Patent Application
20240042563
The present invention relates generally to a loading system for an optical machine according to the preamble portion of claim 1. In particular, the invention relates to a loading system for loading and unloading optical workpieces, such as spectacle lenses, such as are widely employed in modern “RX workshops”, i.e. industrial production facilities for production of individual spectacle lenses according to prescription. If in the following there is also discussion of, in particular, loading or unloading workpieces, then the loading system is also equally suitable for change of, for example, tools, which accordingly is to be regarded as included.
The invention further relates to a device for deblocking optical workpieces, particularly spectacle lenses, from associated block pieces, which comprises such a loading system in order to handle blocked workpieces prior to the deblocking and block pieces and deblocked workpieces after the deblocking.
In optical production, “blocking-on” or, for short, “blocking” generally denotes the procedure in which an optical workpiece is temporarily fastened with the aid of a suitable material (alloyed material of low melting point—so-called “alloy”—or adhesive) on a so-called “block piece” or, however, the blocking material is coated on the workpiece so as to itself form the block piece, which then serves the purpose of holding the workpiece in the respective processing machine and/or coating system. Accordingly, in optical production that process in which the optical workpiece after (final) processing thereof (at surface and/or edge) and/or coating thereof is again separated from the block piece/blocking material is called “deblocking”.
Spectacle lenses are blocked on a large scale in the afore-mentioned RX workshops before each blocked spectacle lens is then processed by material removal with geometrically defined cutting (milling/turning) or geometrically undefined cutting (grinding/polishing) at its back surface or front surface with respect to its optical effect and/or at the edge for fitting in an associated spectacle frame and/or is coated on its back surface or front surface for achieving additional effects (increase in scratch resistance, anti-reflection properties, vapor deposition, hydrophobic properties, etc.).
When in the following in connection with the present invention mention is made in general of “spectacle lenses” as preferred field of use there are to be understood by that optical lenses or lens preforms (blanks) for spectacles of customary materials such as polycarbonate, mineral glass, CR 39, HI-index, etc., which may have any desired (preliminary) shape of the circumferential edge of the lens or lens blank and which prior to blocking may—but do not have to—have already undergone (preliminary) processing and/or (preliminary) coating at one optically effective surface or both optically effective surfaces and/or at the edge. In addition, the spectacle lens can be provided on its surface, at which it is or is to be blocked, with a film, a lacquer or the like so as to protect this surface from contamination and damage and/or to improve the adhesion characteristics between spectacle lens and blocking material, without this being specifically mentioned on each occasion in the following.
There is no lack of proposals in the prior art as to how in industrial production of spectacle lenses the workpieces can be automatically loaded into an optical machine for processing or further treatment and removed again from the optical machine after the processing or further treatment. Thus, document DE 10 2014 015 053 A1 (
As loading system, the prior art polishing machine further comprises a gantry handling system by which the spectacle lenses can be automatically transported between the afore-mentioned stations and polishing cells and positioned in the respective station or polishing cell. For that purpose the gantry handling system has a three-dimensionally movable sucker unit for holding a spectacle lens, which is to be polished, at the optically effective surface to be polished as well as a three-dimensionally movable multi-finger gripper for holding a polished spectacle lens at the edge thereof. The discussed possibilities of three-dimensional movement comprise horizontal (x, y) and vertical (z) linear movements as well as a tilting movement (b) about a transverse axis parallel to a horizontal movement direction (y).
More precisely, the gantry handling system has two x linear units with drive arrangement for producing the x movement, which are arranged at the polishing machine at the top on either side of the machine frame. The x carriages of the x linear units each carry a pivot mount, which with the assistance of a pneumatic cylinder enables tilting of a y linear unit, which is mounted on the pivot mounts and forms the “gantry”, with drive arrangement for producing the y movement through a predetermined angle. By virtue of this measure a z linear unit mounted on a y carriage of the y linear unit can be tilted out of the vertical so as to be adapted to a workpiece spindle inclined setting which arises in the state of the polishing cells being mounted in the machine frame. Finally, the sucker unit and the multi-finger gripper are mounted on the z linear unit to be longitudinally displaceable and, in particular, in such a way that they can be moved in opposite sense by a common drive, i.e. if the sucker unit is moved downwardly the multi-finger gripper moves upwardly at the same time, and conversely.
