EP1985420A1 - Cutting device for shortening component belts, supply device and automatic loader - Google Patents

Abstract

The cutting device shortens belts on a mounting machine. It has a housing (13), with a belt channel (14) formed in it, a cutter cutting the belt across the conveying direction, and a belt holding device (31) containing first and second clamping elements (36, 37) to clamp the belt. The belt holding device enables the belt to be fixed relative to the housing between the clamping elements.

Description

The invention relates to a cutting device for shortening component belts, a feeding device and a placement.

In a placement machine for loading substrates with electrical components, the components are provided by feeding devices arranged on the placement machine. The electrical components are often stored in pocket-like depressions of a correspondingly long component belt. The component belt is transported by means of a transport mechanism of the feeder by the feeder, wherein the components are removed at a pick-up position of a placement of the placement of the pickups. The empty belt leaves the feeder at a suitable location. Often, there is a need to cut the empty component belts after exiting the feeder at certain intervals to bring the residual waste into a manageable form. Repercussions on the pick-up positions of the components due to the cutting process lead to positioning inaccuracies and therefore to a deterioration of Bestückvorganges.

From the patent DE 19604608 For example, a cutting device for a placement machine is known, which extends over the entire width of the feeders arranged on the placement machine and cuts off the component strips by means of a single long and movable cutting knife. The cutting of the component straps by a scissor-like movement of the movable cutting blade against a correspondingly long formed cutting edge. In this cutting device, the component straps protrude with their loose end in the cutter. This can lead to disturbances such as the jamming of component straps between the cutting blade and the cutting edge, which then leads to a Tugging on the straps and thus can lead to changes in the position of the components at the unprotected pickup positions.

It is therefore the object of the present invention to provide a cutting device for component straps, which has a higher reliability.

This object is achieved by the cutting device and the associated feed device and the associated placement according to the independent claims.

The cutting device for shortening the component straps according to claim 1 has a housing, a belt channel, which is formed in the housing for passing the component belts to be shortened in a conveying direction and a cutting device which cuts through the component belt guided in the belt channel transversely to its conveying direction. Furthermore, the cutting device has a belt holding device for fixing the component straps, which comprises at least a first and a second clamping element with mutually facing clamping surfaces for clamping the component straps, wherein the belt holding device is configured such that the component straps between the clamping elements are fixed relative to the housing stationary. Such a configured cutting device has the advantage that caused by the cutting effects on the pickup positions of the feeders can be avoided, for example, by snagging and tearing the cutter on the component straps on the component straps. For a higher reliability is feasible.

In one embodiment of the cutting device according to claim 2, the cutting device is provided in a direction transverse to the conveying direction displaceable on the housing, such that during the process of the cutting device guided in the belt channel component belts are severed transversely to its conveying direction. Such a cutting device can be arbitrarily adapted to the width of the belt channel and thus to the length of the travel path of the cutting device.

In one embodiment of the cutting device according to claim 3, the cutting device additionally comprises a deflection device. The first clamping element of the belt support device is formed as at least one clamping belt, which extends in the direction of displacement over the entire travel distance of the cutting device, is guided over the deflecting device and at both its ends firmly anchored in the housing, that together with the second clamping element a catching area for the component straps is formed, which tapers to an effective range of the cutting device. In this case, the region of the cutting device in which a component belt guided in the belt channel is severed is defined as the effective region or contact region. If a component belt is grasped by the catching area of the cutting device and fed to the effective area of the cutting device, the pockets of the component belt are compressed by the tapering catch area. With the help of this schematic arrangement, even component belts with deep pockets can easily be fed to the cutting device and subsequently severed.

In one embodiment of the cutting device according to claim 4, the deflecting element has at least one rotatably mounted deflection roller. In contrast to a fixed deflection element are at a rotatably mounted pulley significantly better friction conditions. Furthermore, the rotatably mounted deflection roller can also be used as a drive element for the clamping belt.

In one embodiment of the cutting device according to claim 5, the standing clamping belt is guided by means of a so-called omega deflection by the cutting device. By means of this omega belt guide can be as large a deflection be achieved over the drive roller, which brings with it corresponding advantages in power transmission. Furthermore, this type of deflection allows a favorable geometric design for the capture range of the cutting device.

In one embodiment of the cutting device according to claim 6, the cutting device on a deflecting device. Furthermore, the first clamping element of the belt holding device is designed as at least one closed circumferential clamping belt, which is guided over the deflection device and movable with the cutting device. The circumferential clamping belt is arranged such that between the clamping belt and the second clamping element a catching area is formed, which tapers towards the effective range of the cutting device. With the aid of this embodiment, even component belts with deep pockets can be easily fed to the cutting device and severed.

In one embodiment of the cutting device according to claim 7, the clamping belt is coupled to a drive such that the belt speed in the effective range of the cutting device, i. in the position of the smallest distance of the clamping belt to the second clamping element, is equal to the speed of movement of the cutting device. By contrast, it is to be understood that the two velocity vectors are oppositely directed and of equal magnitude. When the two vectors are added, the zero vector is obtained. Although the clamping belt is movable with the cutting device, is ensured by the coupling with the drive that the component straps are fixed in place not only between the clamping elements, but also relative to the housing. In addition, as a result, the belt holding device can be kept compact and arranged in the immediate vicinity of the cutting device.

According to one embodiment of the cutting device according to claim 8, the clamping belt is guided such that both during Method of the cutting device in the direction of displacement and in the opposite direction, the component straps fixed to the effective range of the cutting device can be fed. It should be noted in particular that a catching area is formed between the clamping belt and the second clamping element on both sides of the cutting device. By means of this arrangement, the component straps can be severed both in the process of the cutting device in the direction of displacement and in one of the direction of displacement oppositely directed opposite direction. "Empty runs" of the cutting device back to its original position are avoided.

In one embodiment of the cutting device according to claim 9, the second clamping element is formed as a closed, circumferential clamping belt. The resulting advantages for the second clamping element corresponding to those of the first clamping element according to the statements to the claims 6 to 8.

