DE4305795A1 - Thread tensile force measuring device - Google Patents

Abstract

The present invention relates to a thread tensile force measuring device on a thread processing machine, the measuring body of which is deformed resiliently under loading by the thread and is designed essentially cylindrically and has load applied to it in the direction of its longitudinal axis.

Description

The invention relates to a thread tension measuring device Preamble of claim 1.

Such a thread tension measuring device is used, for. B. on a thread processing machine to check the thread tension there to monitor a continuously running chemical thread.

It is aimed for these thread tension measuring devices, repro to obtain measurable results, d. that is, not just qualitative To be able to make statements about the amount of thread tension, but under the same experimental conditions at the same quantitative Statements to come.

It has been shown that the thread tension occurring in each case fluctuates within certain ranges. This is u. a. on thread attributed to roughness, so that already at an ent high resolution accuracy for different threads speeds result in different thread tensile forces because the Thread roughness has an impact on the measurement result.

Another problem with thread tension measurement is the so-called called wear on thread-guiding elements.

In this regard, the aim is always to be stochastic To detect thread tension change due to the thread roughness, because wear can only be measured reproducibly if the stochastically occurring thread tension peaks reliably can be measured.

The previously known systems for thread tension measurement set this endeavor, however, has limits.

This is due to the fact that the so-called natural frequency the known thread tension measuring devices is relatively low, and thus falsifies the measurement result, under which suffers from reproducibility.  

A thread tension measuring device is also known for which uses a thin glass pin as a thread overflow element, and at which the glass pin fixed on one side in a stationary holder is clamped.

This known thread tension measuring device has the disadvantage a low overload capacity with a high risk of brittle fracture Glass pen on.

It is therefore an object of the invention to carry out a thread tension measurement to create direction with the natural frequencies of at least 100 Kilohertz and higher can be reached.

This object is achieved by the features of the An spell 1 solved.

The advantage of the invention is that for the first time inexpensive and practical high-frequency sensor ready is provided.

In relation to the known solutions, this is high frequency sensor not only extremely resistant to Overload, but also represents a completely new stress principle zip represents which basis for the achievable high eigenfre quenz is.

The invention has recognized that a hollow cylinder not only is extremely pressure resistant, but that it is also very accurate has detectable deformation and also a Eigenfre 100 kilohertz and more.

The invention takes advantage of the knowledge that the Stiffness of a measuring body designed in this way in relation to the mass is extremely high, with materials in particular special light and stiff materials can be used nen.

It is recommended to use the hollow cylinder e.g. B. ceramic or To produce aluminum.  

Without restricting the invention, however, the hollow cylinder can also be made of steel.

A further development of the invention provides for the hollow cylinder To manufacture silicon. This will be discussed later.

Depending on the material used come as measuring devices either metal alloy resistors, e.g. B. Constantan, or Resistors made of semiconductor materials into consideration. The selection of the suitable material depends on the given parameters depending on the size of the expected deformation mung.

The so-called K-factor is essential for the selection for a resistance the quotient from resistance sand tion and associated elongation. The K factor is therefore a Measure of the sensitivity of the respective resistance to the convert expected deformation into a measurable signal.

In the context of the invention, the term "hollow cylinder" is not limited to hollow cylinders. The term "hollow cylinder" includes in particular cylindrical bodies with one of material recesses conditions such. B. concavities, internal hollows, breakthroughs, Cavities, holes, blind holes, embossed cross section with ver permanent retaining walls, the wall thickness of which is thin to very thin, is in particular in the range below about 1 millimeter.

The further development according to claim 2 is particularly advantageous In this case, the invention makes use of the knowledge that the rigidity even with a very thin-walled hollow cylinder is extraordinarily high, but that in addition each of the masses set in motion as a result of the Longitudinal stress decreases with decreasing wall thickness, so that the expected natural frequency increases.

In particular, the training according to claim 3 can be expected that the desired natural frequencies are still exceeded.  

Anyone can produce these thin-walled hollow cylinders common methods are used, in particular the cutting processes, such as. B. loops, particularly should be lifted.

Another method for producing the invention Hollow cylinder is based on producing it from a solid material make which is continuous, preferably under more uniform Movement that is removed by etching.