A spectacle lens to be polished can thus be lifted (z) by the sucker unit of the gantry handling system out of a job tray on the transfer station by movement of the z linear unit, then moved three-dimensionally (b, x, y) and adjusted (z) to an inclined workpiece spindle of the desired polishing cell for processing by polishing. After the processing by polishing, the spectacle lens polished to finished state can be lifted (z) by the multi-finger gripper out of the respective polishing cell, transported (b, x, y) to the washing station and inserted (z) into this so as to remove polishing medium residues by washing. The clean spectacle lens can subsequently be lifted (z) by the multi-finger gripper out of the washing station, moved (x, y) to the respective job tray on the transfer station and deposited (z) therein. The spectacle lenses can accordingly be transported back and forth by the gantry handling system as desired or necessary between the polishing cells and stations.
Document DE 10 2017 001 679 A1, which forms the preamble portion of claim 1, discloses a similar loading system for the case of a deblocking device. The loading system, which in the terminology of this specification is termed “manipulation device” and which is attached to a frame of the deblocking device above a work space, comprises three grippers which can be telescoped independently of one another in vertical direction (z). The grippers serve the purpose of gripping, picking up, conveying and depositing the blocked lens, thus the lens together with the associated block piece, the deblocked lens and the deblocking block piece independently of one another and, in particular, at or between transport carriers on a conveying device and holding devices, which are spaced therefrom, for lens and block piece at a work space in which the deblocking takes place.
In that case the grippers together with their associated setting devices (pneumatic cylinder for the Z direction) are mounted on a carrier which can be moved in a horizontal plane (X-Y plane). For that purpose the carrier is mounted on a first linear guide (Y direction), which in turn is mounted together with its drive on a second linear guide (X direction) mounted on the frame. The supply of energy to the setting devices and linear guides takes place by way of cable trailing systems. However, this and the weight of the linear guides arranged one on the other together with associated drives limit the dynamics of this prior art loading system.
The invention has the object of creating a loading system for an optical machine, particularly for loading and unloading optical workpieces, such as spectacle lenses, and/or block pieces for blocking optical workpieces and/or tools, which is constructed as simply and compactly as possible and enables loading and unloading with highest possible dynamics. The object of the invention also comprises provision of a device for deblocking optical workpieces, particularly spectacle lenses, from associated block pieces, which for the purpose of achieving a highest possible throughput in an industrial production environment comprises such a loading system.
This object is fulfilled by a loading system for an optical machine with the features of claim 1 or by a device for deblocking optical workpieces, namely spectacle lenses, from associated block pieces, with the features of claim 18. Advantageous embodiments of the invention are the subject of the subclaims.
According to the invention, in a loading system for an optical machine, particularly for loading and unloading optical workpieces, such as spectacle lenses, and/or block pieces for the blocking of optical workpieces and/or tools, comprising a carrier which is movable in a movement plane by way of two linear guide units and which carries at least one holder for the optical workpiece and/or the block piece and/or the tool, the carrier being movable in a transverse direction with respect to the movement plane, the linear guide units are constructed and arranged in the form of an H gantry or a cross gantry, with two stationary drive motors for drive in the same or opposite sense of a traction element which is movably arranged in an H shape or a cross shape at the linear guide units and is secured to the carrier.
According to the invention, in the case of a device for deblocking optical workpieces, particularly spectacle lenses, from associated block pieces, comprising a transfer station for the deposit of optical workpieces, which are blocked on block pieces, and/or deblocked optical workpieces and/or block pieces, and a loading station for loading optical workpieces, which are blocked on block pieces, prior to the deblocking and/or unloading deblocked optical workpieces and/or block pieces after the deblocking, there is provided the above loading system by which the optical workpieces blocked on block pieces and/or the deblocked optical workpieces and/or the block pieces are transportable between the transfer station and the loading station and can be placed in or removed from the respective station.
