DE1402710A1 - Loop lifter - Google Patents

Description

υ 8050 Etefr & jbffa » pjitozyof.L · 10. ^. 1907

United Engineering and Foundry Company

Sling lifter

The invention relates to a looper ^ for chipboard a nen between two devices, for example two VTaIzgerüsten continuously running strip by means of a tensioning roller of a pivotally mounted at a pivot lever is disposed in abutting against a hinge side position at one end of the one arm and the Belt while generating a tension at variable distances from its shortest passage line between the devices or 'Jalzgerüst deflects, for which purpose a piston-cylinder actuator is provided on its arm for the purpose of pivoting the lever and wobex the relationship between the tensioning roller The force exerted, deflecting the belt and the tensile stress generated thereby changes with the distances up to which the belt is deflected from its shortest Larch running line, and the lever arm carrying the tensioning roller on the pivot is connected to one end of a strut, the other End with the piston rod d he piston-cylinder actuator is in communication.

BAO ORiGlNAL

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New documents

The purpose of the invention is to improve the rapid regulation of tape loops, with optimal simplest means.

Several known devices of this type, however, have the disadvantage that the tensile stress caused in the Eand with the angular position of the tensioning pulley supporting

oäer belarms is variable, so that the tensile stress can not be kept constant / only with very expensive means could, resulting in a number of disadvantages, including "fluctuations in the strip thickness and the bandwidth and count unwanted vibrations of the belt. With the known sling lifters it is not possible with a constant actuation pressure of the sole lever to achieve constant tension in the belt independent of the angular position of the lever arm carrying the tensioning pulley, These disadvantages also result in a sling lifter function that is limited only to a very narrow practical range.

These disadvantages also arise in particular from the fact that the adjusting device actuating the lever system is rigidly fixed with respect to this, so that the contact pressure without taking into account the angle of attack of the clamping

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roller lever arm can only be exercised in a fixed parallel sighting.

The object of the invention is to avoid these disadvantages of known sling lifters and to create a sling lifter with the simplest means, with which, in addition to ensuring that the belt tension is kept constant over a significantly extended loop lifter working range, also has a positive influence on decisive factors such as the belt thickness and bandwidth and the salting speed, possible i st.

The solution created by the invention consists in a sling lifter of the type mentioned at the beginning, which thereby is characterized in that the piston-cylinder Bci-c Actuating device one with its free end over a further pivot pin arranged at a distance from the pivot pin hinged strut forms, vrobei the arm carrying the tensioning pulley, the two struts, the two pivot pins and the tension pulley for the purpose of mutual cooperation in terms of their mutual position, the distance between the facilities or roll stands and the variable distances between the strip and its shortest line of travel are matched to each other so that the relationship between the exerted by the tension roller on the belt

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and by the piston-cylinder ßetätigungseinrichtung force exerted in a practically remains constant dependence on the variable relationship between the tape deflecting force un ^r i of the tape tension is available and the tension of the belt, as long as the pressing force in the piston-cylinder Betätigungseinrichtuiig practically constant remains practically constant regardless of the steering distance of the belt from its shortest passage line.

The sling lifter according to the invention is expedient also characterized in that the pivot next to the passage line between the two devices or Rolling stands are arranged and connected by means of the arm to the tensioning roller that the further pivot pin outside the pass line and through fixtures

^ vstrahlweise adjustable- · is and that both pivot pins are relatively f

are adjustable to each other.

A preferred embodiment of the invention Boot lifter is characterized in that the two struts are connected to one another by a joint and the practically constant dependency of the puncture

-2 sin (a + b «)
^ß l

ο _rnfi ι a - ba + b

Z cos _{flI - 2) sin 2

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follows, where R _{1 is} the length of the arm, R _{2 is} the length of one strut, a and b are the angles between the deflected belt and the pass line, and a ¹ and b ^{1 are} the angles of the two struts with an imaginary line through the two pivot pins .

Instead of the one used for the loop lifter according to the invention special form of the actuating device as a piston-cylinder drive are of course also other devices, for example a rack and pinion device or the like. conceivable.

Since the sling lifter lever device according to the invention Can also be used generally with advantage for the significantly simplified construction of tape or strip tension measuring devices Their application is not limited to tape measurements between seaming frames, but also between other obvious pass-through devices.

