DE102008044465B3 - Profile cutter for even cutting of material strand to lengths, particularly plastic strand profile, has base frame, drive arranged at base frame, cam mechanism connected with drive and control unit for controlling drive - Google Patents

Abstract

The profile cutter (1) has a base frame (2), a drive (3) arranged at the base frame, a cam mechanism (4) connected with the drive and a control unit for controlling the drive. A blade carriage (5) is provided with a blade (51) and an operative connection (52) for a mechanical cam disk (41), and a main carriage (6) is provided with a receiver (61) for guidance and storage of the blade carriage. An independent claim is included for a control method for a profile cutter.

Description

The The invention relates to a profile cutter for uniform cutting to length in the conveying direction uniform and continuously conveyed in a first level of material strand, in particular Kunststoffstrangprofiles, and a control method for a Profile cutter with a controllable and / or adjustable rotary drive and a main slide reciprocable by the rotary drive.

Out In the prior art are different arrangements and associated control methods known to be continuous within a production line funded Cut strand materials in precisely defined lengths.

From the DE 600 317 A Cross cutter for moving paper webs known in which a knife carriage is guided by a straight line back and forth. In this case, an at least partially synchronous movement of the cross cutter takes place analogously to the movement of the conveyed paper web, so that an exact cut of the uniformly moving paper web takes place without the paper web being damaged in the process.

Next is from the DE 195 04 152 A1 an apparatus for cutting a continuously conveyed strand-like sub-molds of equal length conveyed strip of plastically deformable material into individual moldings at the ends of the lower molds in a cutting station, at least one cutting tool being mounted on a reversibly movable carriage. In order to provide a device in which carriage and lower mold are moved over a distance of several centimeters with absolutely synchronous speed to each other, so that deep cuts, for example, for Ortgang- or gable stones can be performed, a cam mechanism is provided to drive the carriage, which moves the carriage over a finite distance at the speed of the strand parallel to its conveying direction. The cam mechanism has a substantially heart-shaped cam and on this applied with the carriage connected guide elements.

From the DE 27 57 823 C2 For example, there is known a web material cutting apparatus that can cut a continuously moving web to a predetermined length during a continuous advance. Here, a controlled power source is used to move cutting blades in synchronism with the web movement and make a precise cut with the cutting blade without jamming or damaging the material.

The DE 694 02 748 T2 discloses a motion synchronization device for acting on a reciprocable cutter which is moved in parallel with a conveyed product line. The speed during cutting is the same for the cutting device and the conveyed product strand, so that no damage to the product takes place here. In particular, an angular velocity control of the drive takes place here as a function of its angle of rotation.

To the Cutting of defined lengths a continuously funded Strand materials serve profile cutter, which on the continuously funded Strand material act by means of a cutting device. The cutting off takes place here in dependence of a defined length through a stop or corresponding sensors, so a uniform cut of continuous and uniform promoted strand to achieve.

Problematic in the known arrangements and methods is that in the state technically used profile cutter very complex are. In particular, many levers and deflections are provided, about a rotational movement generated by a drive in a translational To transform movement.

Farther Due to the design, there is no possibility with the in the state known in the art profile cutters in high-speed cuts perform, around with the production speed of extruded profile producing To draw up machines. The extrusion profile-producing used today Machines have a very high conveying speed, the in the range of 30 cm per second, with one being so fast and continuously funded Strand material required sections of, for example, 7 cm in length are, resulting in a crossover frequency of over 4 cuts per second leads. For this it is necessary to make 250 cuts per minute, which leads to a very high stress of the profile cutter.

The present invention has for its object to provide an arrangement that a kon structurally simple, low-maintenance and subject to little wear profile cutter shows, which is designed for very high production speeds and high cutting frequencies and consequently also high forces and loads resisting.

Further It is an object of the invention to show a control method, that makes it possible one to be carried out Cut in sync with the subsidized Profile, so the cut surface is straight and no upsets and / or strains on the subsidized Profile arise, in particular when the direction of a mitlaufenden profile cutter resulting high forces and the associated burden should be avoided.

Be solved These objects with an arrangement according to claim 1 and a control method according to Claim 10.