Due to the fact that, in accordance with the invention, the two drive motors for drive of the traction element in the same sense or opposite sense are arranged in stationary location, i.e. in distinction from the drive motors in the afore-described prior art are not moved together with the movable carrier or a linear guide unit and also do not have to be supplied by way of associated cable trailing systems, according to the present invention in conjunction with a comparatively low outlay on a device technology and an advantageously flat system mode of construction there is only a small moved intrinsic mass of the loading system. This makes possible high accelerations of the movable carrier in the two axial directions of the movement plane, so that the parts (optical workpieces, block pieces or tools) held at the transversely movable holder of the carrier can be moved with a very high dynamic.
In that regard, the linear guide units of the loading system according to the invention are constructed and arranged in the form of an H gantry—as will be described in more detail in the following—or, however, in the form of an X gantry or a cross gantry. Since merely the H gantry will be explained in more detail later with respect to the embodiment, the cross gantry shall be briefly described at this point: In the case of a cross gantry the linear guide units comprise two cross members, namely a stationary first cross member, which, for example, is mounted on a machine frame of the optical machine and on which a carriage is guided to be movable in, for example, a y direction, and a movable second cross member, which crosses—giving the name—the first cross member and which is arranged on the afore-mentioned carriage to be movable in a transverse direction, that is to say, for example, an x direction. The carrier, on which the holder is mounted to be movable in a further transverse direction, i.e. here a z direction, is then mounted on the second cross member at the end. As seen in plan view, i.e. towards the z direction, the result is thus a cross with a horizontal orientation of the stationary first cross member (y direction to the right) and vertical orientation of the longitudinally displaceable second cross member (x direction downwardly).
Provided for movement of the carrier in the movement plane x-y of the cross gantry is the traction element, which is movably arranged in cross shape at the linear guide units and secured to the carrier. More precisely, the traction element is guided over four 90° deflection rollers at the carriage, two 180° deflection rollers at the ends of the stationary first cross member and a 180° deflection roller at the free end, which is remote from the carrier, of the movable second cross member. The drive of the traction element can take place by way of the two 180° deflection rollers at the ends of the stationary first cross member, which are each drivingly connected with a respective one of the two stationary drive motors.
As seen in the afore-described plan view the following movements of the carrier in the movement plane x-y of the cross gantry can be generated: If the two 180° deflection rollers are driven at the same speed and with a positive direction of rotation (i.e. in clockwise sense), then the carrier mounted at the end of the second cross member moves in negative y direction. If the drive of the two 180° deflection rollers takes place at the same speed and in negative direction of rotation (i.e. in anticlockwise sense), then the carrier moves in positive y direction. A movement of the carrier in positive x direction arises when the 180° deflection roller, which is on the right as seen in plan view, is driven in positive direction of rotation and the 180° deflection roller, which is on the left as seen in plan view, is driven in negative direction of rotation at the same speed. In the case of reversal of direction of rotation of the two 180° deflection rollers, the carrier is moved in negative x direction.
If only the 180° deflection roller on the left as seen in plan view is driven in positive direction of rotation, whilst the 180° deflection roller on the right is stationary, then the carriage moves on the stationary first cross member in negative y direction, whilst the movable second cross member is displaced in negative x direction, so that the carrier moves diagonally in negative y direction and negative x direction. This can reverse through a reversal of rotational direction at the 180° deflection roller on the left, so that the carrier moves diagonally in positive y direction and positive x direction. Analogously thereto, when the 180° deflection roller on the left is stationary a diagonal movement of the carrier in negative y direction and positive x direction or in positive y direction and negative x direction can be produced by the 180° deflection roller on the right being driven in clockwise sense or in anticlockwise sense. Moreover, any desired path in the movement plane x-y of the cross gantry can be travelled by the carrier through suitable superimposition of the drive motions.
It will be apparent to the expert that in this way the carrier can move to any desired position in the movement plane x-y through suitable activation of the stationary drive motors. This applies equally to the cross arrangement and the H arrangement of the linear guide units, wherein, however, the H arrangement by comparison with the cross arrangement promises a higher degree of stiffness with less need for installation space and to that extent can be regarded as a preferred arrangement.