It is also possible to use the thin-walled hollow cylinder to produce thin-walled tube by drawing.

The development of the invention according to claim 4 offers the front part that pronounced the deformed area of the hollow cylinder is small, which gives the advantage of high kink resistance, and thus a correspondingly high load in the hollow cylinder can be initiated.

For an embodiment of the invention, it should be pointed out that z. B. on a hollow cylinder made of aluminum with the longitudinal dimensions of claim 4 in connection with the wall dimensions according to claim 3, can apply a force in the longitudinal direction, the from a thread running over it on a thread processing machine seems never to be reached.

This results in a further development of the invention extraordinarily high operational reliability, so that even short-term Stresses, e.g. B. by thread printing, the hollow cylinder nothing can wear.

The development of the invention according to claim 5 offers the front part of a symmetrical deflection of the hollow cylinder in Bean saying.

The arrangement of the measuring devices on the hollow cylinder according to claim 6 enables the Messein with appropriate wiring directions harmful influences are prevented, which the knife could falsify the result.  

Here, the measuring devices should preferably only the longitudinal Detect movement of the hollow cylinder parallel to the thread path level is oriented.

Strain gauges (= DMS) into consideration, e.g. B. glued or in the thick film process printed or sputtered. It is however a contactless measurement of the longitudinal movement is also possible, e.g. B. by laser scanning or capacitive or inductive Messein directions.

The development of the invention according to claim 8 is a special attention, since the invention has recognized that the Strain gauges of a full bridge are not necessarily all on the Hollow cylinders must be arranged. So this is the Natural frequency of the hollow cylinder despite the expansion applied Measuring strips (= strain gauges) kept as high as possible.

In this exemplary embodiment, however, the DMS is required on the hollow cylinder with the supplementary resistors. A separate circuit board for the supplementary resistors can be used for this be provided. However, the board does not have to be inside the cavity cylinders are arranged.

The development according to claim 9 offers the advantage that a full bridge thus switched extremely sensitive and reacts quickly to any changes in load.

The development according to claim 10 offers the advantage that in essentially the entire, by upsetting or pulling forth called deformation of the hollow cylinder is included in the measurement.

The further education according to claim 11 makes itself known take advantage of the fact that with low deformation the strain gauges turn out high provide output signal, which only needs to be amplified slightly.

However, it should be said that when using DMS-Wider made of metal alloy through a special circuit Noise can be reliably prevented.  

The development of the invention according to claim 12 offers the Advantage that an electrical short circuit on the surface of the Hollow cylinder is reliably avoided.

The development of the invention according to claim 13 avoids one Pollution or other harmful environmental influences for the sometimes very sensitive strain gauges. In this case it is you not necessary for the hollow cylinder.

The development according to claim 14 offers the advantage of a extremely low mass of the hollow cylinder a very high rigidity speed, the training according to claim 15 tech niche is particularly easy to implement if you have an elec wants to maintain a tric isolating surface.

There are basically two types of loading for the invention Consideration. It is essential in all cases that the hollow cylinder is exposed to longitudinal stress. The direction of the longitudinal stress is essentially parallel to the cylinder walls or to the cylinder jacket surfaces towards the solid Clamping end of the hollow cylinder directed, or away from this.

This means that the hollow cylinder either according to the characteristics of claim 16 is under compression load, or according to the Features of claim 17 under tensile load.

Since the deformation of the hollow cylinder is internal in both cases can play half of the linear elastic range are also assumed that the direction of loading will have no influence on the measurement result, provided you advance sets that in the linear elastic range the mate used rialien a constant independent of the load direction Have spring stiffness.

The training according to claim 18 offers the advantage of an substantially evenly into the load end of the hollow cylinder initiated thread tension, over the entire load-bearing surface of the hollow cylinder is transferred into the cylinder walls.  

A radial dent of individual zones of the cylinder edge areas is reliably excluded with these features.

The development according to claim 19 has recognized that this is appropriate can also offer advantages for the clamping end of the hollow cylinder, and that without influencing the measurement result, since the measuring device Definitely in the area between the stabilization zones are to be arranged.

However, it should be expressly pointed out that the Arrangement of stabilization zones both individually one end of the hollow cylinder is encompassed by the invention as also the joint arrangement of two stabilization zones on the both ends of a single hollow cylinder.