In one embodiment of the cutting device according to claim 10, a housing part of the cutting device can be used as the second clamping element. The capture region is consequently formed by the first clamping element, which may be formed as at least one stationary or circumferential clamping belt, as well as by the housing part as a second clamping element. This minimizes the mechanical complexity of the cutting device, resulting in lower susceptibility to interference and thus lower maintenance.

In one embodiment of the cutting device according to claim 11, the clamping belts are made of adhesive material. As a result, the frictional connection between the clamping belt and the component belt when clamping the straps can be improved. Frictional and slip effects between the clamping belt and belt are thus avoided or minimized. Alternatively, it is also possible to make the clamping belts of a material having an abrasive surface.

In one embodiment of the cutting device according to claim 12, the deflecting device is formed elastically transversely to the displacement direction, so that the distance from the first to the second clamping element to the thickness of the component straps is independently adaptable. This can be realized for example by a prestressed spring element. This ensures that the cutting element can not be separated from the counter element, in particular in the case of wide component straps with deep pockets, which are also thicker in the compressed state. Also, these thicker component straps can be safely perform so with the cutter. The prestressed spring element may be formed, for example, as a spiral spring. However, there are also other structural configurations such as disc spring assemblies, electrical or pneumatic solutions conceivable.

In one embodiment of the cutting device according to claim 13, the cutting device comprises a cutting unit, which has a rotatably mounted cutting element with at least one cutting edge formed on the circumference, and a counter unit, which has a counter element. Cutting unit and counter unit are arranged such that upon rotation of the cutting element, the at least one cutting edge of the cutting element interact with the counter element in the so-called active or contact area such that when moving the cutting device guided in the belt channel component belts are severed transversely to its conveying direction.

Such a cutting device is arbitrarily adaptable to the width of the belt channel and thus to the length of the travel path of the cutting device by its structural design. A jamming of the component straps due to deflection, for example, the cutting or bar knife is no longer possible in this case. As a result, higher reliability can be realized.

In one embodiment of the cutting device according to claim 14, the cutting element are designed as a rotatably mounted roller blade with a peripheral edge formed on the cutting edge and the counter element as a rotatably mounted pressure roller with a peripheral pressure surface formed. Cutting unit and counter unit are arranged such that upon rotation of the cutter blade, the cutting edge of the roller blade rolls on the pressing surface of the pressure roller. With this configuration, a simple and cost-effective solution both in terms of production and maintenance can be realized.

In one embodiment of the cutting device according to claim 15, the cutting device on a biasing device which presses the roller blade and the pressure roller in a working position against each other, so that the component straps are separated by a squeezing between roller blade and pressure roller. In the simplest case, the biasing means can be realized via a compression spring. The fact that the component straps are squeezed and not sheared off as in cutting, jamming of the component straps is excluded. Furthermore, the squeezing operation takes place essentially without a relative speed between the component belt and the cutting edge of the roller blade at the point of intersection. The formation of Gurtfasern, which can jam the knife, is no longer possible. Also, the removal of microparticles, such as occurs when sawing, can be avoided. As a result of the squeezing process, virtually no dust particles are generated, so that the contamination can be minimized, which likewise contributes to increasing the operational safety.

In an embodiment according to claim 16, the cutting element is designed as a rotatably mounted stamp wheel with two cutting edges formed on the circumference. The counter element has a likewise rotatably mounted die wheel with a recess formed on the circumference, in which the punch wheel at least partially immersed. In the simplest case, the stamp wheel has a cylindrical shape. The recess may be formed as an annular groove. The width of the annular groove is to be chosen so that the dimensioned only slightly larger than the thickness of the stamp wheel. As a result, in the process of the cutting device, the punch wheel and the die wheel cooperate in such a way that the component belts are severed by a double cut at the two cutting edges of the cutting element. By this punching separation process, a piece is punched out of the component belt to be cut through, the width of which corresponds approximately to the width of the annular groove.

Since the two cutting edges of the stamp wheel each have an angle of about 90 °, injuries, such as those that can occur on a sharp cutting disc, for example in the context of maintenance, can be avoided. In order to achieve a better collection of the material to be cut in the cutting unit, the end face of the stamp wheel can be performed fluted or knurled.

In one embodiment of the cutting device according to claim 17, the cutting edge of the cutting element and the cooperating with the cutting element areas of the counter element are made of hardened material. As a result, the wear behavior of the tools is improved, thus increasing the stability, which in turn has a positive effect on maintenance costs and reliability.

According to one embodiment of the cutting device according to claim 18, the component straps can be severed when moving the cutting device both in the direction of displacement and in a direction opposite to the opposite direction. A "Leerfahrt" of the cutting device, ie a movement back to the starting position is not necessary, which significantly increases the process safety and the efficiency of the cutting process. Furthermore, malfunctions can For example, be avoided by tangling or jamming of the shortened component straps in the mechanics of the cutting device, which also contributes to an improvement in process safety and the stability of the cutting device.

An embodiment of the cutting device according to claim 19 further comprises a linear drive, by means of which the cutting device in the displacement direction or in the opposite direction is movable, and a rotary drive for the cutting element. In this case, the rotary drive is coupled to the linear drive such that the circumferential speed of the at least one cutting edge of the cutting element in the area of contact with the counter element is equal to the travel speed of the cutting device. By this arrangement, a nearly relatively speed-free crushing or cutting operation can be realized, so that the component straps can be cut clean. In addition, less polluting microparticles or belt fibers occur.

According to one embodiment of the cutting device according to claim 20, the rotary drive comprises a rack, which is provided on the housing and extending in the direction of displacement, a gear which is in engagement with the rack and a shaft through which the gear is connected to the cutting element such that in the process of the cutting device, the cutting element is set in rotation. Alternatively, it is also possible to attach a toothed belt to the housing instead of a rack and to use, instead of a gear, a pulley which engages with the toothed belt and is connected to the cutting element in such a way that it is set in rotation.

By this structural design, a structurally simple mechanical rotary drive for the cutting element can be realized. Furthermore, it is when choosing a suitable transmission ratio It is possible to realize this by separating the component straps between the at least one cutting edge of the cutting element and the contact area of the counter element substantially without any speed. A suitable transmission ratio is present, for example, when the effective circle diameter of the gear wheel equals the diameter of the cutting element. Such a designed mechanical rotary drive has the advantage that neither a power supply nor a controller are needed. Last but not least, it is a solution that is robust with regard to maintenance and servicing, and ideally suited for continuous use in the production environment.

