Stripping device comprising a groove for. The stripping device according to claim 1, wherein there is no common divisor for the number of centering jaws 8 and the number of cutter holders with cutters 23, 25, 26. . The cutter holder according to any one of the preceding claims, wherein the cutter holder with cutters (23, 25, 26) is provided so that at least two different layers of cable can be cut or accessed at two different diameters. A cutter holder with cutters 23, 25, 26 for actuation can be driven radially via the first actuating means, for entering and storing at least two different radial positions and for controlling at least the first actuating device. Stripping device characterized in that an electronic means for providing. The stripping device according to any one of the preceding claims, wherein the stripping device comprises a cutter flange (12) supporting a cutter holder with cutters (23, 25, 26) for cutting at least two cable layers. And a second actuating means for moving the cutter flange 12 to at least two axial positions relative to the cable, preselectable for the cable in the axial direction, to remove at least two cable layers, and Stripping device, characterized in that an electronic means for storing at least two different preselectable axial positions and for controlling at least the second actuation means is provided.

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