The technical progress achieved with the invention consists, first of all, of the possibility of to keep a really constant tension in the strip between the devices or roll stands, namely in particular optimally without inertia and with maximum responsiveness as well as with the simplest means · With

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With the loop lifter according to the invention, the sole loop regulation can also take place under the advantageous constant tensile stress conditions in the belt over a wide loop deflection range that has not yet been achieved. These advantageous properties of the loop lifter according to the invention ensure maximum uniformity. speed, in particular the strip thickness and the strip width, a higher rolling speed and also an advantageously narrower distance between the rolling stands.

On the other hand, it is with the invention The sling lifter is also possible in a significantly lighter and far more precise form, On the one hand, it is also easier to measure and, in particular, to consciously adjust it differently in order to also have a positive effect caused by a variety of factors, including metallurgical • Factors affecting certain strip thicknesses and also strip widths, and indeed via a significantly enlarged one Sohlingenhebebetfeich. When coupling the looper pitch pressure with the folding motor or actuator control Finally, a combined control of additional rolling factors can also be achieved, which in particular

especially when all tandem stands of a WaIz plant work together, with the loop lifters arranged in between is effective. For the measurement of whale irregular

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Due to the constant tensile force in the belt, the respective angle of incidence of the tensioning pulley can also be used. ^r he the «

Another advantage of the loop lifter according to the invention also consists in the fact that most of its structural parts are arranged at a considerable distance from the actual belt are, which means that they can be used both in spray water and Vfalzemulsionseinuss as well as in a VJhot rolling mill are protected from the influence of radiant heat or are easier to protect from it. This is especially true for the hydraulic piston actuator the accuracy of which is additionally improved by this protection.

The invention is described below in exemplary embodiments described in more detail with reference to drawings. Show it:

Pig. 1 a plan view of one between two roll stands arranged sling lifting device with the Features of the invention,

FIG. 2 is a side view of the device shown in FIG with additionally drawn rollers of the Roll stands,

Construction ot

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Flg. 3 is a schematic representation of the one described for Facility used control system,

Pig. k is a diagram of forces for the band shown in FIG. 2,

FIG. 5 is a schematic diagram for the illustrated in FIG. put levers,

Flg. $ an explanation of the force diagrams in the preferred embodiment of the invention and

7 shows a schematic side view of a tandem rolling mill with the loop lifters according to the invention.

In Figs. 1 and 2, a loop-controlling fc loop lifter 11 for tapes or strips is shown, with the help of which one from one device to the other, for example from a roll stand 12 to a roll stand 13 running strip S from the normal direct connection line between the roll stands for the purpose of training a loop can be deflected upwards, the size or height of which depends on the free length between the roll stands and the position set by the sling lifter 11 can fluctuate over a wide range.

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The sling lifter 11 has a pivot bearing on the outer End of an arm 15 rotatably mounted on freely rotating tensioning roller 14, the arm! ^ At its other end from one in on the outside of the roll stand uprights 18

and 19 of the roll stand 12 arranged bearings 1? stored Trunnion 16 is carried. In the case of FIGS. 1 and 2 The pivot pin 16 shown is located next to and a little below the belt passage line, namely, the distance of the pivot pin 16 from the pass line is equal to the radius of the tension pulley ~ 4, where however, this distance can also have any other size.

A strut 21 is located at each end of the pivot 16 attached, at the lower end of which a joint 22 is provided in each case. As can be seen, the arm forms I5. and the strut 21 is an angle lever arrangement. Under each strut 21 there is a second, generally designated 23 Strive, polygamy from a cylinder arrangement: 24 with There is associated piston 25 with piston rod, at the outer end of which a pivotably attached to the joint 22 Clevis 26 is screwed on.

As can be seen from Fig. 2, the lower end of each cylinder 24 is mounted on a pivot pin 27 at the end of an arm 28, which in turn is rotatably mounted in bearings 3 ¹

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stored! -Teile 29 is attached. These bearings 3I are attached to the base of the VJalzgerüst near the floor panels. A lever 32 is also wedged onto the ball 29, at the outer end of which a rod 33 is pivotably attached, which rod is provided with a thread over part of its length as seen from its upper end. This threaded part of the rod 33 extends according to Pig. I by one. Gear box Jk through which the thread engages a worm wheel with a central thread, which in turn engages in a suitable worm which can be rotated through a handwheel 35. Since the worm wheel is suitably fastened in the gear box 3 * J- to prevent it from moving vertically when it is rotated, the C-thread rod moves up or down depending on the direction of rotation of the handwheel 35. On the shaft of the handwheel there is a Chain wheel 36, around which an endless chain 37 runs, which engages in a chain wheel 38 of a counter 39 arranged next to hand wheel 35. When hand wheel 35 is rotated, rod 33 moves up or down depending on the direction of rotation, whereby the pivot pin 2? Is shifted to a new position due to the movement of the lever 32. If the cylinder 2k is not under pressure at this moment, its piston moves freely and thereby changes the effective length of the strut 23, whereby the movement of the