By comparison with the prior art outlined in the introduction, the loading system in an embodiment according to the invention makes possible, particularly in a case of use at a device for deblocking optical workpieces, namely spectacle lenses, from associated block pieces a substantial increase in throughput of optical workpieces as a consequence of its high dynamic. This high level of throughput performance makes the loading system according to the invention suitable for use in an industrial production environment in which a very high number of optical workpieces for treatment or processing arises.
In a preferred embodiment of the loading system one linear guide unit comprises two stationary x guide elements which extend parallel to one another and at each of which a respective x half-carriage is guided to be longitudinally displaceable, whilst the other linear guide unit comprises two y guide elements which extend parallel to one another and transversely to the x guide elements and rigidly connect the x half-carriages together and at which the carrier as y carriage is guided to be longitudinally displaceable. In principle, it is in fact also conceivable to provide other guide element arrangements, for example a stationary x guide element with a y guide element, which is displaceable thereon by way of an x carriage, for the carrier as y carriage in a T arrangement as a special case of the above-described cross gantry, as also a stationary x guide element on which two y guide elements for the carrier as y carriage are movably arranged by way of an x carriage, or two stationary x guide elements on which a y guide element for the carrier as y carriage is displaceably arranged in H shape by way of two x half-carriages, wherein the directions x and y can also be interchanged. However, these alternative guide element arrangements with individual guide elements in one direction (x and/or y) would have to be of appropriately solid construction in order to be able to accept torsional moments. By contrast, the first-mentioned embodiment of the loading system, in which two y guide elements are a component of a divided x carriage, is preferred particularly with respect to a high level of stiffness with a compact form of construction.
In the case of such linear guide units constructed and arranged in the manner of an H gantry, provision can be made in an expedient embodiment of the loading system that two 180° deflections for the traction element are associated with each of the stationary x guide elements and arranged at the end, whereas each of the x half-carriages carries two 90° deflections for the traction element, wherein one of the 180° deflections is drivable at one x guide element by one of the stationary drive motors and independently thereof the other one of the 180° deflections is drivable at the other x guide element by the other one of the stationary drive motors. In that regard, the stationary drive motors can be arranged at the x guide elements in a particularly service-friendly manner on the same side of the x guide elements or at opposite ends of the x guide elements, i.e. diagonally offset.
It is further preferred particularly with respect to reliable and low-wear functioning of the loading system if one of the 180° deflections for the traction element is provided with a tensioning device for the traction element. In principle, tensioning of the traction element can indeed also take place at the carrier or one of the 90° deflections, but such an embodiment is less preferred insofar as the tensioning device would then increase the moved mass of the loading system. By comparison with an equally conceivable, stationary tensioning roller or the like for the traction element the tensioning device at one of the 180° deflections additionally offers the advantage that even with a small setting travel of the tensioning device a large tensioning effect can be achieved, because there is tensioning at two runs of the traction element at the same time in the same direction.
Fundamentally, for example, linear guides with a guide profile and guide carriages engaging therewith can be used for guidance of the x carriage or y carriage of the loading system. However, on the other hand it is preferred if the x guide elements and/or the y guide elements are guide rods which as a consequence of the possible guidance at the circumference or wrapping ensure particularly rigid guidance even in the case of rapid movements. In particular, the x guide elements and/or the y guide elements can be guide rods with a round cross-section, which by comparison with other equally possible cross-sectional shapes offers special advantages with respect to possibilities of cleaning and smooth running as well as promises high load ratings. In that regard, it can also be provided that, in particular, the y guide elements are constructed as hollow bodies. By comparison with an equally conceivable solid configuration of the y guide elements, above all weight advantages—which in turn also favor a high dynamic—are offered by y guide elements formed as hollow bodies. Finally, a further advantage of the rod guides preferred here is that the x carriage can be constructed as a light self-supporting unit from the two x half-carriages and the rod-shaped y guide elements without further load-bearing components being needed.