The development according to claim 20 offers the advantage that Thread overflow element can be equipped with a low weight. This characteristic favors the demand for a high natural frequency the thread tension measuring device.

The thread overflow element is in a manner known per se from one Manufacture material with high abrasion resistance and with thread friendly surface, which prefers a small has specific weight. Ceramic is suitable for this Material especially.

The features of claim 21 deserve special attention. On the one hand, silicon combines low properties Weight and high rigidity with each other, on the other hand Silicon extremely resistant to aggressive media. With the features of claim 22, the measuring devices can be integrated directly into the jacket of the hollow cylinder.

It should not be overlooked that the mechanical limits zen in the manufacture of the hollow cylinder according to the invention u. a. can be seen in the application of the DMS, since not arbitrarily small DMS can be applied to any small surface.  

The development of the invention according to the feature of claim 22 in Connection with the features of claim 21 therefore offers the Possibility of moving in motion as a result of the longitudinal load To keep the mass of the hollow cylinder extremely low, so that with a such hollow cylinder easily even natural frequencies of well over 100 kilohertz can be achieved.

The hollow cylinder can for example by known Ver drive how etching or cutting are made. It also comes considering the possibility through lithography, electroforming and molding three-dimensional microstructured hollow cylinders to manufacture.

According to the invention, the measuring elements can be directly on the circuit processed silicon structures are applied, the z. B. with known methods in the cylinder jacket areas have been implanted.

For this, e.g. B. Boron as an acceptor to define the resistance paths to a depth of e.g. B. 4 microns in the silicon structure be diffused. Then the surface of the sili structure opened up to the resistance paths and the elec Trical contact can then be caused by metal vapor deposition be put.

In the following, the invention is illustrated using exemplary embodiments explained in more detail.

Show it

Fig. 1 shows a first embodiment of the invention,

Fig. 2 shows another embodiment of the dung OF INVENTION with arrangement of strain gauges,

Fig. 3 is a front view of the embodiment of Fig. 2 from the top,

Fig. 4 is a developed view of the exporting approximately embodiment according to Fig. 2,

Fig. 5 is a DMS stressed in compression,

6 is cut. A compression cylinder with an elliptical cross,

Fig. 7 shows an embodiment of the invention with a separate board with supplementary resistors,

Fig. 8 is a circuit diagram for an embodiment according to Fig. 7,

Fig. 9 is a bottom view of a exporting approximately example of FIG. 6,

FIG. 10a to 10e examples of various cross-sections for the hollow cylinder in the sense of the invention,

Fig. 11 is an exemplary embodiment of a cast-on train bean hollow cylinder,

Fig. 12 shows a possible embodiment for a stabilization zone at the end of the load.

Unless otherwise stated below, the following description always applies to all of FIGS . 1 to 12.

The figures show a thread tension measuring device 1 on a thread processing machine, not shown. However, such a thread processing machine is generally known. It can e.g. B. can be a spinning system or texturing machine or a spinning-twisting system.

The thread tension measuring device 1 has a fixed, tensioned, resilient measuring body 2 , which is loaded by a thread 3 running above it, deflected in a thread running plane. The load caused by the thread 3 running over it results from the vectorial addition of the parallelogram of forces, the resultant of which lies in the longitudinal axis 14 of the thread tension measuring device 1 .

The resulting thread tension has the reference number 5 . It is a resultant force that has dynamic components. With the thread tensile force measuring device according to the invention, the absolute value of the thread tensile force can be detected at any time in accordance with the amplitude and in the correct phase.

In particular, with the thread tension according to the invention measuring device Peak values of the thread tension are detected, the  Duration is in the millisecond range or shorter. For this reason it is necessary that the thread tension measuring device next to a correspondingly high natural frequency an extremely low one Has damping so as not to distort the measurement result.

This resulting thread tension is due to the dynamic Properties also provided with the index "dyn".

The load on the thread tension measuring device 1 as a result of the resultant force 5 leads to a deformation which is detected and evaluated by a measuring device 6 .

In the exemplary embodiment according to FIG. 1, the measuring device 6 consists, for example, of a pair of capacitor plates 7 , one plate of which is arranged in a stationary manner by means of the holder 8 , while the other plate, together with the thread tension measuring device 1, travels a deformation path 15 , which will be discussed below.