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Pivot 2? is compensated. Moved to this whiteness the strut 21 does not, so that the movement of the pivot pin 2? 'the distance between an imaginary line between the pivot pins 16 and 27 and the joint 22 forming the point of connection of the two struts changes. In order to the tension roller 14 keeps the belt under constant tension when a constant pressure is applied to the cylinder 24., the distance between said imaginary line and the joint 22 must be in constant proportion to the piece, around which the tape by the tension roller 14 · from the direct Pass line is deflected. This relationship is through a correct ratio of the struts in relation to the distance between the Vlalzgerusten, the arrangement of the tensioning roller 14 and the arrangement of pivot pins 16 and 2? causes.

A piston-cylinder unit 41 is used to compensate for the Weight of the loop-forming tensioning device and, if desired the weight of the belt against which the tension roller 14 rests. The cylinder 42 of the piston-cylinder unit 41 is pivotally attached to an arm 43 while the outer end of its piston rod 44 is attached to the arm 15 is. Although a special stop can be provided for this purpose, the piston-cylinder unit 41 is used as a stop for the tension roller 14 and the arrangement connected to its piston rod 44 in the through the lower

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End position of the piston rod defined lowest position. In the lowest position of the tensioning roller 3Λ, the upper side is slightly above the horizontal line of the belt, so that it already forms a small loop as it passes the tensioning roller, before the tensioning roller Xk is even swiveled upwards.

In Fig. 3 an example of a control is shown, with the help of which the sling lifter can be used for three different ways of working, namely once while maintaining a constant tension on the belt, and secondly under variably controlled tension on the tape to control the tape dioke or thirdly as a tape tension measuring device. With each of these three Types of application, the result is independent of the angular position of the loop lifter. In an arrangement in which only a constant tensile stress is exerted and this is also to be measured, the arrangement can be considerably simplified will. To illustrate the advantages of the loop lifter according to the invention in detail the following describes a more comprehensive arrangement in which a single system all three different modes of operation enables.

In Fig. 3, the roll stands 12 and 13, the loop lifter

ι BAD ORIQfNAL j

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11 with tensioning roller 14, arm 15, pivot pin 16 and cylinders 24 and 41 as well as the strip S which extends between the rolling stand and whose underside rests on tensioning roller 14 is shown schematically. In this arrangement, the rolling mill is provided on the discharge side 13 is a "known thickness measuring device 45, for example, an X-ray device. The actual Dickenmeßeinrichtuug 45 connected via lines L ₁ and Lp electrically to an automatic setpoint controlled thickness measurement and Hegel 46.

The thickness measuring and regulating device 46 is via lines L _? and Lq connected to a moving coil device 48 which cooperates with a hydraulic ratio regulator 49. For this Hegler, just like for all other components of the system, a commercially available *? Unit can be used that converts a variable electrical input into a proportional hydraulic output. Suffice it to say that the ratio regulator 49 consists of a double-acting cylinder 51 having a piston 52 and a rod 53, many controls the spindle of a pressure regulating valve 54. The piston 52 weiet ewei on with its front and rear sides in Related inner bores 55 endent pivoted mounted in a common opening at the bottom of the piston 56 Pilot it is by a pump 5? fed pluidura

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4 *

the opening 55 from. A horizontal mechanical force brought about by the moving coil device 48 pivots the pilot 56, which in turn moves the piston 52. This moves the pressure control valve 5+, whereby the pressure fluid it emits is fed via a bore 59 to a Bourdon tube 58, which converts the positive pressure into a proportional horizontal mechanical force which is applied to the right side of the pilot. Therefore, if this pressure is equal to the pressure of the moving coil device 48, the correct cylinder pressure will be obtained and maintained as long as that of the caliper and Control device 46 output voltage does not change.