Thereby, that the profile cutter for uniform cutting to length in the conveying direction uniform and continuously conveyed in a first level of material strand, in particular Plastic extrusions, with a base frame, one on the base frame arranged drive, connected to the drive cam gear, comprising a mechanical cam, a knife carriage with a knife and an operative connection to the mechanical cam, the knife carriage being in an up and down direction, perpendicular to the conveying direction Movable up and down, a main carriage with a recording to the leadership and storage for the knife carriage and a coupling means for coupling the main carriage to the mechanical cam, one arranged on the frame guidance system to the back and forth of the main carriage along the conveying direction and a control means is designed to control the drive, it is possible a uniform and continuously promoted material strand to cut into short sections. Here is in particular a high cutting frequency possible, because the profile cutter is structurally very simple. It was especially on complicated deflections and levers, as well as waived sensors or the like.

The Arrangement on a base frame allows mass production of the profile cutter independently from the later to use strand production machine, since the base frame easy can be attached to the output of the strand production machine.

Surprised simple and equally efficient is the construction of the arrangement with a cam gear, that for the movement of the knife carriage in an up and down movement direction provides and at the same time the main carriage by means of a coupling agent along the conveying direction moved back and forth.

If the mechanical cam is provided with a milled groove and the Operative connection of the knife carriage arranged on a knife carriage and in the milled Groove free running guide pin is, is particularly efficient up and down movement of the knife realized. In particular, the number of rotating or Moving parts greatly reduced. By this configuration is almost a direct movement of the knife through the cam gear allows.

in this respect forms the combination cam gear with the operative connection to Knife carriage and the coupling means for coupling the main carriage a simple, low-maintenance design with a low wear, which is very high production speeds and high cutting frequencies and consequently also high forces and resisting loads is formed.

By the overall guidance system consisting of the guidance system for the Main carriage and the inclusion of the main carriage to guide the Knife carriage takes a precise guide of the knife along the conveying direction, so that no incorrect positioning of the knife are possible. The combination both guides forms a coherent one Unity, the big ones Loads withstood.

According to the method, the drive is controlled by a periodic control profile with a period T so that the main slide over a predetermined time interval .DELTA.t ₁ moves at a constant speed for controlling a profile cutter with a controllable and / or controllable rotary drive and reciprocated by the rotary main slide being, being .delta.t 1 < T 2 is. As a result, a cut of the material strand to be performed takes place synchronously with the conveyed material strand. In particular, the cutting surface on the profile of the material strand becomes straight and clean due to the synchronicity of the moving blade. An upsetting or stretching or splintering or tearing of material from the material strand is thus excluded.

und eine Asynchronphase mit

, wobei das Durchlaufen bei dem Übergang von einer Phase in die andere Phase stetig in Bezug auf die Winkelgeschwindigkeit erfolgt, ist gewährleistet, dass der Antrieb diese periodische Bewegung schonend vollziehen kann, da kein abruptes Abbremsen oder extreme Beschleunigungen erfolgen, die zu einem schnellen Verschleiß des Antriebes und der Gesamtanordnung führen würden.In particular, the periodic control profile has a parallel running phase

and an asynchronous phase with

, wherein the passage in the transition from one phase to the other phase is continuous with respect to the angular velocity, it is ensured that the drive can perform this periodic movement gently, since no abrupt deceleration or extreme accelerations take place, leading to rapid wear of the Drive and the overall layout.

Thereby, that the control profile is periodic, only the default is done one over the entire period of the defined control profile. This control profile Following, the movement of the knife results along the conveying direction of the material strand. A dynamic change of the control profile is not provided here because a dynamic control in one so fast pace would have to be calculated that too much capacity is needed would. Any changes the control profile due to sensory detected events are equally undesirable because of these changes as well would be associated with intensive calculations of the control profile. The susceptibility of the profile cutter for a failure due to a dynamically changed or incorrectly calculated one Control profile is too big so that should be omitted.

The for a have such a control method used machines Transformation arrangement of a rotational movement in a translational movement on. Here, the period comprises a reciprocating motion of the main carriage, so that this one move from one start position to another Inflection point and then returns to the starting point. This is for a clean cut requires a synchronous runtime. These must be less than half the duration of the period to be sufficient return time to ensure.

The Groove of the cam is as a guide and for receiving the guide pin designed such that the guide pin the width of the groove has, with still a margin is given, the a jamming of the guide pin prevented. It can also be used to further optimize storage be provided, which is the guide pin smooth store in the groove.

Thereby, that recording for leadership and storage of the knife carriage a slot in the main carriage includes, so that the knife carriage perform an up and down movement in the recording can, the knife carriage in the main carriage is sufficient guided, stabilized and intercepted. A stable holder with the slot makes the admission in the main carriage. For better guidance can still more Holding and securing means are provided. It can backup plugs or reserved guide elements be attached to the main carriage so that the knife carriage in the main carriage only along the up and down movement direction can move.