The electrical wiring of the capacitor plate pair 7 is shown as an example. A carrier frequency generator 9 generates an electrical pulse train in a rectangular shape, which was passed through the opposing 10 to a capacitor plate.

In this case, depending on the distance between the pair of capacitor plates, a voltage drops across the resistor 10, which voltage changes continuously.

This voltage is tapped and fed to an evaluation electronics 11 , which can have a measuring amplifier, among other things, in order to then be made visible on the oscillograph 12 .

It can be seen that the amount of voltage, which stood at the counter 10 drops, depends on the distance of the capacitor plates pair 7 , which in turn is a measure of the force 5 introduced into the measuring body 2 .

It should be noted that the capacitive Meßauswer device according to FIG. 1 is only exemplary and that a variety of measurement methods can be used, which can not be listed in detail here.

In other exemplary embodiments, which will be discussed below, so-called strain gauges are used as sensors used.

It is essential that the measuring body 2 is a hollow cylinder which is under longitudinal stress in the direction of its longitudinal axis 14 and parallel to the cylinder walls, the longitudinal deformation of the cylinder walls being detected and evaluated.

In the present embodiment, the hollow cylinder is designed as a hollow compression cylinder 13 , which is stressed in the direction of its longitudinal axis 14 under compression load. However, the invention can also be implemented on a hollow pull cylinder 16 (see FIG. 11) which is under tensile stress in the direction of its longitudinal axis.

In terms of measuring accuracy, both devices are the same valuable, at least as long as the deformation in the linear elastic The range of material properties remains and as long as it remains it can be assumed that the modulus of elasticity for pressure and tension are identical is table.

In the context of the present application, "longitudinal loading" is therefore understood to mean a type of load which is directed in the direction of the longitudinal axis 14 of the hollow cylinder and which either tries to compress it or to pull it apart. A change in length occurs in the cylinder walls, which is to be evaluated as a measurement result.

According to Fig. 1 now the upsetting cylinders 13 will deform in the sense that it is shortened by the path of the swage 15 °. The distance traveled is initially linearly dependent on the resultant force 5 that is introduced and thus a measure of the tensile force actually occurring.

Here, the invention makes use of the knowledge that the hollow upsetting cylinder 13 , and analogously to the hollow pull cylinder 16 , has a linearly elastic load range within which it can be loaded reversibly under pressure or tension in the longitudinal direction.

It is also essential that the hollow cylinders shown are thin dig that their wall thickness 19 are in the millimeter range.

The hollow cylinders are preferably so thin-walled that the Wall thickness is less than 0.5 millimeters. But also with Wall thicknesses of less than 0.1 millimeters, which are technically without further to be realized lies with the usual thread materials the maximum force that can be introduced into the hollow cylinder is still far below half the force that would destroy the hollow cylinder.

Very good results have been achieved with hollow cylinders, their height up to about 15 millimeters.

In this case, even with the very small wall thicknesses A tenth of a millimeter area ensures that one doesn't linear buckling of the hollow cylinder is avoided.

Basically, the invention therefore prefers thin-walled Hohlzy linder, whose wall thickness is less than 1 millimeter and whose longitudinal dimensions are chosen so that kink resistance be stands.

This is an insight into the invention, because as intended, the required natural frequency in the area around Get 100 kilohertz or more.

Figs. 2-4 show now different from the illustration of FIG. 1, that the deformation of the hollow cylinder of strain gauge strip S, D is detected. This deformation occurs as follows:

As can be clearly seen from FIG. 3, the thread 3 runs in a thread running plane which is spanned by the thread running towards the thread overflow element 17 and the thread running off the thread overflow element 17 . During the overflow of the thread over the thread overflow element 17 , the thread is deflected, as a result of which the resulting thread pulling force arises in the direction of the longitudinal axis 14 of the hollow cylinder.

It is essential that ver over the circumference of the hollow cylinder divides, in the exemplary embodiments shown in FIGS. 2-4, four strain gauges are arranged, which are each assigned in pairs and are diametrically opposed to each other.