The hydraulic medium for the main system is pumped from a sump 60 by a pump 61 and fed to the pressure regulating valve 5 ** via a line 62. The hydraulic output of the pressure regulating valve 54 brought about by the position of its central protruding field 64 opposite the opening 65 is fed to a drilling 66 which is connected to a main control valve 6? which is connected via a line 66a to the rear end of the cylinder 24 of the loop 11 and keeps it under a constant pressure. A pressure switch 66b serves a purpose which will be explained in more detail later. The spindle of Hauptfteudrvent ils 67 has openings with 70 or? L tu "

00tim / ooio

saramenarbeltende protruding areas 68 and 69 and is displaced in the usual way in one direction by a spring 72 and in the opposite direction by the fluid of an auxiliary valve 73, the fluid supply of which can be interrupted by the piston 7k of a solenoid valve 75.

A valve 76 similar to the main control valve 67 is connected via a line 77 to the pump 61 and via a line 79 to the front end of the cylinder Zk , whereby pressure fluid can be supplied to the front end of the cylinder for the purpose of lowering the tensioning roller 1Λ »The spindle of this valve 76 has three protruding areas 81, 82 and 83 which cooperate with openings 8 * 4 *, 85 and 85, respectively. The axial movement of the spindle is brought about in one direction by a spring 87 and in the other direction by pressure fluid supplied to an auxiliary valve 88 which works together with a solenoid valve 89. The valves 88 and 89 are constructed similarly to the valves 73 and 75 and work accordingly.

A voltmeter 9I is connected to a hydraulic-electrical conversion unit 92, which is arranged immediately at the rear end of the cylinder Zk

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Voltmeters from the Dickenmeß- und Regeleinriohtung 46 and of the voltmeter 91 are displayed, can be determined and compensated for by setting the thickness gauge and control device 46 accordingly. This voltmeter are accordingly calibrated directly to the belt tension. In addition * off the voltmeter 91 serves as a measuring instrument for display the voltage as well as an electrical transmitter whose Operation is described in more detail below.

That in Pig. 3 works as follows: If the sling lifter 11 is to be used to fine-tune fluctuations in the strap dioke over its length and the strap does not have the desired thickness, an electrical pulse representing the error in the diok fluctuation across the strap length is generated via the lines L ^ and Lp from the thickness measuring device 45 to the thickness measuring and regulating device 46. By setting it accordingly, an electrical impulse is transmitted to the reel device 48 and the vertical movement of its spindle is converted into a horizontal force which acts on the one side of the balanced, pivotably mounted pilot 56 of the hydraulic ratio regulator 49 acts. As already mentioned, the other side of the pilot 56 is subject to the hydraulic pressure converted into a horizontal mechanical force

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the Bourdon boring 58 “It can be seen that when the pump 61 is working, the pluidum located in the line 62 occurs regardless of the position of the protruding field 64 ·. . of the pressure regulating valve Sk through this valve and continuously supplies fluid to the hydraulic side of the pilot 56 via the line 59.

Before the rear end of the cylinder 2k Pluidum is fed, both solenoid valves 75 and 89 are energized by suitable, not shown means, whereby the spindles of the valves 67 and 76 are hydraulically moved to the left, so that the areas 82 and 83 of the valve 76 the Openings 85 and 86 close and the areas 68 and 69 of the main control valve 67 open the openings 70 and 71 so that the fluid is only supplied to the rear of the cylinder 2k. The pressure is set by the relative position of the above field 6k in relation to the opening 65 of the pressure control valve Sk , which is determined by the position of the piston 52 of the ratio regulator k9 for setting a hydraulic ratio. In this way, the hydraulic pressure supplied to the rear of the cylinder 2k is made directly proportional to the difference in the variation in thickness, this pressure representing either all or part of the necessary balancing force exerted on the struts 21 of the

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Looper 11 must be exercised. Whether this pressure is equal or unequal to the necessary balancing force, depends on the multiplication effect of the lever system of the loop lifter 11. The compensation pressure is, although it corresponds to the output of the thickness measuring and Hegel device ^ 6 can fluctuate, not influenced by the respective position of the tensioning pulley l * l ·. In other words this pressure is always directly proportional to the fluid pressure of the pressure control valve 5 ^.

If the sling lifter is to be used to give the belt a constant tension and not to be used to correct fluctuations in thickness, the thickness measuring and regulating device is adjusted accordingly. Since, in this case, the thickness measuring device k-5 does not emit a signal via a deviating banr ¹ x thickness, the thickness measuring and control device ^ 6 emits a pulse proportional to the display in the voltmeter and the ratio controller 49 in turn causes the rear side of the cylinder 24 to fall below the correct pressure is maintained. The other valves and elements assume the same positions and work exactly as in the case described above, in which the sling lifter was used to correct deviations in thickness.