If the coupling means a slot recess in the main carriage and one on the mechanical cam outside the cam rotation axis arranged and in the slot recess freely running eccentric pin is, with the longitudinal extent the slot recess perpendicular to the reciprocating direction the main slide is aligned, is such a simple design the implementation of a rotational movement in a translational movement possible. For this purpose, the co-rotating on the mechanical cam moves Eccentric pin in the slot recess back and forth, the eccentric pin the main carriage along the conveying direction by the translation of the rotation in a translation back and forth.

The Langlochausnehmung is on the back of the main carriage provided with the main carriage to the Cam mechanism is arranged aligned. This in turn can on cumbersome Deflections and levers that would be necessary, at the same time and movement of a main carriage and an up and down movement a knife carriage to realize without two drives at to use such an arrangement.

Thereby, that a common slot is provided in the main carriage, this from the slot of the recording and the slot recess exists, the overall arrangement is made more efficient, so that the profile cutter both production-related and maintenance easier is designed. Furthermore, this makes the overall arrangement still made more compact, so that the profile cutter even smaller can be built and in the later Production environment requires less space.

Around correspondingly high forces or to achieve speeds is between the drive and the cam gear a gearbox / reduction gearbox arranged.

Thereby, that the drive is designed as an electric motor is the Profile cutters can be used in different production plants, there at least everywhere an electrical connection available is. The control of the electric motor via the control means takes place this electronically, this by varying the energy supply can be realized.

If the control means to control the drive a software programmable Control is, can complicated controls of the drive are realized, so that also fast changes in the energy supply of the drive and thus corresponding effects or resulting revolutions and forces of the Drive possible are.

Around a clean and exact cut of the knife into the material strand to ensure, the main carriage has a die holder with a replaceable one Die on, wherein the die to the shape of the material strand to be cut is customizable. By a customizable to the profile of the material strand Die on the die holder is an exact guide of the Material strands in relation to the main slide. As the main slide the knife carriage exactly guided is, can be done so a clean cut.

Thereby, that the knife carriage a changing device for changing the Messers can, so a quick change of the knife without long downtimes take place. The knife change can also be automated done, with a magazine provided by knives on the knife carriage is, for example, be changed periodically.

oder durch die Funktion der Winkelgeschwindigkeit des Antriebes mit

beschrieben wird, mit ν_L = Fördergeschwindigkeit und r_K = Kurbelradius, erfolgt eine exakte Parallellaufphase in Abhängigkeit von der Fördergeschwindigkeit und dem Kurbelradius. Hierzu kann zu jedem Zeitpunkt t die für das Steuerungsprofil notwendige Winkelgeschwindigkeit bzw. Winkelbeschleunigung festgelegt werden. Besonders vorteilhaft ist die Abhängigkeit von nur zwei Konstanten, nämlich der Fördergeschwindigkeit und dem Kurbelradius, so dass die Parameter der geforderten gleichförmigen Bewegung analytisch exakt herleitbar sind.When the parallel running phase by the function of the rotation angle of the drive

or by the function of the angular velocity of the drive with

is described, with ν _L = conveying speed and r _K = crank radius, there is an exact parallel running phase as a function of the conveying speed and the crank radius. For this purpose, at any time t, the angular velocity or angular acceleration necessary for the control profile can be determined. Particularly advantageous is the dependence on only two constants, namely the conveying speed and the crank radius, so that the parameters of the required uniform movement can be derived analytically exactly.

In order to optimize the second phase of the periodic movement, namely the asynchronous phase of the control profile, the asynchronous phase is determined by the function of the rotation angle of the drive f 3 : φ 2 (t) = 1 5 a 4 t 5 + 1 4 a 3 t 4 + 1 3 a 2 t 3 + 1 2 a 1 t 2 + a 0 t + c or the function of the angular velocity of the drive f 4 : ω 2 (t) = a 4 t 4 + a 3 t 3 + a 2 t 2 + a 1 t + a 0 with a ₀ , a ₁ , a ₂ , a ₃ , a ₄ = coefficients of the polynomial function of the fourth degree and c = integration constant described. Here, in particular, the continuity of the angular acceleration in the transition from parallel running phase to the asynchronous phase and vice versa of particular importance for the control profile. The return phase consists of an accelerated movement followed by a delaying movement.

A Adaptation to different product lengths takes place in this asynchronous phase by variation in acceleration or deceleration.