In a further preferred embodiment of the loading system each of the x half-carriages is provided with two axially mutually spaced-apart linear bearing elements which co-operate with the respective guide rod associated as x guide element. This is primarily of advantage with respect to the stability of the arrangement by comparison with an also possible construction with a respective longer linear bearing element per x half-carriage. Equally, the carrier constructed as y carriage can preferably comprise three mutually spaced-apart linear bearing elements, of which two linear bearing elements co-operate with one y guide element constructed as a guide rod, whilst the other linear bearing element co-operates with the other y guide element constructed as a guide rod. Conceivable as a possible alternative to this statically defined bearing arrangement would be a bearing arrangement with two linear bearing elements associated individually or four linear bearing elements associated in pairs with the two y guide elements at the carrier, which, however, would be less stiff or heavier than the above preferred embodiment.
In the case of the above statically defined bearing arrangement at the y carriage it is additionally of advantage if in a preferred embodiment of the loading system the traction element is fastened near the two linear bearing elements, which both co-operate with the one y guide element constructed as a guide rod, to a fastening point provided at the carrier. Thus, tilting moments, which may detract from smooth running of the bearing arrangement, at the carrier are avoided in simple manner. The individual linear bearing element remote from the fastening point for the traction element in that regard bears merely a part of the weight of the carrier on the associated y guide element and supports the carrier against twisting with respect to the other y guide element.
In principle, all linearly guiding easy-motion bearings are conceivable as linear bearing elements, for example linear slide bearings or linear ball bearings with a ball cage. However, with respect to good serviceability and low costs it is preferred if the linear bearing elements are ball bushings. Strippers can be respectively associated therewith at both longitudinal sides for smooth running which is as permanent as possible.
Various alternatives are also conceivable for the traction element, thus, for example, a cable with loopings at the drive for transmission of the drive moment or a chain, such as link chain or a ball chain. However, with respect to a satisfactory capability of force transmission, ease of maintenance and a high degree of longitudinal stability it is preferred if the traction element is a belt, namely a cogged belt. In the case of a cogged belt, which has no slip and a fixed pitch, measuring systems for the travel paths of the carrier or the holder or holders may even be superfluous for positioning tasks of the loading system.
Moreover, the at least one or each holder is preferably movable by an associated pneumatic cylinder in the transverse direction with respect to the movement plane. Other actuators for producing a linear movement are also conceivable as an alternative thereto, for example an electric drive or a hydraulic cylinder, which, however, is less preferred particularly from the aspect of lowest possible costs.
Furthermore, in a preferred embodiment of the loading system it can be provided that the at least one or each holder is pivotable by an associated pneumatic pivot mechanism from a position aligned with the transverse direction to a position oriented substantially perpendicularly to the transverse direction, and conversely. Here, as well, it is possible to use—instead of pneumatic generation of movement—other principles of generation, for example electric or hydraulic, although less preferred, especially since compressed air is usually present in any case at an optical machine. The thus-given possibility of pivotation of the holder or holders advantageously increases the flexibility of the loading system, because the holder or holders can be three-dimensionally moved not only in the sense of a simple “pick & place” system, but also tilted for different insertion or removal tasks at the optical machine, for example from a vertical orientation to a horizontal orientation or conversely.
The at least one or each holder is preferably a pneumatically actuable multi-finger gripper, which advantageously is capable of gripping optical workpieces with any circumferential contour without coming into contact with the usually sensitive front surface or back surface of the workpiece at the time of gripping or during holding, in distinction from, for example, a vacuum suction head or cup equally conceivable as a holder. The above statements correspondingly apply here with respect to alternative principles of generation of movement for the gripper fingers (for example, electric or hydraulic).
In further pursuance of the concept of the invention the arrangement can be such that a valve terminal for activation of the pneumatic cylinder or the pneumatic cylinders and/or of the pneumatic pivot mechanism or the pneumatic mechanisms and/or the pneumatically actuable multi-finger gripper or the pneumatic actuable multi-finger grippers is arranged on the carrier constructed as y carriage. It is thus merely necessary to lead a common supply line to the valve terminal, which is moved together with the carrier and from where further pneumatic subdivision takes place. A more substantial trailing system, which may hinder or even prevent highly dynamic movements of the carrier, for the supply is thus advantageously avoided.