An embodiment of the cutting device according to claim 21 further comprises a linear drive, by means of which the cutting device in the displacement direction or in the opposite direction is movable, and a rotary drive for the counter element. In this case, the rotary drive is coupled to the linear drive, which is the peripheral speed of the counter element in the contact region with the at least one cutting edge of the cutting element against the speed of movement of the cutting device. With regard to the advantages of this embodiment, reference is made to the comments on claim 19.

In an embodiment of the cutting device according to claim 22, the rotary drive comprises a rack, which is provided on the housing and extending in the direction of displacement, a gear which is in engagement with the rack and a shaft through which the gear is connected to the counter element such that when moving the cutting device in the direction of displacement, the counter element is set in rotation on. Alternatively, it is also possible to provide a toothed belt on the housing instead of a toothed rack and to use a pulley instead of a toothed wheel, which meshes with the toothed belt and with the counter element is connected in such a way that it is set in rotation.

Due to this structural design, the rotary drive can be realized simply robust and cost-effective. Furthermore, a selection of a suitable transmission ratio, a virtually relatively speed-free crushing or cutting operation can be easily realized. A suitable gear ratio is present, for example, when the effective circle diameter of the gear corresponds to the diameter of the counter element in the contact area.

According to claim 23, a cutting device is claimed in which the cutting device is formed such that the cutting unit and the counter unit relative to each other between a working position of the cutting device in which the cutting element and the counter element cooperate and a securing position in which the cutting element is separated from the counter element , are slidably mounted. Furthermore, a securing mechanism is provided, which is designed such that when a maximum force occurring during the cutting process is exceeded, the cutting unit is separated from the counter unit. This can be realized for example by pivoting the separating element and is z. B. necessary if components that were not picked up in its pickup position from the placement and are left in the belt pockets, get into the engagement area of the cutter. In this case, the cutting device can be moved into the securing position in an attempt to sever the straps with the components therein, in order to avoid damage to the cutting device, especially at the at least one cutting edge of the cutting element.

Furthermore, the destruction of remaining in the pockets of the component straps tantalum capacitors must be avoided. Released and finely divided tantalum reacts violently with the ambient air and can lead to burns under high heat. These risks are taken into account by moving the cutting device into the securing position. However, it is also possible to detect any obstacles on the current consumption of the motor and to interrupt the cutting process electrically controlled.

The cutting device according to claim 24 shows a belt channel which has return mechanisms at both ends in the direction of displacement and / or in the opposite direction. These serve to transfer the cutting device from the securing position back to the working position. As a result, a cutting device located in the securing position can be returned to the working position at the end of each travel path. An intervention of the machine operator is not necessary.

According to claim 25, the return mechanisms of the cutting device are designed as two-sided inlet slopes. The transferring of the cutting device from the securing position into the working position can be achieved by means of the inlet bevels with the least possible constructional outlay.

According to claim 26, a supply device for electrical components, which are provided in component straps and transported to a pick-up position of a placement machine, claimed. This feeding device has a cutting device as described in the above claims. The resulting advantages are apparent from the comments on the above claims.

According to claim a placement machine for loading substrates with electrical components, which has a cutting device according to one of the above claims, claimed. For the resulting advantages, reference is also made to the embodiment of the above claims.

In the following the invention will be explained in more detail with reference to the attached figures.

Figur 1

eine schematische Darstellung eines Bestückautomaten,

Figur 2

ein schematischer Schnitt durch die Zuführeinrichtung sowie die angrenzende Schneidvorrichtung in Förderrichtung der Bauelementgurte,

Figur 3

ein schematischer Schnitt durch Schneidvorrichtung quer zur Förderrichtung der Bauelementgurte,

Figur 4

eine schematische Darstellung der Schneideinrichtung,

Figuren 5A, 5B

Ausgestaltungsformen des Drehantriebs,

Figur 6

eine schematische Darstellung einer Gurthalteeinrichtung mit umlaufendem Klemmriemen,

Figur 7

eine schematische Darstellung einer Gurthalteeinrichtung mit stehendem Klemmriemen,

Figur 8

eine schematische Darstellung einer Gurthalteeinrichtung mit stehendem Klemmriemen in Omega-Anordnung,

Figur 9

eine schematische Darstellung eines vorgespannten Federelements,

Figur 10

eine schematische Darstellung der Arbeitsposition und der Sicherungsposition der Schneideinrichtung.

In the figures are

FIG. 1

a schematic representation of a placement machine,

FIG. 2

a schematic section through the feeder and the adjacent cutting device in the conveying direction of the component straps,

FIG. 3

a schematic section through cutting device transverse to the conveying direction of the component straps,

FIG. 4

a schematic representation of the cutting device,

FIGS. 5A, 5B

Embodiments of the rotary drive,

FIG. 6

a schematic representation of a belt holding device with circumferential clamping belt,

FIG. 7

a schematic representation of a belt holding device with a stationary clamping belt,

FIG. 8

a schematic representation of a belt support device with upright clamping belt in omega arrangement,

FIG. 9

a schematic representation of a prestressed spring element,

FIG. 10

a schematic representation of the working position and the securing position of the cutting device.

FIG. 1 schematically shows a placement machine 1 for loading substrates 2 with components 3. The placement machine consists of a cross member 7, which extends in a y-direction and is fixedly connected to the machine frame. On the cross member 7, a portal arm 8 is mounted, which extends in the x direction and is slidably mounted in the y direction on the cross member 7. At the portal arm 8, the placement head 6 is slidably mounted in the x direction. Farther a transport path 4 is provided for transporting the substrates 2 to a placement position. In addition to the transport path 4 feeders 5 are arranged in the vicinity of the placement position, at the defined collection positions 10, the electrical components 3 are provided in component straps 11. Between the feeders 5 and the transport section 4, a cutting device 9 for shortening the empty component straps 11 is arranged.