• 1. Startpunkt P1
  
• 2. Endpunkt P2
  
• 3. Steigung im Punkt P1 gleicht der Winkelbeschleungung α_1-Ende
• 4. Steigung im Punkt P2 gleicht der Winkelbeschleungung α_1-Anfang
• 5. Die Fläche unter der Kurve der Asynchronphase entspricht dem verbleibenden Drehwinkel φ_R = 2π – φ_G

The boundary conditions of the equation are set out below, in which case the following prerequisites must be included:

• 1st starting point P1
  
• 2nd endpoint P2
  
• 3. Slope at point P1 is similar to the Winkelbeschleungung α _{1 end}
• 4. Gradient at point P2 equals the angle acceleration α _1-beginning
• 5. The area under the curve of the asynchronous phase corresponds to the remaining rotation angle φ _R = 2π - φ _G

mit den Randwerten R1 bis R4 und der Integrationskonstante C:

Boundary conditions G1 to G5 of the asynchronous phase:

with the boundary values R1 to R4 and the integration constant C:

R1, ..., R4

Randwerte

G1, ..., G5

Randbedingungen

ω₁

Winkelgeschwindigkeit

Δt₁

Zeit für die Gleichlaufphase

T

Dauer einer Periode

t

Zeit

α₁

Winkelbeschleunigung

C

Integrationskonstante

r_K

Kurbelradius

φ_G

Synchronwinkel

The following are the formula symbols used.

R1, ..., R4

boundary values

G1, ..., G5

boundary conditions

ω ₁

angular velocity

Δt ₁

Time for the synchronization phase

T

Duration of a period

t

Time

α ₁

angular acceleration

C

constant of integration

r _K

crank radius

φ _G

synchronous angle

Hereinafter, an embodiment of the profile cutter according to the invention and the control method will be described in detail with reference to the accompanying drawings, in which reference 1 to 5 on the profile cutter and the 6a to 8b on the control process.

In this demonstrate:

1 a spatial representation of an embodiment of the profile cutter with representation of the material strand to be cut,

2 a spatial representation of the main carriage, in particular of the rear side,

3 a spatial representation of the die holder with the die,

4 a spatial representation of the cam mechanism,

5 a spatial representation of the knife carriage,

6a a diagram of the angle of rotation after the time,

6b a diagram of the carriage feed after the time,

7a a graph of angular velocity after time,

7b a diagram of the sled speed after the time,

8a a graph of angular acceleration over time and

8b a diagram of the carriage acceleration after the time.

In 1 is a perspective view of an embodiment of the profile cutter 1 with representation of the material strand to be cut 100 shown. The profile cutter 1 has a base frame 2 ,

The base frame 2 includes a carrier plate, not shown here, and a machine plate, which is shown here in a vertical plane. On the base frame 2 are on the back of the drive 3 and the gearbox 31 arranged. Next to the profile cutter is a control means 8th assigned, which is provided with a corresponding control profile. The control means 8th this can be a PLC, software programmable controller, or a computer control.

The drive 3 is preferably designed as an electric motor, wherein the power is adjusted accordingly to the cut to be performed and the associated movement of the carriage, which will be described below. At the corresponding drive output of the drive 3 , For example, a rotary shaft, there is the transmission / reduction gear 31 that the rotational movement of the generating drive 3 according to the transmission / reduction ratio of the speed reducer / reducer 31 passes. There is an adaptation to the requirements, such as power or speed requirements.

In the base frame 2 is located in a cutout a cam gear 4 , This cam mechanism 4 is with the output of the speed reducer / reducer 31 on the back of the base frame 2 verbun the. In this way, there is a transmission of the rotational movement of the drive 3 to the cam mechanism 4 ,

With the cam gear 4 is a main sled 6 connected. This main sled 6 is located on the front of the base frame 2 , To guide the main slide 6 in a reciprocating direction X is a guide system 7 on the base frame 2 arranged.

The leadership system 7 in this case consists of two horizontal guide rods 71 , each with two guide slots 72 at the outer ends of the guide rods 71 with the base frame 2 are connected. The two horizontal guide rods 71 are arranged parallel to each other.

On the guide rods 71 of the management system 7 can the main slide 6 along the reciprocating direction X are reciprocated. For this purpose are bushings 73 in the main carriage 6 provided that prevent tilting or uneven sliding.

To the reciprocation of the main slide 6 a coupling means is provided, which is the main carriage 6 with the cam gear 4 combines. By means of this coupling agent 62 an implementation of the rotational movement takes place in a translational movement. This is the main slide 6 reciprocated in the reciprocating direction X.