Two strain gauges are attached to the hollow cylinder so that they are in the sit essentially parallel to the thread plane, and two each further strain gauges are located in a plane that is exactly perpendicular to this. The the former strain gauges are referred to as "subjected to compression DMS "S, while the latter DMS as" stretched DMS "D are called.

As can be seen clearly from FIG. 3, which is a top view of the thread tensile force measuring device according to FIG. 2, compressed strain gauges S alternate with stretched strain gages D in their arrangement on the hollow cylinder 13 , with two adjacent strain gauges in each case are exactly 90 degrees apart.

The zero-degree mark is at that point of the upset cylinder, which is on the inlet side of the thread from the thread running plane is cut.

Accordingly, the 180 degree mark is diametrically opposite, that is on the surface line of the hollow cylinder that is in the thread running level at the expiring point.

For the sake of completeness, it should also be pointed out that in the case of a hollow tension cylinder which is under tension (see FIG. 11), the above applies analogously to the strain gauges stressed by compression, but that instead of the compression load, the term tension stress always applies has to stand.

As the figures show, the hollow cylinder can be designed in this way be that it is symmetrical with respect to the plane of the thread Cross section.

In this case, it is advantageous that no crookedness Bending parts arise during the deformation, which leads to a distortion could lead to the measurement result.

Furthermore, the figures show that the deformation of the cylinder is detected at two points diametrical to the thread running plane, which are arranged essentially symmetrically to the thread plane are.

It can be of considerable advantage that the strain gauges S which are subject to compression are connected to the strain gauges D which are subjected to stretching to form a full bridge, whereby, as shown in FIGS. 7 and 8, the strain gauges which are subjected to stretching are known as supplementary resistors 28, for example can be arranged on a separate circuit board 24 outside the measuring body 2 .

It can be seen that the intended deformation range of the measuring body 2 has dimensions comparable to the dimensions of the strain gauges. This has the advantage that the entire deformation of the measuring body 2 can be detected by the strain gauges.

So if the dimensions of the deformation area, namely the compression area of the upsetting cylinder 13 or the pulling area of the pulling cylinder 16 , are in the order of the dimensions of the strain gauges, the strain gauges are each subjected to a linear deformation on their entire connecting surface to the hollow cylinder.

In an advantageous development of the invention, so-called semiconductor strain gauges can be involved, with the advantage that only a slight amplification of the output signal is necessary. In particular, the embodiments of the invention according to FIGS . 10b, c, d and e are suitable for such strain gages, since they offer favorable attachment points for semiconductor strain gauges.

It is required when using conventional resistance strain gauges Lich to amplify the output signal of the strain gauge accordingly. Should prove that due to the high gain Resistance noise affects the measurement result, so it will beaten to record the output signal of the strain gauge discontinuously sen, e.g. B. supplied with a pulsed voltage or by a bridge circuit powered by pulsed current.

It can now be easily imagined that the compression cylinder or hollow cylinder acted on with a resisting thread tensile force due to the thread friction always present on the thread overflow element 17 not only undergoes a deformation in the longitudinal direction, but also a bend about the longitudinal axis 14 .

It can therefore be expected that the strain gages S which are subjected to compression will be curved accordingly, as shown in FIG. 5.

However, it is a special finding of the invention that the curvature of the strain gages S can have no effect on the measurement result. As can be seen from FIG. 5, the strain gage S that is subjected to compression is curved around its neutral fiber 22 .

This results, based on the strain gauge, a so-called compression zone 20 and an expansion zone 21 , although the influence of compression in compression zone 20 and the influence of expansion in expansion zone 21 mutually neutralize each other.

So it is measured with the arrangement of the strain gauges exactly parallel to the thread running plane and in pairs diametrically to each other only the deformation caused by the compression or extension of the upsetting cylinder or pull cylinder in its longitudinal axis 14 . This deformation leads namely according to the invention without detuning the bridge diagonals of the Wheatstone full bridge to a signal voltage representing the deformation in the longitudinal direction only.

As can be seen in FIG. 6, it may be expedient to equip the hollow cylinder with an elliptical cross section, such that the long semiaxis points in the plane of the thread running direction. This fact can also be seen in FIG. 9, which can be a view of the embodiment according to FIG. 6 from below.