To load the substrates 2, these are transported via the transport path 4 to their placement position. The electrical components 3 provided by the feed devices 5 are picked up by the placement head 6 and positioned on the substrate 2. The empty component straps 11 are led out of the feed devices 5 and fed to the cutting device 9.

In FIG. 2 is a section (AA in Fig. 1 ) by the feeder 5 and the adjacent cutting device 9 shown schematically. The feed device 5 consists of a transport wheel 16, which has transport pins in the radial direction on the circumference. About the transport wheel 16 of the component belt 11 is guided in the pocket-like recesses 17, the electrical components 3 are magazined. At the pickup position 10, the components can be removed with the aid of a pipette 15 of the placement head 6. Adjacent to the feeding device 5, the cutting device 9 is arranged. This consists of a housing 13 in which a Gurtkanal 14 is formed, and a cutting device 12 for shortening the component straps 11th

By rotation of the transport wheel 16, the feeding device 5 transports the components 3 lying in the pocket-like depressions 17 of the component belt 11 in a conveying direction F to the pick-up position 10. There, the components 3 are removed from a pipette 15 of the placement head 6. After removal of a component 3, the component belt 11 conveyed by a transport wheel 16 of the feeder 5 by a defined distance, so that the subsequent component 3 is located at the pick-up position 10 and can be picked up. The emptied component belt 11 is transported further in the conveying direction F and introduced into the belt channel 14. At the opposite opening of the belt channel 14, a cutting device 12 is mounted transversely to the conveying direction F movable. At regular time intervals, the cutting device 12 moves transversely to the conveying direction F and cuts through the component straps 11 protruding from the belt channel 14.

FIG. 3 shows a schematic section (BB in Fig. 1 On the housing 13 of the cutting device 9 14 linear guides 18 are mounted on both sides of the belt channel, by means of which the cutting device 12 can be moved both in a direction of displacement V and in a reverse direction G. ,

The component belts 11 projecting from the belt channel 14 formed in the housing 13 are cut through by the method of the cutting device 12. The cut-off component straps 11 are collected by a collecting container, not shown in the drawing.

In FIG. 4 the kinematics of the cutting device 12 is shown schematically. The cutting unit 12 consists essentially of the cutting unit 19 and the counter unit 23. The cutting unit 19 has a cutting element 20 with a circumferentially formed cutting edge 21 which is rotatably mounted on a shaft 22 and a mounted on the housing 13 of the cutting device 9 linear guide 18 transversely to the conveying direction F of the component straps 11 is displaceable. The counter unit 23 has a counter element 24 which is rotatably mounted on the counter shaft 26 and also via a mounted on the housing 13 linear guide 18 transversely to Conveying direction F is displaceable. Further shows FIG. 4 two more component straps 11, one of which is already cut off; the other is first cut through by the cutting device 12 and projects out of the belt channel 14.

With the help of a compression spring 27, the contact surface 25 of the counter element 24, which is formed in this illustration as a pressure roller 124, frictionally against the cutting edge 21 of the cutting element 20, which in FIG. 4 is shown as a roller blade 120, pressed. If the roller blade 120 rotates, then also the pressure roller 124 is automatically rotated in the opposite direction. Conversely, upon rotation of the pressure roller 124 and the roller blade 20 is set in an opposite rotation. If the cutting device 12 is moved in the direction of displacement V or in the opposite direction G, the roller blade 20 and the pressure roller 24 can be set in rotation via a rotary drive 28 (not shown).

The direction of rotation is selected such that the component straps 11 to be shortened are pulled into the engagement region of the cutting device 12. Ideally, the rotational speed is set in such a way that the rotational speed of the cutting edge 21 of the roller blade 120 at the point of contact with the pressure surface 125 of the pressure roller 124 is exactly the same as the linear velocity V of the cutting device 12. If the two velocity vectors are oppositely directed and of equal magnitude, ie "equal to one another", then the vector of the vector results in the zero vector. As a result, when a component belt 11 is cut between the cutting edge of the roller blade 120 and the component belt 11 to be severed, virtually no relative speed occurs. The component straps 11 are pressed in the crunching cut by the "relatively speed-free" unwinding of the cutting edge 21 of the roller blade 120 on the pressing surface 125 pressure roller 124. It occurs in the direction of travel V or in the opposite direction G of the cutting device no relative speed, ie no relative movement between the component belt 11 and the roller blade 120, on. The necessary for the squeezing surface pressure is applied by the compression spring 27.

For the operability of the cutting device 12, it is irrelevant whether the roller blade 120 or the pressure roller 124 is coupled to the rotary drive 28, since the not directly driven via the rotary drive element is non-positively driven by the bias of the compression spring 27 with.

In contrast to the cutting saw process, in which by moving the tool, the cutting teeth penetrate into the material to be cut, and by removing thin chips, a groove is incorporated into the body, which ultimately leads to separation, takes place during the crushing cut no material removal. The formation of dust particles, which lead to contamination of the machine and therefore must be removed again, is minimized. The maintenance effort can be reduced. Compared with the shear cutting, in which the material to be cut is initially plastically deformed by two cutting edges moving past each other and finally separated, jamming of the material to be cut between the cutting edges is excluded during squeezing despite the plastic deformation of the material.

FIG. 5a shows a possible embodiment of the rotary drive 28 for the cutting device 12 for the crushing cut by means of roller blade and pressure roller. The rotary drive 28 has a rack 30 which extends in the direction of displacement V and is mounted on the housing 13 of the cutting device 9, and a gear 29 which engages the rack 30 and is mounted on the shaft 22. Between the cutting unit 19 and the housing 13, a linear guide 18 is formed.

If the cutting device 12 is moved in the direction of displacement V or in the opposite direction G, then the gear 29 rolls over the rack 30 and offset via the shaft 22, the roller blade 120 in rotation. By applied via the bias by the compression spring 27 frictional connection with the pressure roller 124, these are also driven.

In order to realize the appropriate for the "relatively speed" unwinding rotational speed, the effective circle diameter of the gear 29 is to be selected so that it corresponds to the diameter of the roller blade 120. As a result, the translational movement of the cutting device 12 can be transferred in a simple manner into a rotational movement of the roller blade 120, so that at the contact point of the roller blade 120 with the pressure roller 124, the peripheral speed of the cutting edge 21 of the roller blade 120 exactly the same Linear velocity V of the cutting device 12 is.