At the main carriage 6 there is a recording 61 for receiving, storing and guiding a knife carriage 5 , This recording 61 is here as a combination of a slot 611 and a guide rail 612 educated.

The knife carriage 5 will be in the slot 611 through the main carriage 6 with a section of the knife carriage 5 , the sliding area 561 , passed through. At the end of this sliding area 561 of the knife carriage 5 there is an active connection 52 ,

The active compound 52 is at the cam gear 4 connected. The active compound 52 serves to transmit a mechanical curve profile, namely a sinuoid profile. The Sinuidenprofil of the cam gear 4 is used to implement a sinoid movement in an up and down movement in up and down movement Y. Further details of the sinuidenprofils of the mechanical cam are discussed below in 4 shown.

Next is on the knife carriage 5 a rail coupling 54 provided that to protect against the slipping out of the knife slide 5 from the recording 61 of the main slide 6 serves. This rail coupling 54 engages in a guide rail 612 one, the guide rail 612 on the main slide 6 is fixed.

On the knife carriage 5 is a knife 51 arranged. This knife 51 performs in analogy to the movement of the knife carriage 5 the up and down movement in up and down movement Y. It intersects periodically according to the Sinoidenprofils in the continuously funded material strand 100 one, so that are cut off from this sections.

At the main carriage 6 is a die holder 64 intended. This die holder 64 has a receptacle for a template 641 on. This template 641 is designed to match the cross-sectional profile of the material strand 100 corresponds and the material strand 100 absorbs and according to the material strand 100 along the conveying direction X, and the reciprocating X direction leads. The matrix 641 serves the knife 51 on the one hand as lateral guidance and on the other hand it acts as an abutment.

In this arrangement can be dispensed with the usual counter blade, since the profile of the material strand 100 sufficiently through the matrix 641 to be led. The knife is in this context designed such that it runs along the side of the die 641 is plan and on the matrices-distant side, the cutting slope is formed. As a result, a clean cut is realized and a clean exact guidance of the knife 51 guaranteed.

following will continue to discuss the operation of the profile cutter.

By the drive 3 a rotational movement is generated. This rotational movement is by means of the cam gear 4 converted into a translational movement in the direction of movement X back and forth. In this case, the movement takes place in the direction of movement X back and forth by the main carriage 6 , At the same time done by the cam gear a second movement, namely an up and down movement in up and down movement Y of the knife carriage 5 with the knife 51 ,

The reciprocating motion takes place periodically, as well as the up and down movement. During a periodic back and forth movement of the main carriage 6 Only exactly one up and down movement of the knife carriage 5 , The up and down movement of the knife carriage 5 takes place within the period half T / 2, in which the main slide 6 moved in the same direction X, in which also the material strand 100 moved, namely the conveying direction X. A synchronization of the material strand 100 and the knife carriage 5 This is not mandatory. For example, elastic materials do not rely on precise synchronism between movement of the strand of material 100 and movement of the knife carriage 5 at. In a plastic profile of the material strand 100 However, for example, for sales displays of store shelves in shopping malls, it is important that over a certain defined path section, a synchronism between movement of the strand of material 100 and movement of the knife carriage 5 is present. This is to the 6a to 8a below, a description is given below.

In 2 is a schematic representation of the main slide, in particular of the back shown.

Here is a common slot 613 at the center of the main carriage 6 , The longitudinal extent of the common elongated hole 613 is in the direction of the up and down movement direction Y, perpendicular to the reciprocating X. The common slot 613 consists of the slot 611 the recording 61 , which is not shown here, but on the front of the main carriage 6 located. Another component of the common slot 613 is the slot recess 63 , The slot 611 serves to accommodate the sliding area 561 of the knife carriage 5 , On the front of the main carriage 6 there is still a guide rail 612 that are part of the recording 61 at the main slide 6 is. This guide rail 612 fits into the management area 562 of the knife carriage 5 , Details will be provided below in 5 shown.