The elliptical jacket 23 is thus oriented in such a way that the upsetting cylinder 13 opposes a bending stress caused by thread friction occurring, the greater of its resistance moments. In the plane perpendicular to this, in which the short axis of the ellipse also lies, the strain gauges S that are subjected to compression are to be arranged according to the invention, while the strain gages D that are subjected to expansion are to be arranged in the plane in which the long semiaxes lie.

As can further be seen in FIG. 9 by way of example, the upper surface of the upsetting cylinder 13 can be made of an electrically insulating material. If the upsetting cylinder consists of light metal or light metal alloy, in particular aluminum, it can advantageously be anodized. This electrically insulating upper surface is then referred to as an anodized layer 29 .

Furthermore, Fig. 7 shows an example of how an inventive hollow cylinder, here upsetting cylinders 13, can be arranged on a machine stage 27. For this purpose, a support arm 25 is used , which is rigidly fixed to the machine frame by means of suitable clamping devices 26 .

The projecting free end of the support arm 25 serves to fasten the upsetting cylinder 13 , which in the present example is loaded perpendicularly to the paper plane by the thread 3 running over it. It is shown here by way of example that the strain gages S which are subjected to compression can sit on the inner lateral surface of the upsetting cylinder 13 . The strain gauges are connected to a separate circuit board 24 by means of suitable connecting lines, which, in addition to the supplementary resistances, also sits the rest of the necessary wiring.

The advantage of this design is that only the strain gauges S additive to the moving mass of the upsetting cylinder, while the supplementary resistors mounted outside do not  Influence on the vibration behavior or the natural frequency of the Have upsetting cylinders.

The output of the separate board 24 then takes place to the evaluation electronics 11 , which, for. B. can be designed according to FIG. 1.

Fig. 8 now shows the local arrangement of cast-on bean compression DMS and S on tensile DMS D to a full bridge.

It is, as I said, essential that only the strain gauges S which are subjected to compression are seated on the hollow upsetting cylinder 13 , while the strain gages D are arranged as so-called supplementary resistors 28 on the separate board 24 .

Between one of the strain gauge S and its adjacent abutment supplement was 28, a supply voltage VS is then applied, while the signal to be detected voltage 55 at the equivalent points of the second resistor pair S, is tapped 28th

Instead of the measuring instrument shown schematically, an elec tronic evaluation is carried out to determine the expected tensile force peaks to be able to record with the required speed.

Furthermore, the figures show that the hollow cylinder is closed at its end loaded by the thread from a stabilization zone 30 , which can be designed differently. Referring to FIG. 1, the stabilizing zone can consist of a simple cap, while in the case of the embodiment according to FIG. 12, the stabilizing zone can be formed of a stabilizing bead at the open end of the hollow cylinder.

It is essential that the stabilization zone all in the mantle of Hollow cylinder takes initiated forces. This will make one Denting of the outer surfaces of the hollow cylinder prevented. From The very even force can also be of considerable importance line in the entire jacket of the hollow cylinder, whereby high linearity is achieved.  

Regardless of the stabilization zone at the thread-loaded end, or depending on it, the hollow cylinder can also be stabilized with a stabilization zone 31 (see FIG. 1) at its fixedly clamped end in the above sense.

With continued reference to FIG. 10 show to e eligible for the OF INVENTION dung substantially cylindrical body into consideration, which have a marked by material recesses 33 cross-section, with the remaining support walls, the wall thickness 19 thin to very thin, especially in the range below about a Millimeter.

This is based on the knowledge that it is precisely the thin wall thicknesses on the one hand, sufficient thread loads Provide stability, but on the other hand guarantee for high natural frequencies and the associated measuring accuracy.

The requirement for low weight is supported by a thread overflow element 17 , which is tubular. This is shown in Fig. 2 by way of example, that the yarn guide member is pierced by a longitudinal bore 17, thus having a weight-saving material recess.

Such thread overflow members can also be used in the case of a train cylinder 16 (see Fig. 11), but the path taken from the thread must be determined through a bore 32 which must be introduced between the thread overflow member 17 and the measuring body 2 .