FIG. 5b shows that already too FIG. 5a described embodiment of the rotary drive for the cutting device 12, but not for the squeezing cut, but for the punching cut, wherein the cutting element 20 as a punch wheel 220 and the counter element 24 are formed as a die wheel 224. For this purpose, the stamp wheel 220 has a disc-shaped basic body with two cutting edges 21 formed on the circumference. The die wheel also consists of a disk-shaped base body and further has a pronounced annular groove on the circumference. As in FIG. 5a illustrated, the rotary actuator 28 has a rack 30 which extends in the direction of displacement V and is mounted on the housing 13 of the cutting device 9, and a gear 29 which engages the rack 30 and is mounted on the shaft 22. As a result, when the cutting device 12 moves in the direction of displacement V or in the opposite direction G, the plunger wheel 220 is set in rotation. Stamp wheel 220 and Die wheel 224 are arranged in such a way to each other that the punch wheel 220 at least partially immersed in the annular groove of the die wheel 224. Also in this case, a quasi relatively speed-free "rolling" can be realized by appropriate dimensioning of the effective circle diameter of the gear 29.

In contrast to the crimping cut, the material to be cut is not compressed during punching cutting, but stretched over the two cutting edges 21 of the stamp wheel 220 in cooperation with the die wheel 224. It is irrelevant whether the die wheel is driven: a separate drive is of course possible, but not necessary.

In both cases, both for the crimping and the punching cut, it is also possible to use a correspondingly translated, mechanical transmission or an electric drive with a corresponding synchronization. In principle, it is also possible to synchronize the rotary drive 28 with the counter element 24 instead of with the cutting element 20.

Through these constructive configurations, a relatively speed-free cutting can be realized easily and inexpensively.

In FIG. 6 a strap holder 31 is shown schematically. As clamping elements, a first and a second circumferential clamping belt 36 and 37 are shown. The first circumferential clamping belt 36 sits on the cutting unit 19 and is moved with this. It is guided over the main body of the cutting element 20, if possible in the immediate vicinity of the cutting edge 21, and via two deflection devices, which are designed here as deflection rollers 38. The second clamping belt 37 is arranged on the counter unit 23 and movable with this. It is about the peripheral surface 25 of the counter element 24 and also about two pulleys 38th guided. Both the cutting unit 19 and the counter unit 23 are guided over mounted on the housing 13 of the cutting device 9 linear guides 18. In the engagement region between the cutting element 20 and the counter element 24, it must be ensured that the at least first clamping belt 36 can yield in the z-direction in order not to lift the cutting unit 19 away from the counter unit 23. This can be realized, for example, by the base body of the cutting element 20 having at least at the contact surfaces with the first clamping belt 36, a layer of hard foam or sponge rubber, which can give in accordance with thick component straps 11. Alternatively, the first clamping belt 36 instead of over the main body of the cutting element 20 via a separate from the cutting element 20, guided in the z-direction deflecting pulley 34 are guided.

By the coupling of the first clamping belt 36 with the main body of the cutting element 20, the first clamping belt 36 is also driven upon rotation of the cutting element 20. The cutting element 20 can be coupled to the rotary drive 28, so that it can be set in the displacement direction V in process of the cutting unit 19 in rotation. The belonging to the counter unit 23 and guided over the peripheral surface 25 of the counter unit 24 second clamping belt 37 has no own drive, but is driven by adhesion to the first clamping belt 36 with. However, it is also possible to provide the pressure roller 24 with its own rotary drive 28 ', which then - as well as the rotary drive 28 of the cutting element 20 - must be synchronized with the linear drive of the cutting device 12.

Between the mutually facing belt surfaces of the two clamping elements 36 and 37 to be shortened component straps 11 clamped and fixed relative to the housing 13 fixed. If the cutting device 12 moves to the left, then the two clamping belts 36 and 37 move relatively in the area of contact between the cutting element 20 and the counter element 24 to the cutting device 12 with appropriate translation at the same speed in the opposite direction to the right. Relative to the housing 13 of the cutting device 9, the two clamping belts 36 and 37 in the contact area therefore have zero speed. In this way, the component straps 11 protruding from the belt channel 14 can be fixed in a stationary manner relative to the housing 13. Pulling and tugging on the component straps, which can lead to positional inaccuracies at the removal position, is thereby avoided.

The geometric guidance of the clamping belt 36 and 37 is accomplished by the pulleys 38. The guide geometry of the clamping belts 36 and 37 is designed such that between the two clamping belts 36 and 37, a catch area is formed, which tapers on both sides to the effective range between the cutting element 20 and the counter element 24. In this case, the region of the cutting unit in which the at least one cutting edge of the cutting element cooperates with the counter element in such a way that the component belt is severed is defined as the effective region. As a result of the design of the catching area, the pocket-like recesses 17 of the component belts 11 standing out of the belt channel 14 are compressed by the two standing clamping belts 32 and 33 during the process of the cutting device 12, which facilitates the cutting process both during squeezing and during punching.

If a component 3 is not picked up by the placement head 6 at its pick-up position 10 and also remains in the pocket-like depression 17 when the component belt 11 is indexed further, this could lead to damage to the cutting element 20, in particular when attempting to sever the component belt 11 at this point at the cutting edge 21 of the roller blade 120 lead. Therefore, the fastening mechanism of the compression spring 27 is designed so that when a certain limit force in the z direction is exceeded, the cutting unit 19 is separated from the counter unit 23.

With the help of in FIG. 6 shown strap support means 31, the component straps 11 fixed relative to the housing 13 fixed fix the cutting device 12 perform and cut through safely. Due to the symmetrical design of the cutting device 12 and the belt support device 31, it is possible to cut through the component straps 11 both when moving the cutting device in the direction of displacement V, as well as in the opposite direction G. It is also possible to form only a clamping element of circumferential clamping belt and to use as a second clamping element, for example, a housing part of the cutting device 9. With regard to the advantages of the "relatively speed-free" separating the component straps 11 is to the comments too FIG. 5 directed.