Furthermore, in the slot recess 63 the common long hole 613 an eccentric pin 42 of the cam gear 4 exerting force on the main slide 6 guided. The cam mechanism 4 with the eccentric pin 42 will be detailed here 4 described below. Both the eccentric pin 42 of the cam gear 4 as well as the knife carriage 5 with its sliding area 561 lead a movement in the common slot 613 in up and down movement direction. Part of the sliding area 561 serves as a guide for the eccentric pin 42 , However, the forces generated by the movements of the corresponding transmitting rotational forces are different in nature. The eccentric pin 42 of the cam gear 4 in the slot hole 63 is guided causes a back and forth movement of the main carriage 6 in the direction of movement X. The forces here vary according to the time-dependent position / position of the main carriage 6 within the range of movement along the guidance system 7 , Accordingly, the knife carriage 5 by the coupling of the sliding area 561 of the knife carriage 5 on the walls of the long hole 611 of the main slide 6 carried. At the same time, the guide rail not shown here serves 612 the recording 61 for guiding and stabilizing the knife carriage 5 through the connection with the guidance area 562 of the knife carriage 5 ,

In 3 is the die holder 64 shown. In front of the die holder 64 there is the matrix 641 , The matrix 641 takes the material strand accordingly 100 on and leads this exactly. Especially important here is that for every material strand 100 the matrix 641 must be adjusted or replaced accordingly. It is necessary that the die profile the cross-sectional profile of the material strand 100 equivalent. As a result, as already described above, it is possible to dispense with a counter-blade since a corresponding counter-bearing already passes through the die 641 is realized.

4 shows part of the cam gear 4 , The cam mechanism 4 consists of a mechanical cam 41 which rotates in one about a cam rotation axis R. In this case, there is a coupling to the drive or the over / reduction gear on the back 31 , so that the rotary motion of the drive 3 on the mechanical cam 41 can be transferred.

On the mechanical cam 41 is the eccentric pin 42 , This eccentric pen 42 is located crank radius distance r _K of the cam rotation axis R. The eccentric pin 42 is, as already described above, for the reciprocation of the main carriage 6 in Float X direction. To accomplish this, the eccentric pin 42 an analogy to the rotational movement of mecha niche cam 41 corresponding rotational movement through the guide within the slot recess 63 of the main slide 6 leads to the said reciprocating movement in the direction of movement X.

Next is on the mechanical cam 41 a milled groove 411 brought in. This milled groove 411 has a sinuoidal profile that serves as the knife carriage 5 during one revolution of the cam 41 to move the cam rotation axis R up and down. The sinuoid profile consists of a circle in which a path segment obeys a sinusoidal time function. This time segment is as denting of the circle on the mechanical cam 41 to see. The inside of the milled groove 411 guided guide pin 511 Exactly in this web segment experiences an acceleration in the direction of low movement and at the reversal point an acceleration in the opposite direction of movement Y. Approximately in the turning point, which represents the middle of the bulge of the Sinuidenprofils, is the cut of the knife 51 through the material strand 100 completed. In the rest of the web segment is a resting position in a plane parallel to the strand of material 100 or parallel to the conveying direction X or the reciprocating direction X is located.

5 shows a spatial representation of the knife carriage 5 , Here is the knife carriage 5 with the active compound 52 shown, wherein the active compound 52 here as a guide 511 is trained. Next, the knife carriage 5 a changing device 53 for receiving the knife 51 on. Furthermore, the sliding area 561 to recognize the one in the common slot 613 , more precisely the slot 611 of the main slide 6 to be led. Next is the leadership area 562 to recognize the knife carriage 5 on the guide rail 612 of the main slide 6 leads and restrains secures.

By this configuration of the knife carriage 5 is it possible for this to be along one shot 61 of the main slide 6 moved up and down. Thus, this can be done on the knife carriage 5 arranged knives 51 that in this 5 is not shown, during the up and down movement in up and down movement Y in the material strand 100 penetrate cutting and so a section of the material strand 100 split off.

Below are the 6a to 8b described in connection with the method. The 6a to 8b are divided into a and b, where the index a represents the control function and the index b the reaction of the main slide 6 represents.

bei dem eine Synchronbewegung des Hauptschlittens 6 parallel zu der Bewegung des Materialstranges 100 erfolgt. Diese Parallellaufphase endet bei

Diese Phase entspricht der Parallellaufphase I und ist gekennzeichnet durch die konstante Fortbewegung des Hauptschlittens 6. Diese konstante Fortbewegung des Hauptschlittens 6 folgt der konstanten Fortbewegung des Materialstranges 100.The period of a run is T. Starting point is at

in which a synchronous movement of the main carriage 6 parallel to the movement of the material strand 100 he follows. This parallel running phase ends at

This phase corresponds to the parallel running phase I and is characterized by the constant movement of the main carriage 6 , This constant movement of the main slide 6 follows the constant movement of the material strand 100 ,

beginnt und am Endpunkt der Periode

endet. Während der Asynchronlaufphase II findet der Rücktransport des Hauptschlittens 6 statt, so dass die Periode von Neuem durchlaufen werden kann. Während der Asynchronlaufphase II findet keine gleichförmige Bewegung statt.Following the parallel operation phase I, the asynchronous phase II, the at

begins and ends at the end of the period

ends. During Asynchronlaufphase II finds the return transport of the main carriage 6 so that the period can be run through anew. During the asynchronous phase II no uniform movement takes place.