In a preferred embodiment of the loading system it is provided, particularly with respect to a largest possible stiffness and stability with low weight, that the carrier as seen in plan view is of substantially O-shaped construction with a central opening in which the at least one holder is mounted to be movable in the transverse direction with respect to the movement plane.
In a possible use of the loading system according to the invention in a deblocking device for deblocking optical workpieces, namely spectacle lenses, from associated block pieces it is particularly advantageous if the carrier of the loading system carries three holders which are movable in the transverse direction with respect to the movement plane and of which a first holder is assigned to the optical workpieces blocked on block pieces, a second holder is assigned to the deblocked optical workpieces and a third holder is assigned to the block pieces. A parallelization, to the greatest possible extent, of the loading and unloading processes during deblocking is thus possible, in which, in particular, the carrier of the loading system has to be moved only a small amount at the respective station (transfer station or loading station) of the deblocking device, which is conducive to a high dynamic and a large throughput of optical workpieces.
In that case, the transfer station of the deblocking device preferably has a conveyor belt for transport of job trays in a transport direction, wherein the job trays serve for reception of optical workpieces blocked on block pieces and/or deblocked optical workpieces and/or block pieces. However, it is also possible to operate without job trays and conveyor belt, for example with different workpiece carriers or block piece carriers for carrying individual optical workpieces in the blocked or deblocked state and/or different conveying device such as, for example, a chain or carousel conveying device or with a mere deposit possibility for the optical workpieces and/or the block pieces.
Finally, in the case of an embodiment of the deblocking device with conveyor belt and job trays it can be provided that the second holder for the deblocked optical workpieces as seen transversely to the transport direction of the conveyor belt lies adjacent to the third holder for the block pieces. This is also advantageously helpful with respect to parallelization of the loading and unloading processes—particularly without the necessity of conveyor belt movement—and thus with respect to a large throughput of optical workpieces.
The invention is explained in more detail in the following on the basis of a preferred embodiment with reference to the accompanying partly simplified or schematic drawings, which are not to scale and in which:
With respect to the drawings it may also be noted at this point that the illustration of the deblocking device with the loading system according to the invention is in a right-angled Cartesian co-ordinate system in which the letter x denotes the length direction, the letter y denotes the width direction and the letter z denotes the height direction of the deblocking device or loading system. In order to reveal a view of essential components or subassemblies of the deblocking device and the loading system and for simplification of the illustration, parts of the cladding, the supply devices (inclusive of lines, hoses and pipes) for power, compressed air and water as pressure medium, the suction device as well as the measuring, maintenance and safety devices, in particular, have mostly been omitted in the drawings, since they do not appear necessary for an understanding of the invention and are in any case familiar to the expert.
A deblocking device, for example for an optical machine for treatment and/or processing optical workpieces, for the deblocking of optical workpieces, such as spectacle lenses L, from associated block pieces B is generally denoted by the reference AV in
The basic construction of the deblocking device AV and, in particular, of the workpiece holding arrangement WH is the subject of parallel German Patent Application DE 10 2019 006 504.2 (called parallel application in the following), i.e. filed with the same application date, under the title “Optical machine for treatment and/or processing optical workpieces, such as spectacle lenses, as well as deblocking device and deblocking method therefor”, to which at this point for avoidance of repetition express reference may be made with respect to the more precise structure and function of the deblocking device AV in general and the workpiece holding arrangement WH specifically.
As can be best recognized in
The deblocking station DS comprises—as shown in the afore-mentioned German parallel application, but not here—as a first treatment device a first nozzle subassembly with a first high-pressure nozzle for delivery of a high-pressure pressure medium jet for deblocking the spectacle lenses L from the respectively associated block piece B. The cleaning station CS comprises—again not illustrated here, but shown in the afore-mentioned German parallel application—as a second treatment device a second nozzle subassembly with a second high-pressure nozzle for delivery of a high-pressure pressure medium jet for cleaning the deblocked spectacle lenses L and, as a third treatment device, a third nozzle subassembly with a third high-pressure nozzle for delivery of a high-pressure medium jet for cleaning the block pieces B.