FIG. 7 schematically shows a belt holding device with stationary clamping elements, which in turn are designed here as a clamping belt. Under a standing clamping element or a stationary clamping belt is understood a clamping element which is not movable with the cutting device, but is anchored stationary relative to the housing.

A first stationary clamping belt 32 is guided over a deflection pulley 34, which belongs to the cutting unit 19 and sits on the shaft 22 in the immediate vicinity of the cutting element 20, which is designed here as a roller blade 120. A second upright clamping belt 33 is guided over a deflection surface 35, which is formed on the cylindrical outer surface of the counter element 24, here the pressure roller 124 (see section DD). In contrast to the peripheral clamping belts 36 and 37, which are movable together with the cutting device 12, the standing clamping belts 32 and 33 are secured at their ends in the housing 13 of the cutting device 9.

To realize this arrangement, the radius of the deflection disc 34 is to be chosen so that it is slightly smaller, approximately to the thickness of the clamping belt 32, than the radius of the roller blade 20. To prevent lifting of the cutting unit 19 of the counter unit 23 and the Cutting device 12 to adapt to the different thickness component straps 11, the deflection plate 34 are either resiliently mounted in the z direction, or in the contact area with the clamping belt have a resilient, elastic layer of foam rubber or hard foam.

Since the clamping belt 32 is firmly anchored in the housing, when moving the cutting device 12 in the direction of displacement V or in the opposite direction G, the deflecting pulley 34 rotatably mounted on the shaft 22 rolls on the upright clamping belt 32. Also, the radius of the deflecting surface 35 formed on the pressure roller 124, over which the second stationary clamping belt is guided, is to be chosen so that it is slightly smaller, approximately to the thickness of the clamping belt 33, than the radius of the pressure roller 124 also formed Andrückfläche 125. Thus rolls when moving the cutter 12 in the direction of displacement V or in the opposite direction G, the deflection surface 35 of the pressure roller 124 on the stationary clamping belt 33 from. The Kinimatik shown by the non-positive connections between the first stationary clamping belt 32 and the deflection pulley 34 and the second stationary clamping belt 33 and the deflection surface 35 of the pressure roller 124 and the two clamping belts 32 and 33 with each other realized. However, it is useful to drive the shaft 22 or the counter shaft 26 by means of an additional rotary drive.

In the sectional view too FIG. 7 is a possible embodiment of such a rotary drive 28 to see: The gear 29 is fixedly connected to the shaft 22 and rolls when moving the cutting unit 19 on the housing 13 attached to the rack 30 from. The effective circle diameter of the gear 29 is to be chosen so that it corresponds to the diameter of the cutting edge 21 of the roller blade 120. Since the deflection pulley 34 and the roller blade 120 also sit firmly on the shaft 22, this positive connection leads to a precisely defined, slip-free rolling motion of the roller blade 20. It is also possible, alternatively or in addition to the shaft 22, to also provide the counter shaft 26 with a rotary drive synchronize.

By choosing the anchoring points of the clamping belt 32 and 33 in the housing 13 and the dimensioning of the roller blade 120 and the pressure roller 124, the geometric position of the stationary clamping belt 32 and 33 is fixed. In this case, a catching area is formed by the two standing clamping belts 32 and 33, which tapers on both sides towards the effective area, where the cutting edge 21 of the roller blade 120 presses into the component belt and cuts it, between the roller blade 120 and the pressure roller 124. The pocket-like depressions 17 of the component belt 11 protruding from the belt channel 14 are thereby compressed by the two clamping belts 36 and 37 during the movement of the cutting device 12. Furthermore, the compressed component straps 11 fixed relative to the housing 13 fixed to the effective range of the cutting device 12 between the roller blade 120 and the pressure roller 124, so that they are severed with a squeezing cut sure.

If a component 3 is not picked up by the placement head 6 at its pickup position 10 and also remains in the pocket-like depression 17 when the component belt 11 is indexed, this could lead to damage on the roller blade 120 when attempting to sever the component belt 11 at this point. Therefore, the fastening mechanism of the compression spring 27 is designed so that when a certain limit force in the z direction is exceeded, the cutting unit 19 is separated from the counter unit 23. Thus, those on the deflection plate 34, which is connected to the cutting unit 19 is, or the deflection surface 35 of the connected to the counter unit 23 connected to the pressure roller 124, stationary clamping belt 32 and 33 separated.

The quasi-symmetrical design of the cutting device 12 and the belt support device 31 ensures that the component straps 11 are reliably severed both in the process of the cutting device in the direction of displacement V and in the opposite direction G. However, it is also possible to form only one clamping element as a standing clamping belt and to use as a second clamping element, for example a housing part of the cutting device 9.

In principle, a belt holding device with upright clamping elements is also suitable for the cutting body pairing of the punch wheel 220 / die wheel 224, which, however, is not specifically shown.

In FIG. 8 is a Gurthalteeinrichtung 31 with a standing clamping belt in omega arrangement 40 shown schematically. The fixed in the housing 13 at its one end by means of a tension roller 39 clamping belt serves as a first clamping element and is guided over at least 5 pulleys 38, so that approximately the shape of the Greek letter Omega results. The guide rollers 38 are rotatably mounted on a carrier (in the sectional drawing of FIG. 8 not shown), which is movable with the cutting unit 19 of the cutting device 12. Together with the cutting unit 19 also moves the counter unit 23 on which the counter-element 24 is rotatably mounted. As a second clamping element, the wall of the housing 13 of the cutting device 9 acts.

If the cutting device 12 moves with the cutting element 20 and the counter element 24 in the direction of displacement V or in the opposite direction G via the belt channel 14, the standing clamping belt 40 is moved over the deflection rollers 38 by the cutting unit 19 pulled and pressed against the wall of the housing 13. The at least one cutting edge 21 of the cutting element 20 rolls in contact with the peripheral surface 25 of the counter element 24 on this.

Due to the geometry of the belt guide, a catching area is formed on both sides of this contact area by the wall of the housing 13 and the standing clamping belt 40. Unlike the in FIG. 7 As shown solution remains the geometry of the capture area over the travel distance of the cutting device 12 away unchanged, the opening angle does not change due to the omega-leadership of the belt.