The 6a and 6b show the movements of the drive, namely the rotation angle in time 6a , and the carriage feed s of the main carriage 6 , namely the carriage feed s after the time. In both diagrams it is quite clear that during the parallel running phase I the movement is uniform. It can also be seen that the control of the drive 3 or the movement of the drive 3 is not uniform, since different distances s or different angles of rotation are covered per unit time.

zu erkennen. Von dieser Ausgangsposition

kann der Hauptschlitten 6 erneut parallel mit der Bewegung des Materialstranges 100 laufen, so dass der Bereich während der Parallellaufphase I dazu verwendet werden kann, dass ein synchroner Schnitt des Profilschneiders, genauer des Messers 51 in den Materialstrang 100 erfolgen kann.The 7a and 7b show diagrams, namely in a the angular velocity after the time and in b the sled speed after the time. Here it is clear how out 7b can be seen that during the parallel running phase I, the carriage feed is uniform. The speed in the parallel running phase I is constant, further corresponds to the carriage speed ν of the conveying speed ν _{L of} the material strand 100 , The speed of the main slide 6 is slowed down in the asynchronous phase, then negatively accelerated, then slowed down and then accelerated again. It is quite clear the sinusoidal feedback of the main slide 6 to the starting position

to recognize. From this starting position

can the main slide 6 again parallel with the movement of the material strand 100 run, so that the area during the parallel running phase I can be used to that a synchronous cut of the profile cutter, more precisely the knife 51 in the material strand 100 can be done.

und im Endpunkt

der Parallellaufphase gegeben ist.The angular velocity ω of the drive during the parallel running phase I is opposite to the speed ν of the main slide 6 not constant, but decreases in the first half and increases in the second. In the asynchronous phase II there is an increase in the angular velocity ω in the first section and then a reduction in the angular velocity ω in the second section. Very important here is to note that the continuity in the starting point

and in the endpoint

the parallel running phase is given.

The 8a and 8b show diagrams of acceleration, namely 8a the angular acceleration after the time and 8b the carriage acceleration after the time.

While in 8b the acceleration of the main slide 6 in which it can be clearly seen that a uniform constant motion in the parallel running phase I through the main carriage 6 is performed, since no acceleration takes place, the angular acceleration α of the drive 3 during the parallel phase I neither zero nor constant.

This graphic makes it clear why a pure sinusoidal or pure linear control of the drive 3 is not sufficient to realize a synchronous phase of the carriage by simply driving the drive. Rather, one needs the above given complex equation, by means of which it is possible, over one period, the main slide 6 by means of the drive 3 to move such that during the parallel running phase I a synchronous cut by means of the knife 51 in the material strand 100 can be done.

1

profile Schneider

100

material strand

2

base frame

3

Drive, rotary drive

31

Over- / reduction gear

4

cam gear

41

mechanical cam

411

Milled groove

42

eccentric

5

blade slide

51

knife

511

guide pin

52

operatively connected

53

changing device

54

rail coupling

561

sliding

562

guide region

6

main carriage

61

admission

611

Long hole

612

guide rail

613

common Long hole

63

elongate recess

64

die holder

641

die

7

guidance system

71

guide rod

72

guide seat

73

bushings

8th

control means

R

Cam rotation axis

X

Conveying direction, Float direction

Y

On- and low movement direction

I

Parallel-up phase

II

Asynchronlaufphase

T

period

t

Time

ν _L

conveyor speed

r _K

crank radius

φ

angle of rotation

s

carriage

ω

angular velocity

ν

carriage speed

α

angular acceleration

a

sled acceleration

a ₀ , ..., a ₄

coefficients the polynomial function of 4th degree

c

constant of integration

Claims (12)