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If the sling lifter is to be used as a tape tension measuring device, the solenoid valve 75 is released, whereby the associated piston 7k interrupts the fluid supply on the right side of the main control valve 67 , so that the spring 72 of this valve displaces the valve tip to the right, as in Fig. 3 is shown, and the area 68 pushes in front of the opening 71, whereby the escape of fluid from the cylinder Zk via the main control valve 67 is prevented. The position of the spindle of the valve 76 remains unchanged and, as mentioned above, covers the openings 85 and 86, so that neither the front side of the cylinder Zk fluid is supplied nor fluid can escape at the opposite end.

According to FIG. 3, the ventilation openings and ducts which facilitate the lowering of the tensioning roller Ik in the reverse mode of operation of the cylinder Zk are provided which are necessary for the completion of the hydraulic system. It seems sufficient if it is pointed out that the retraction of the cylinder piston for the purpose of lowering the tensioning pulley Ik takes place by de-energizing the solenoid valves 75 and 89, whereby the protruding areas 82 and 83 of the valve 76 expose the openings 85 and 86 and the protruding areas 68 and 69 of the main control valve 67 close the openings 7 * «

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As a result, pressure is supplied to the front end of the cylinder via the line 79, while pressure can escape from the rear end of the cylinder Zh- via a ventilation line connected to the valve 76.

The * connected to the voltmeter 9 hydraulic-electric Unrvandlungseinheit 92 may also be r still connected to-one cooperating with the roll motor 93 speed control unit 95 also, whereby the operating speed of the V may be regulated alzgerüsts purpose of adjusting the tension of the belt / .

An electrical control system for the V-fold motor 93 of the roll stand I3 serves to control the size of the strip loop between the roll stands 12 and I3 at all times. This system, shown in more detail in FIG. 3, together with the cylinder motor 93, has a _{generator 9 ^ connected via lines L g} and L ₁₀ , which in turn is connected to the speed control unit 95 and a speed regulator 96 connected to a potentiometer 97 is. As shown, the potentiometer is actuated by rotating the pivot pin 16 when the tensioning roller 14 is raised or lowered.

If the sling grows very quickly, i.e. loosely

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and should lift off the tensioning roller Ik when the sling lifter is used as a tape tensioning device, the tensioning roller does not rise under normal conditions in order to remain in contact with the bath, since the cylinder is blocked. To eliminate this possibility , the pressure switch 66b is inserted into the line 66a and responds to a predetermined pressure drop in the line 66a 2k fluid supplies and they ¹ ", the tension roller 14 raises in pursuit of the strip. When the tensioning roller 14 comes into contact with the belt again, the sling lifter works again while maintaining only constant belt tension. Immediately after the tensioning roller 14 has been raised, the potentiometer 97 is actuated and the speed of the roller motor 93 is readjusted, as a result of which the size of the tape loop is reduced to the Ilaxiamlwert. The resetting of the loop lifter to the measuring process is brought about by actuation of a limit switch 98 which also cooperates with the pivot pin 16 and which is actuated when the tensioning pulley 14 is in a predetermined position, whereby the solenoid valve 75 is de-energized and the main control valve 67 is closed.

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In the preferred embodiment, the potentiometer 97 also works in those cases in which the device is set to maintain a constant voltage and acts on the thickness of the strip. Although, as explained above, irrespective of the height to which the strip is deflected, a practically constant tension b can be exerted on the belt by applying a constant pressure to the cylinder Z ^ , it is operationally useful to adjust the height of the loop to be kept relatively constant and preferably at a value lying midway between the extreme upper and lower positions of the tensioning roller.

In the following it is explained why the loop lifter holding the belt under practically constant tension, regardless of the position of the tensioning roller Ik- holds the belt under constant tension within its working range. In the previously known loop lifters, a constant tension could only be maintained if the arms supporting the tensioning roller were always kept parallel or practically parallel to the path of movement of the belt and if the tensioning roller could still only move practically in a vertical direction and exert a constant pressure Facility directly on one of the roller arms in the direction of

BATHROOM O 909811/0010 "

Axis acted. An arrangement of this technique proved to be used, although theoretically sound, impracticable because it too expensive if they meet the above conditions to manufacture and cumbersome to handle