The hydraulic supply of the afore-mentioned nozzle subassemblies is carried out by way of a hydraulic arrangement HA, which according to
This hydraulic arrangement HA is the subject of parallel German Patent Application DE 10 2019 006 505.0, i.e. filed on the same application date, under the title “Hydraulic arrangement for a device for deblocking optical workpieces, particularly spectacle lenses, from associated block pieces”, to which, for the avoidance of repetition, express reference may be made at this point with respect to the more precise construction and function of the hydraulic arrangement HA.
Arranged at approximately the same height as the workpiece holding arrangement WH and on the right in
Mounted above the workpiece holding arrangement WH and the transfer station TS at the machine frame MG is a loading system LS, which is described in more detail in the following and by which the spectacle lenses L blocked on block pieces B, deblocked spectacle lenses L and deblocked block pieces B can be transported between the transfer station TS and the loading station PS, which is provided at the workpiece holding arrangement WH, with its sub-stations PS1, PS2 and placed in and removed from the respective station TS, PS1, PS2.
As
A feature of this loading system LS is that—as explained in more detail in the following—the linear guide units LF1, LF2 are constructed and arranged in the form of an H gantry, with two stationary drive motors AM1, AM2 for drive—in the same sense or in opposite sense—of a traction element ZG which is movably arranged in an H shape at the linear guide units LF1 and LF2 and is attached to the carrier TR.
In addition,
Before the loading system LS is described in detail, the machine concept of the deblocking device AV with the afore-mentioned workpiece holding arrangement WH shall firstly be briefly explained. A feature of the workpiece holding arrangement WH is that the workpiece holding arrangement WH comprises a plurality of partition walls TW (marked in, for example,
The work spaces AR1, AR2, AR3 and AR4 can be moved in common together with the workpiece holding arrangement WH with respect to the machine frame MG so that each work space AR1, AR2, AR3 and AR4 can be selectably moved from the loading station PS, which is stationary at the machine frame MG, to the treatment or processing station DS, CS physically spaced from the loading station, and conversely. More precisely, each work space AR1, AR2, AR3 and AR4 can be displaced together with the workpiece holding arrangement WH in a movement cycle (indicated by a central round arrow in
For that purpose, the work spaces AR1, AR2, AR3 and AR4 of the workpiece holding arrangement WH together with their workpiece holders CH are arranged to be rotatable about a common axis RA of rotation (see, in that regard,
Whereas a first end wall SW1 of the workpiece holding arrangement WH of drum-like construction carries the workpiece holders CH, as can be readily seen in, for example,
Further details of the loading system LS can now be inferred from, in particular,
A respective x half-carriage HS1, HS2 is guided at each of the x guide elements XF1, XF2 to be longitudinally displaceable. For that purpose each x half-carriage HS1, HS2 is provided—as illustrated in the section according to
By contrast, the other linear guide unit LF2 for the y direction comprises, according to, in particular,
As can be best seen in the section according to
The afore-mentioned carrier TR as y carriage is guided at the y guide elements YF1, YF2 to be longitudinally displaceable. For that purpose, the carrier TR according to
Not only the respective two linear bearing elements LL at the x half-carriages HS1, HS2, but also the three linear bearing elements LL at the carrier TR constructed as y carriage are ball bushings. In that case, a stripper AS is associated with each of the linear bearing elements LL at the two longitudinal sides, as schematically illustrated in
In this connection it is to be mentioned that the loading system LS in the case of use, which is described here, in or at the deblocking device AV is exposed to special use conditions. Due to the deblocking and cleaning processes with high pressure (water as medium with a temperature of up to 50° Celsius) an extremely high level of humidity arises in the deblocking device AV. This humidity precipitates on all components. The afore-described embodiment of the guide system comprising round rods and ball bushings with strippers has proved advantageous here inasmuch as the loading system LS is capable of permanently withstanding not only the mechanical and dynamic loads, but also these environmental conditions.