As a result of this structural design of the belt holding device 31, the component straps 11 to be shortened are pressed against the wall of the housing 13 and fixed there until they are separated by a squeezing or punching cut between the cutting element 20 and the counter element 24. Disturbing effects on the pickup positions 10 of the electrical components 3 - such as vibrations and other movements of the component straps 11, which could lead to changes in position of the components 3 at the pickup positions 10 - can be avoided by fixing the component straps 11.

FIG. 9 shows a biased spring element 43, shown here as a spiral spring. The spring element 43 is attributable to the counter unit 23 and serves for the independent adaptation of the belt holding device 31 to the thickness of the compressed component straps 11. The peripheral surface 25 of the counter element 24 is displaceably mounted relative to the remaining counter unit 23 in the z direction, so that the distance of the pressing surface 25 of the pressure roller 24 to the deflection plate 34 can be varied to a small extent. This is necessary because the component straps 11 may have a different thickness depending on the size of the pocket-like depressions 17 in the compressed state.

By the spring element 43, which is fastened with its one end to the mounting of the counter element 24 and with the other end to the carrier of the counter unit 23, the two clamping belts 36 and 37, over the peripheral surface 25 of the counter element 24 and over the deflection 35 of the deflection plate 34 are guided, pressed against each other. In the case of thicker component straps 11, the spring element 43 is correspondingly more strongly compressed by the force exerted by the component straps 11 in the z direction on the clamping belt and thus also on the mounting of the counter element 24, as would be the case with a thin component belt 11.

By using this prestressed spring element and thicker component straps 11 can be securely clamped. Instead of coil springs and other structural configurations for the spring element, such as cup spring packages can be used.

In FIG. 10 the cutting device 12 is shown schematically in the two positions "working position" and "securing position". The cutting device 12 is arranged displaceably in the x-direction together with the belt holding device 31 via the belt channel 14 (not shown). In the working position, the cutting unit 19 cooperates with the counter unit 23, the at least one cutting edge 21 of the cutting element 20 is in contact with the counter element 24. The two clamping elements, shown here as circumferential clamping belts 36 and 37, are pressed against each other. In the securing position cutting unit 19 and counter unit 23 are separated from each other, wherein the clamping elements are separated from each other.

Such a separation may become necessary if an electrical component 3 is not picked up by the placement head 6 at its pick-up position 10 and remains in the pocket-like recess 17 when the component belt 11 is indexed further.

When attempting to sever the component strap 11 at this point, damage to the at least one cutting edge 21 of the cutting element 20 could occur. Threatens an electrical component 3 during the cutting process between the cutting element 20 and 24 counter element, so when trying to clamp the device 3 between the two clamping belts 36 and 37, a certain limit force in the z direction exceeded, whereby the cutting unit 19 of the counter unit 23 is disconnected.

Here, the pressing mechanism 42 is displaced for the counter-element 24 in the z-direction relative to the cutting device 12 from the working position to the securing position. The component 3 remaining in the component belt 11 is thus not damaged, the belt is not severed. The cutting device 12 remains for the remainder of the route over the belt channel 14 in the securing position; The component straps 11 to be passed are likewise not severed. It is also possible to couple the cutting element 20 instead of the counter element 24 with the pressing mechanism 42 and to move from the working position to the securing position.

In the direction of displacement V or in the opposite direction G 9 inlet slopes 44 are formed at both ends of the belt channel 14 on the housing 13 of the cutting device. If the counter unit 23 moves in the securing position over the belt channel 14, the inlet bevel 44 presses against the pressing mechanism 42 of the counter element 24 at the end of the belt channel 14 and pushes it back into the working position. Those component straps 11 which were not severed in this cutting process can be severed in the subsequent cutting process.

LIST OF REFERENCE NUMBERS

1

automatic placement

2

substratum

3

Electrical component

4

transport distance

5

feeding

6

placement

7

crossbeam

8th

port alarm

9

cutter

10

collection position

11

component tape

12

cutter

13

casing

14

belt channel

15

pipette

16

Transport wheel

17

Pocket-like depression

18

linear guide

19

cutting unit

20

cutting element

21

cutting edge

22

wave

23

counter unit

24

counter element

25

peripheral surface

26

counter shaft

27

compression spring

28

rotary drive

29

gear

30

rack

31

Gurthalteeinrichtung

32

First standing clamping belt

33

Second stationary clamping belt

34

deflection plate

35

deflection

36

First circulating clamping belt

37

Second circumferential clamping belt

38

Deflection device / deflection roller

39

idler

40

Standing clamping belt in omega arrangement

41

Pressure mechanism belt holding device

42

Pressure mechanism counter element

43

Prestressed spring element

44

Return device / inlet slope

120

roller blades

124

capstan

125

pressing surface

220

Stempelrad

224

die wheel

225

ring groove

Claims (27)