Fundamental geometrical considerations show that when a roller in contact with the strip is arranged in the middle between two devices or rolling stands and forms the junction point between two extendable struts having piston-and-cylinder assemblies connected to it, the other ends of which form located on the center lines of the devices concerned, thereby limiting the movement of the tensioner pulley to a perpendicular path

always
the struts / remain parallel to the belt, the tension exerted on the sand when the arrangements are actuated is always equal to the compressive forces in the struts for all positions of the tensioning pulley. Conversely, a force exerted in the same geometrical manner by the belt on the tensioning roller is proportionally transmitted to the arms of the looper. Using the same geometric analysis, it can be seen that every noticeable change in the geometry produces a belt tension which changes extremely sharply with the height of the tensioning roller. To put it simply, this is based on the fact that the constant

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Relationship between the angles is disturbed.

With the loop lifter described, they need Arne the tensioning pulley is no longer practically parallel until now to the path of movement and the one on the sling lifter exerted force can no longer be applied directly to the tensioning pulley. In addition, it is no longer in the The same amount is required that the tensioning pulley is moved in a vertical direction, so that greater freedom of design is possible and the inertia is noticeably reduced.

In the known arm arrangement working parallel to the belt, the angles of the lever system between the belt and the line of passage of the band, as well as the diaper between the arms and a plane connecting the pivot points of the arms and parallel to the line of passage, were the same regardless of the position of the looper or practically the same. Conversely, the tension exerted on the belt changed and became indeterminate when corresponding angles were not maintained uniformly. In contrast, it has been found that a proportional relationship between the belt tension and the purpose of actuating the snare lifter applied force can be obtained by, in the inventive construction is that

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the individual angles of the belt opposite the direct line of passage and the rail arms are mutually exclusive compensate, thereby exerting a practically constant tension on the belt, even if the range of motion the tension pulley is very large. Algebraically, this relationship can be expressed by the equation

R _?

~ sin (a ^l + b ¹ )
1 const.

2 cos (at - ⁵ ^ Tp- sin

express in which the individual sizes through the geometry an arrangement are determined in which for a predetermined distance between two arranged one behind the other Vfalzgerüst two pivot points can be selected from which d.er one serves as a storage for a VJinkelhebel, at one end of which a tensioning roller is attached xst. With the a pressure medium is connected to the other end of the angle lever

other the one whose opposite end with clen / pivot point in Connection is and forms the link of the system. In such a system the constant relationship remains aich obtained with a change in the deflection height of the belt.

The derivation of the above equation results from that in Pig. ² J diagram of forces shown and the diagram of the angled lever shown in FIG. 5. From the

and

Forces diagram results when T is the belt tension / for ¹ the

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The resulting force on the tensioning pulley 1Λ means:

C = a + b

2 A + (a + b) «180
A = 90 -

B = 90 ■ -. a

D = A-B = 90- - 90 + a -! ■ -

2 T cos 9O.f- = 2 T sin

In the diagram shown in Fig. ^ The resulting de loop pressure force F applied to the V / angle lever with the arms IL and R _{2 is} shown in the angular position resulting from equation (1), on which the cylinder force P continues to act at its point of application .

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The torques around point 0 are:

₁ sin (90 - a «+) = PR ₂ sin (a ¹ + b ¹ )

H B

P sr ² _sin ( _a t _{+ b} i) ρ _

K K

sin

(90 .. a "+ 3-§-SJ cos / a" - & -f ^ J

From equations (1) and. (2) results in:

R ₂ Έ j ~ sin (a '+ b ¹ )

2 T sin = -— ^ 7 ΤΓ - Ϊ respectively.

² cos [3 ? )

-— ^ 7 ΤΓ

cos [a '- 3— ? -

^ sin (a «2 oos (a '- ² ^) sin

For the purpose of explanation, the constancy of the The relationship between tension and pressure shown in the equation above can be illustrated by the fact that actual Dimensions are assumed, for which purpose reference is made to the force diagram shown in FIG. 6. About the theory To fully understand the constant ratio, two different physical embodiments were made selected. In case 1 the lever arms were of the same length,

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while in Pall 2 the arms of the bell crank were unequal. In spring case the tension value was for three different ones Positions of the tension pulley, namely one for a low, the second for a medium and the third for a high Position calculated:

Case 1:

L = 222 inches = 56k cm
1 "= 100 inches - 254 cm
R ₁ ts R ₂ = J * 3 inches = 108 cm a = 65 inches β 165 cm
D = 12 inches = 30.5 cm
E - 6 inches = 15.25 cm