By virtue of the afore-described arrangement of the linear guide units LF1, LF2 the result is substantially an H shape as can be readily recognized in
In the illustrated embodiment the traction element ZG is a cogged belt. At least the deflections UL1 and UL2 provided for this purpose at the stationary drive motors AM1, AM2 and driven by these are formed by correspondingly toothed belt pulleys. A precise control of the movement of the carrier TR is possible through the thus-produced mechanically positive and therefore slip-free movement transmission.
In this connection, it is additionally to be inferred particularly from
Moreover, it is additionally indicated in
As seen in the plan view according to
A movement of the carrier TR in positive x direction, i.e. downwardly in
If only the 180° deflection UL1 on the left as seen in the plan view is driven in positive direction of rotation, whilst the 180° deflection UL2 on the right is stationary, then the carrier TR moves on the Y guide elements YF1, YF2 in positive y direction, whilst the x carriage XS is displaced on the stationary x guide elements XF1, XF2 in positive x direction, so that the carrier TR in sum moves in the movement plane x-y diagonally in positive y direction and positive x direction, i.e. downwardly to the right in
In analogous manner, when the lefthand 180° deflection UL1 is stationary a diagonal movement of the carrier TR in positive y direction and negative x direction (i.e. upwardly to the right in
Further details with respect to the movement possibilities of the holders H1, H2, H3 relative to the carrier TR can be inferred from
A valve terminal, which is denoted generally by the reference VI and which is arranged on the carrier TR constructed as y carriage, i.e. laterally flange-mounted thereon (see
As
Moreover, a connecting section between the two limbs of the H-shaped guide block FG1 according to
From below, the respective pneumatic pivot mechanism SK1, SK2, SK3 is flange-mounted on each flange plate FG4, as
In the case of loading of one of the two effective surfaces of the pivot piston SK5 with pressure this can be moved from a first end position to a second end position and conversely, wherein the gearwheel SK7 is driven so that the holder H3, which is connected by way of the shaft SK8 and the clamp SK9, is pivoted from a horizontal position, as shown in
The construction and function of the pneumatically actuable multi-finger grippers provided in the illustrated embodiment as holders H1, H2, H3 are known per se, so that no further explanations with respect thereto are necessary at this point. These multi-finger grippers can be controlled so that they selectably grip or release a spectacle lens L or block piece B at the edge.
With regard to the three-dimensional arrangement of the holders H1, H2, H3 at the carrier TR it is additionally to be mentioned that the arrangement is such that in the state of the loading system LS being mounted on the machine frame MG the second holder H2 for the deblocked spectacle lenses L lies adjacent to the third holder H3 for the block pieces B as seen transversely to the transport direction R of the conveyor belt FB, as
Finally, with regard to handling of the deblocked spectacle lenses L in the workpiece holding arrangement WH of the deblocking device AV it remains to be mentioned at this point that according to, in particular,
A fully automatic loading cycle and unloading cycle, which are possible with the afore-described loading system LS, of the deblocking device AV shall be described in a time sequence thereof in the following with respect to the more schematic
By virtue of the high dynamic of the afore-described loading system LS it is possible to master even a comparatively high throughput of spectacle lenses L, which are deblocked in the deblocking device AV, of, for example, 250 spectacle lenses L per hour in terms of loading (loading and unloading) and this with a nevertheless very simple device, a greater degree of overview, good service-friendliness and high production serviceability.
A loading system for an optical machine, particularly for loading and unloading optical workpieces, such as spectacle lenses, and/or block pieces for blocking workpieces and/or tools, comprises a carrier which is movable in a movement plane by way of two linear guide units. At least one holder, which is movable in a transverse direction with respect to the movement plane, for the workpiece, block piece and/or tool is mounted on the carrier. The linear guide units are constructed and arranged in the manner of an H gantry or a cross gantry, with two stationary drive motors for drive in the same sense or opposite sense of a traction element which is movably arranged in an H shape or a cross shape at the linear guide units and is secured to the carrier. The loading system preferably finds use in a deblocking device in order to transport blocked and also deblocked workpieces and block pieces with a very high dynamic between a transfer station and a loading station of the deblocking device and to respectively receive or deliver them thereat.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2019 006 503.4 | Sep 2019 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2020/000150 | 9/7/2020 | WO |