Reference list

1 thread tension measuring device
2 measuring bodies
3 threads
4 thread tension
5 Resulting, resulting thread tension, dynamic
6 measuring device
7 pair of capacitor plates
8 fixed bracket
9 carrier frequency generator
10 resistance
11 Evaluation electronics
12 oscilloscope
13 hollow upsetting cylinders
14 longitudinal axis
15 Upset deformation
16 hollow pull cylinders
17 thread overflow element, tube, ceramic tube
18 height
19 wall thickness
20 compression zone
21 expansion zone
22 neutral fiber
23 elliptical coat
24 board
25 support arm
26 tensioning device
27 machine frame
28 Supplementary resistance
29 anodized layer
30 stabilization zone, end of load
31 stabilization zone, clamping end
32 hole
33 material recess
D strain gauges subjected to strain
S strain gauges subjected to compression, strain gauges subjected to tension
VS supply voltage
SS signal voltage

Claims (22)

1. Thread tension measuring device on a Fadenbear processing machine with a fixedly clamped resilient measuring body, which is loaded by a, under deflection in a thread running plane, running thread and the resulting deformation is detected and evaluated by a measuring device, characterized in that the measuring body is a hollow cylinder is, which is substantially in the longitudinal direction to the cylinder walls under longitudinal stress, wherein the longitudinal deformation of the cylinder walls is detected and evaluated. 2. thread tension measuring device according to claim 1, characterized in that the hollow cylinder is thin-walled, preferably a wall has a thickness of less than 0.5 millimeters. 3. thread tension measuring device according to claim 2, characterized in that the wall thickness in the range of less than 0.1 Millimeters. 4. Thread tension measuring device according to one of claims 1 to 3, characterized in that the deformation range of the hollow cylinder longitudinal dimension gene up to about fifteen millimeters. 5. Thread tension measuring device according to one of claims 1 to 4, characterized in that the cylinder jacket with respect to the thread running plane sym has metric cross section. 6. Thread tension measuring device according to claim 5,  characterized in that the deformation of the cylinder jacket on two to the thread running plane diametrical points is detected in the arranged essentially symmetrical to the plane of the thread are. 7. thread tension measuring device according to claim 6, characterized in that the deformation of strain gauges (DMS) recorded becomes. 8. thread tension measuring device according to claim 6, characterized in that the strain gauge with two additional resistors as a supplement are connected to a full bridge. 9. Thread tension measuring device according to claim 7, characterized in
that two further diametrically arranged strain gauges detect the deformation substantially perpendicular to the plane of the thread, and
that the strain gauges are connected to a full bridge. 10. Thread tension measuring device according to one of claims 7 till 9, characterized in that the deformation range dimensions essentially in the order of magnitude of the dimensions of the strain gauge. 11. Thread tension measuring device according to one of claims 7 until 10, characterized in that the DMS are semiconductor components. 12. Thread tension measuring device according to one of claims 7 to 11. characterized in that the hollow cylinder has an electrically insulating surface owns.   13. Thread tension measuring device according to one of claims 1 until 12, characterized in that the measuring device on the inner surface of the hollow cylinder sits. 14. Thread tension measuring device according to one of claims 1 to 13, the hollow cylinder made of light metal or light metal Alloy (e.g. aluminum). 15. Thread tension measuring device according to claim 13 in conjunction manure with claim 14, characterized in that the surface of the hollow cylinder is anodized. 16. Thread tension measuring device according to one of claims 1 to 15, characterized in that the hollow cylinder is a compression cylinder, which is in the direction its longitudinal axis essentially under compression stands. 17. Thread tension measuring device according to one of claims 1 to 15, characterized in that the hollow cylinder is a pull cylinder, which is in the direction its longitudinal axis essentially under tensile load stands. 18. Thread tension measuring device according to one of claims 1 to 17. characterized in that the hollow cylinder at its end loaded by the thread from a stabilization zone is completed.   19. Thread tension measuring device according to one of claims 1 to 18, characterized in that the hollow cylinder at its fixed end an end Has stabilization zone. 20. Thread tension measuring device according to one of claims 1 until 19, characterized in that the thread is passed over a thread overflow organ, wel ches is tubular and transverse to the thread lies. 21. Thread tension measuring device according to one of claims 1 until 20, characterized in that the hollow cylinder made of elementary semiconductor material, preferably made of silicon material or germanium Material exists. 22. Thread tension measuring device according to claim 21, characterized in that the shell of the hollow cylinder an embossed half lead has measuring device.