Position 1: H = 2 inches = 5.08 cm

(Conversion factor: 1 inch »25.4 mm) Under these conditions:

a β 0.0185 radians = 1.06 ° b «0.0175" = 1.00 ° a «= 0.Ό465" - '2.66 °

I b «β Tao; o35o = 2.0ο ⁰

(Conversion factor: 1 radian = 57.3 °)

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Inserted in equation 3, the result is

_T | 2 sin (0.0 ^ 65 + 0.0350

Pf S

cosj 0.0 ^ 65 - 'sin ° »° ^{8 01}

0.0815

■ = 2.26

1.998 * 0.018

Position 2: ha H = 10 inches = 25 ^ cm under these conditions

a = 0.0933 radians = 5.35 °

b = 0.0866 «= ΐι ·, 96 ^ο

a ¹ «0.23 ^ 7 ^B = 13.45 °

b ¹ = 0.1702 "= 9.75 °

Inserted in equation 3, the result is

sin (0.23 ^ 7 + 0.1? 02)

9 on «= / η ^ L7 0.0933 - 0.0866 I. 0.0933 + 0.0866

0.3939

'= 2.25

0.0898

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Position 3; H = 22 inches = 55.8 cm

Under these conditions is

a = 0.2125 radians = 12.18 °

b = 0 , 1812 dd = 10 .38 " a « = 0 , 5371 If β 30 , 77 ° b ' = 0 , 35U = 20 , 12 °

Inserted in equation 3, this gives

_T ^ ain (0.5371 + 0.351l}

^P ΤΤΤΖΤΤντι 0.2125-0.1812 ]. 0.2125 + 0.1812 2 cosiO, 5371 - - '" - / sin - * ■ —5— *

2 /

J & 0.7760

-ÜJ _β 2.29

* 0.1956

Obviously, the maximum fluctuation when using this inventive tensioning unit is only -0.88 %.

222 Pall 2: 254 cm L β 100 Inch = 108 cm 1 «= 43 Inch = 101 cm H ₁ = UO Inch β 165 , 5 cm R ₂ = 65 Inch = 30th cm a = 12th Inch = 15th , 5 cm D = 6th Inch = , 25 cm E β Inch =

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Position 1; H = 2 inches - 5.08 cm

Under these conditions is

a ■ 0.0185 radians = 1.06 ° b - 0.0175 "« 1.00 °

a «= 0.0465 * = 2.66 °

b ¹ ·· = 0.0310 «β 1.78 °

Inserted in equation 3, the result is

sin (0.0465 + '0.031O)

0.0185 + O.OI75

J, V "fU"> - ^ J ».!. Χ"

cos / Ό, 0465 - 0.018.5 - 0.0I ₇ ? j ^ ^

0.0774

- 2 00

1.998. 0.018

Position 2; H * 10 inches - 25.4 cm
Under these conditions is

a * 0.0933 radians - 5.35 ° b = 0.0866 «« 4.96 °

a "= 0.2347 '-' - 13.45 ° b '- 0.1511 ^K = 8.60 °

Inserted in equation 3, the result is
sin (0.2347 + 0.15H '

0.0933-0.0866]. .0933 + O.086rl y ^sin 2

cos (0.2347 - 0866j _slK
0.3763

₌ 2.00
1.947 x 0.0898

90981 1/0010

Position 3: 'H = 22 inches = 55.8 cm under these conditions

a β 0.2125 radians - 12.18 °

b « 0.1812 Il = 10.38 ° a »« 0.5371 Il - 30.77 ° b «= 0.3022 ti - 17.32 °

Inserted in equation 3, the result is

** ° sin (0.537I + 0.3022?

ο nnain w \ 0.2125 ~ 0.1812 ) ^, ^ 0.2125 + 0.1812 cos / 0.5371 - / sin ■ '-

= 2.0if

. 0.1956

909811/0010

It can be seen that the maximum fluctuation is

• 4-

Turn this sling lifter only inventive - I ₁ OO% · I

Pig. 7 shows the combined use of the sling lever between all stands 101-106 of a tandem mill, "in which on the output side of the first five stands the Schlingen'.ieber 107, 108, 109, Hl and 112 are provided, each of which can be used in one of the three ways described above, i. to exercise a constant tension to exercise a variably adjustable tape tension or as a tape tension measuring device.