Cutting device (9) for shortening component straps (11) for a placement machine (1), comprising: a housing (13, a belt channel (14) formed in the housing (13) for passing the component belts (11) to be shortened in a conveying direction (F), a cutting device (12) which cuts through the component straps (11) guided in the belt channel (14) transversely to their conveying direction (F), - A belt holding device (31) for fixing the component straps (11), which comprises at least a first and a second clamping element (32, 36 and 33, 37) with mutually facing clamping surfaces for clamping the component straps (11), wherein the belt holding device (31) is configured such that the component straps (11) between the clamping elements (32, 36 and 33, 37) relative to the housing (13) are fixed in place. Cutting device (9) according to claim 1, wherein the cutting device (12) in a direction transverse to the conveying direction (F) directed displacement direction (V) movable on the housing (13) is provided such that the process in the cutting device (12) in the belt channel (14 ) guided component straps (11) transversely to its conveying direction (F) are severed. Cutting device (9) according to claim 2, wherein the cutting device (12) comprises a deflecting device (38) and the first clamping element (32 or 36) of the belt holding device (31) is designed as at least one clamping belt (32), which in the direction of displacement ( V) over the entire travel distance of the cutting device (12), is guided over the deflection device (38) and at its two ends in the housing (13) is firmly anchored, that together with the second clamping element (33 or 37) a catching area for the component straps (11) is formed , which tapers to an effective range of the cutting device (12). Cutting device (9) according to claim 3, wherein the deflection device (38) has a rotatably mounted deflection roller (38). Cutting device (9) according to one of claims 3 to 4, wherein the deflection device (38) is designed as an omega deflection. Cutting device (9) according to claim 2, wherein the cutting device (12) has a deflecting device (38) and the first clamping element (32 or 36) of the belt holding device (31) as at least one closed, circumferential clamping belt (36) is formed over the deflection device (38) guided, with the cutting device movable and arranged such that between the clamping belt (36) and the second clamping element (33 or 37) a catching area is formed, which tapers towards the effective range of the cutting device (12). Cutting device (9) according to claim 6, wherein the clamping belt (36) is coupled to a drive such that the belt speed in the effective range of the cutting device is equal to its travel speed. Cutting device (9) according to claim 7, wherein the clamping belt (36) is guided such that both in the process the cutting device (12) in the direction of displacement (V) and in the opposite direction (G), the component straps (11) fixed to the effective range of the cutting device (12) are supplied. Cutting device (9) according to one of claims 6 to 8, wherein the second clamping element (33 or 37) is formed as a closed, circumferential clamping belt (37). Cutting device (9) according to one of claims 3 to 8, wherein the second clamping element (33 or 37) is a housing part (13) of the cutting device (9). Cutting device (9) according to one of claims 3 to 10, wherein the clamping belts (32, 36, or 33, 37) are made of adhesive material. Cutting device (9) according to any one of claims 4, 5, 10 or 11, wherein the deflecting device (38) is formed transversely to the displacement direction (V) elastic, so that the distance from the first to the second clamping element to the thickness of the component straps (11) adaptable is. The cutting apparatus (9) according to any one of claims 1 to 12, wherein the cutter comprises: a cutting unit (19) having a rotatably mounted cutting element (20) with at least one peripheral cutting edge (21), a counter unit (23) having a counter element (24), wherein the cutting unit (19) and the counter unit (23) are arranged such that upon rotation of the cutting element (20) the at least one cutting edge of the cutting element (20) interacts with the counter element (24) in such a way that during cutting of the cutting device (12) the component belts (11) guided in the belt channel (14) are cut transversely to their conveying direction (F). Cutting device (9) according to claim 13, wherein the cutting element (20) as rotatably mounted roller blade (120) with a circumferentially formed cutting edge (21) and the counter element (24) as a rotatably mounted pressure roller (124) with a circumferentially formed pressing surface ( 125) are formed,
wherein the cutting unit (19) and the counter unit (23) are arranged such that upon rotation of the roller blade (120), the cutting edge (21) of the roller blade (120) rolls on the pressing surface (125) of the pressure roller (124). Cutting device (9) according to claim 14, wherein the cutting device (9) comprises a biasing device which presses the roller blade (20) and the pressure roller (24) in a working position against each other, so that the component belts (11) by a squeezing operation between roller blade (20 ) and pressure roller (24) are separated. Cutting device (9) according to claim 13, wherein the cutting element (20) as rotatably mounted punch wheel (220) with two circumferentially formed cutting edges (21) and the counter element (24) as rotatably mounted Matrizenrad (224) with a circumferentially formed annular groove ( 225) are formed, into which the stamp wheel (220) at least partially immersed. Cutting device (9) according to one of claims 13 to 16, wherein the cutting edge (21) of the cutting element (20) and the areas of the counter element (24) cooperating with the cutting element (20) can be made of hardened material. Cutting device (9) according to one of claims 13 to 17, wherein the cutting device (12) is designed such that the component straps (11) during displacement of the cutting device (12) both in the direction of displacement (V) and in a direction opposite to the direction of displacement ( G) are severed. Cutting device (9) according to claim 18, wherein the cutting device (12) is movable by means of a linear drive and has a rotary drive (28) for the cutting element (20) which is coupled to the linear drive in such a way that the peripheral speed of the at least one cutting edge ( 21) of the cutting element (20) at the point of contact with the counter element (24) is equal to the travel speed of the cutting device (12). The cutting apparatus (9) of claim 19, wherein the rotary drive (28) comprises: a rack (30) which is provided on the housing (13) and extends in the displacement direction (V), - A gear (29) which is in engagement with the rack (30), and - A shaft (22) through which the gear (30) with the cutting element (20) is connected such that in the process of the cutting device (12), the cutting element (20) is set in rotation. Cutting device (9) according to claim 18, wherein the cutting device (12) is movable by means of a linear drive and has a rotary drive (28) for the counter element (24) which is coupled to the linear drive such that the peripheral speed of the counter element (24). in the point of contact with the at least one cutting edge (21) of the cutting element (20) is equal to the speed of movement of the cutting device (12). The cutting apparatus of claim 21, wherein the rotary drive (28) comprises: a rack (30) which is provided on the housing (13) and extends in the displacement direction (V), - A gear (29) which is in engagement with the rack (30), and - A counter shaft (26) through which the gear (29) with the counter element (24) is connected such that in the process of the cutting device (12) the counter element (24) is set in rotation. Cutting device (9) according to one of claims 13 to 22, wherein the cutting device (12) is designed such that the cutting unit (19) and the counter unit (23) relative to each other between a working position of the cutting device (12) in which the cutting element ( 20) and the counter element (24) cooperate, and a securing position in which the cutting element (20) is separated from the counter element (24), are displaceable, and a securing mechanism is provided which is designed such that when exceeding a the cutting action occurring maximum force the cutting unit (19) is separated from the counter unit (23). Cutting device (9) according to claim 23, wherein at least one return device (44) is provided on the housing (13) which moves the cutting device (12) from the securing position to the working position. Cutting device according to claim 24, wherein the return device (44) is configured as an inlet slope (44). Feed device (5) for electrical components (3), which are provided in component belts (11) and transported to a pick-up position (10) of a placement machine (1), wherein the feed device (5) via a cutting device (9) according to one of the above claims 1 to 25 has. Placement machine (1) for equipping substrates (2) with electrical components (3), which has a cutting device (9) according to one of the above claims 1 to 25.

Images