Profile cutter for the uniform cutting of a material strand conveyed uniformly and continuously in a conveying direction (X) in a first plane (P) ( 100 ), in particular Kunststoffstrangprofiles, with - a base frame ( 2 ), - one on the base frame ( 2 ) arranged drive ( 3 ), - one with the drive ( 3 ) connected cam gear ( 4 ), comprising a mechanical cam ( 41 ), - a knife carriage ( 5 ) with a knife ( 51 ) and an active compound ( 52 ) to the mechanical cam ( 41 ), wherein the knife carriage ( 5 ) in a up and down movement direction (Y), perpendicular to the conveying direction (X) is moved up and down, - a main carriage ( 6 ) with a recording ( 61 ) for guiding and supporting the knife carriage ( 5 ) and a coupling means for coupling the main carriage ( 6 ) to the mechanical cam ( 41 ), - one on the base frame ( 2 ) arranged guide system ( 7 ) for the back and forth of the main slide ( 6 ) along the conveying direction (X) and - a control means ( 8th ) for controlling the drive ( 3 ), wherein the mechanical cam ( 41 ) with a milled groove ( 411 ) and the active compound ( 52 ) of the knife carriage ( 5 ) on the knife carriage ( 5 ) and in the milled groove ( 411 ) free running guide pin ( 511 ). Profile cutter according to claim 1, characterized in that the receptacle ( 61 ) for guiding and supporting the knife carriage ( 5 ) a slot ( 611 ) in the main carriage ( 6 ), so that the knife carriage ( 5 ) an up and down movement in the recording ( 61 ). Profile cutter according to claim 1 or 2, characterized in that the coupling means a Langlochausnehmung ( 63 ) in the main carriage ( 6 ) and one on the mechanical cam ( 41 ) arranged outside of the cam disk rotation axis (R) and in the slot recess ( 63 ) free running eccentric pin ( 42 ), wherein the longitudinal extension of the slot recess ( 63 ) perpendicular to the direction of movement (X) of the main carriage ( 6 ) is aligned. Profile cutter according to one of claims 1 to 3, characterized in that a common slot ( 613 ) in the main carriage ( 6 ) is provided, this from the slot ( 611 ) of the recording ( 61 ) and the slot recess ( 63 ) consists. Profile cutter according to one of claims 1 to 4, characterized in that between the drive ( 3 ) and the cam gear ( 4 ) an over / reduction gear ( 31 ) is arranged. Profile cutter according to one of claims 1 to 5, characterized in that the drive ( 3 ) is designed as an electric motor. Profile cutter according to one of the preceding claims, characterized in that the control means ( 8th ) for controlling the drive ( 3 ) is a software programmable controller. Profile cutter according to one of the preceding claims, characterized in that the main carriage ( 6 ) a die holder ( 64 ) with an exchangeable die ( 641 ), wherein the die ( 641 ) an opening with a cross-sectional shape of the material strand to be cut ( 100 ) Has. Profile cutter according to one of the preceding claims, characterized in that the knife carriage ( 5 ) a changing device ( 53 ) for changing the knife ( 51 ) having. Control method for a profile cutter ( 1 ) with a controllable and / or controllable rotary drive ( 3 ) and one of the rotary drive ( 3 ) main carriage ( 6 ), in particular according to one of the preceding claims 1 to 9, wherein the rotary drive ( 3 ) is controlled by a periodic control profile determined over the entire period with a period (T) such that the main carriage ( 6 ) is moved over a predetermined time interval (Δt ₁ ) at a constant speed (ν), wherein .delta.t 1 < T 2 is, the periodic control profile a parallel running phase (I) with

and an asynchronous phase (II) with

has, passing through the transition from one phase (I, II) to the other phase (II, I) steadily with respect to the angular velocity (ω) and in the asynchronous phase (II) the motion with v (t) ≠ const. For

he follows. Control method according to claim 10, characterized in that the parallel running phase (I) by the function (f ₁ ) of the rotation angle φ _{1 of} the drive ( 3 )

or by the function (f ₂ ) of the angular velocity ω _{1 of} the drive ( 3 ) With

is described, with ν _L = conveying speed and r _K = crank radius. Control method according to claim 10 or 11, characterized in that the asynchronous phase (II) by the function (f ₃ ) of the rotation angle φ _{2 of} the drive ( 3 ) f 3 : φ 2 (t) = 1 5 a 4 t 5 + 1 4 a 3 t 4 + 1 3 a 2 t 3 + 1 2 a 1 t 2 + a 0 t + c or the function (f ₄ ) of the angular velocity ω _{2 of} the drive ( 3 ) f 4 : ω 2 (t) = a 4 t 4 + a 3 t 3 + a 2 t 2 + a 1 t + a 0 will be described, with a0, a _1, a _2, a _3, a ₄ = coefficients of the polynomial function of degree 4 and c = integration constant.