In a rolling mill, for example, the loop lifters 107 »108 and 109 a constant tension on the strip as it passes from the stands 101 and 102, 102 and 103 as well 103 and IOki- exercise while the last two looper 111 and 112 serve as tape thickness controls and are accordingly combined with tape thickness gauges 113 and H ^ are, of which the Eanddickenmeßgerätl13 with the looper 111 and the tape thickness measuring device 11 *} · with the looper 112 as described works together.

By using a loop lifter ensuring constant tension in all or practically all stands, the tension in these stands during the 'ialzvorgangs is always proportional to the predetermined optimum pressure of the cylinder 2ty, which makes it too strong

909811/0010

U02710

Tension of the tape is eliminated and, accordingly, fluctuations in tape thickness and width based on such excessive forces are avoided. In addition, one or more loop lifter as Di ⁿ kenmeßgeräte can be used and cause a fine correction of the fluctuations in the strip thickness throughout its length.

But loop lifter of the invention may also to all the scaffolding used to gauge regulation no or hold on to the first stands the belt under constant tension and are used in the last stand or the last stands as a voltmeter. This use avoids excessive tension if the last folding machines are equipped with devices for controlling the fluctuations, the strip thickness by readjusting the motor speeds, or by changing the roll adjustment for the same purpose, both systems providing a target / actual value control signal from a thickness measuring device obtain. In this application, the sling lifter prevents excessive tension from being created during rolling.

In addition to those specifically embodied, the invention also encompasses all further conceivable combinations of the disclosed features.

BAD GfMGiNAL 909811/0010

Claims (3)

140271Q U 8050. United ^ Engineering and Foundry Company claims 1. LooperVzuHi Tensioning a belt that runs continuously between two devices, e.g. two rolling stands, by means of a tensioning roller which is arranged at one end of one arm of a lever pivotably mounted on a pivot pin in a position lying against one side of the belt and the belt in variable distances from its shortest passage line between the facilities or rolling stands, for what purpose. Using the lever, a piston-cylinder actuating device is provided on his arm and the relationship between the force exerted by the tensioning roller, deflecting the belt and the tension generated thereby in this with the distances up to which the belt is at its shortest Passage line is deflected, changes, and the lever arm carrying the tensioning roller is connected to the pivot mi ⁴ , one end of a strut, the other end of which is connected to the piston rod of the piston-cylinder actuating device, characterized in that the piston-cylinder Actuating device (2k, 25) a strut (23) articulated with its free end via a further pivot pin (27) arranged at a distance from the pivot pin (16) 9 0 9 8 11/0010 " ² " forms, with the arm (15) carrying the tensioning roller (14) * the Deiden struts (21, 23), the two pivot pins (16, 27) for the purpose of common and the tensioning pulley fäü = their = possible interaction mutual
with regard to their gfiDa & iHsamKK Lagt, the distance between the devices or roll stands and the variable distances of the strip from its shortest passage line are adapted to one another in such a way that the ratio between the force exerted by the tensioning roller on the belt and the force exerted by the piston-cylinder actuating device is in a practically constant dependency on the variable ratio between the force deflecting the belt and the belt tension and the tension of the belt as long as the compressive force in the piston-cylinder actuator remains practically constant regardless of the deflection distance of the belt from its shortest main running line is held. 2. sling lifter according to claim 1, characterized in that the pivot pin (16) next to the pass line between the two devices or roll stands (12, 13) arranged and connected to the tension pulley (14) by means of the arm (15) is that the further pivot pin (27) outside the Passage line is located and is optionally adjustable by devices (351-35-) and that both pivot pins (16, 27) are adjustable relative to each other. 90981 1/0010 H02710 3. sling lifter according to claim 1 or 2, characterized in that . _x net to the belt in such a way that the arm (15) socjgsgsnütoKixxisiiKiEaxiJd (S) is arranged so that an imaginary line running through the first-mentioned pivot pin (16) and the center of the tensioning roller (14) does not run parallel to the belt when this is out of the DuroLlauflinie is deflected, and that the two struts (21, 23) on the pivot pin (.16) form an angle with the arm (15). Fourth sling lifter according to one of the preceding claims, characterized in that the two struts are connected to one another with a joint (22) and the dependence of the action ^R 2, which remains practically constant = - sin (a ¹ + b *) away
2 cos (a ¹ - 2Γ ) sin follows (15) ttt where R _{1 is} the length of the arm ^ R _g d the length of the one Strut (21), a and b denote the angles between the deflected belt and the pass line and a ¹ and b ^{1 denote} the angles of the two struts with an imaginary line through the two pivot pins. 90981 1/0010