A method for separating a respective sheet from a sheet pile and transporting it to a sheet processing machine, wherein the respective sheet is lifted by at least one lifting suction device to a transfer level lying above a suction air intake level, and the respective sheet is taken over by at least one forwarding suction device at the transfer level, includes thereafter transporting the respective sheet by the forwarding suction device on the transfer level in a direction towards the sheet processing machine, and after transferring the sheet from the lifting suction device to the forwarding suction device, lifting the lifting suction device to an elevation level above the transfer level; a device for performing the method; and rotary printing machine and method of operation including the foregoing.

The invention relates to a method and device for separating sheets of paper from a sheet pile with the aid of at least one lifting suction device and for transporting the sheets to a sheet processing machine with the aid of at least one forwarding or pull suction device.
The published German Patent Document DE 43 24 552 A1 teaches the use of a pneumatically controlled lifting suction device and a pneumatically controlled forwarding or pull suction device. In this reference, the lifting suction device separates the sheet from a sheet pile by lifting the sheet to a transfer level. The forwarding or pull suction device takes the sheet from a return level to a lower-lying transport level during a return motion. To prevent tensions in the sheet, the lifting suction device must simultaneously release the sheet; i.e., only a very short time window is provided for releasing the sheet. Particularly in the case of changing machine speeds, the air inertia of pneumatic systems can lead to defective sheet transfers from the lifting suction device to the pull or forwarding suction device, because no assurance can be offered that the lifting suction device would let the sheet go precisely when the forwarding or pull suction device picks it up.
It is accordingly an object of the invention to provide a method and device for separating and transporting sheets whereby sheet transfer from a lifting suction device to a pull or forwarding suction device is improved over the prior art methods and devices.
With the foregoing and other objects in view, there is provided, in accordance with the invention, a method for separating a respective sheet from a sheet pile and transporting it to a sheet processing machine, wherein the respective sheet is lifted by at least one lifting suction device to a transfer level lying above a suction air intake level, and the respective sheet is taken over by at least one forwarding suction device at the transfer level, which comprises thereafter transporting the respective sheet by the forwarding suction device on the transfer level in a direction towards the sheet processing machine, and after transferring the sheet from the lifting suction device to the forwarding suction device, lifting the lifting suction device to an elevation level above the transfer level.
In accordance with another mode, the method of the invention includes, in a return motion, moving the forwarding suction device from one terminal location to another terminal location on a return level situated above the transfer level.
In accordance with a further mode of the method, the return level is the elevation level above the transfer level.
In accordance with an added mode, the method invention includes lowering the lifting suction device from the elevation level to the suction air intake level after transporting the respective sheet away.
In accordance with an additional aspect of the invention, there is provided a device for performing a method of separating and transporting a sheet from a sheet pile, comprising a lifting suction device for separating the sheet from a sheet pile, a forwarding suction device for transporting the sheet in a direction towards a sheet processing machine, and a cam mechanism for moving the lifting suction device to three different elevation levels.
In accordance with another feature of the invention, wherein one of the elevation levels is a suction air intake level, and the suction air intake level of the lifting suction device is adjustable.
In accordance with a further feature of the invention, the forwarding suction device is pneumatically adjustable to two different elevation levels of the three different elevation levels.
In accordance with yet another aspect of the invention, there is provided a sheet-fed rotary printing machine having a device for performing a method of separating and transporting a sheet from a sheet pile, the device comprising a lifting suction device for separating the sheet from a sheet pile, a forwarding suction device for transporting the sheet in a direction towards a printing unit, and a cam mechanism for moving the lifting suction device to three different elevation levels.
In accordance with a concomitant aspect of the invention, there is provided, in a method of operating a sheet-fed rotary printing press, a method for separating a respective sheet from a sheet pile and transporting it to a printing unit, wherein the respective sheet is lifted by at least one lifting suction device to a transfer level lying above a suction air intake level, and the respective sheet is taken over by at least one forwarding suction device at the transfer level, which comprises thereafter transporting the respective sheet by the forwarding suction device on the transfer level in a direction towards the printing unit, and after transferring the sheet from the lifting suction device to the forwarding suction device, lifting the lifting suction device to an elevation level above the transfer level.
The advantage of the inventive method is namely that a larger time window is provided for the sheet transfer from the lifting suction device to the forwarding suction device, while at the same time tension in the sheet and scratches or abrasions of the sheet by the lifting suction device during transport of the sheet by the forwarding suction device are prevented.
In addition, during its return, the forwarding suction device does not contact the sheet which has been lifted with the aid of the lifting suction device, either.
The advantage of the device according to the invention lies particularly in the combination of a mechanically elevation or height-controlled lifting suction device and a pneumatically elevation or height-controlled forwarding suction device.
This measure makes it possible to construct a sufficiently long time window for transferring the sheet and, as a result, the exact sheet transfer does not depend upon the inertia of the air control.
Other features which are considered as characteristic for the invention are set forth in the appended claims.
Although the invention is illustrated and described herein as embodied in a method and a device for separating and transporting sheets, it is nevertheless not intended to be limited to the details shown, since various modifications and structural changes may be made therein without departing from the spirit of the invention and within the scope and range of equivalents of the claims.
The construction and method of operation of the invention, however, together with additional objects and advantages thereof will be best understood from the following description of specific embodiments when read in connection with the accompanying drawings, wherein:

Method and device for separating and transporting sheets of paper


A rainwater distribution system for storing and distributing rainwater includes a first container configured to store rainwater and having a bottom wall and a side wall; a planting container being elevated off of the bottom wall and within the first container, and having a planting container bottom wall and a side wall; a planting container support configured to elevate the planting container off of the bottom wall and within the first container; a cascade aperture having a cascade filter, the cascade aperture positioned on the side wall of the planting container, and allows the rainwater that enters the planting container to exit the planting container into the first container; and an outlet aperture positioned on the side wall of the first container and configured to allow the rainwater to exit the first container at a controlled rate.

Rainwater collection systems such as rain gardens and rainwater tanks prevent rainwater runoff from flowing into storm drains and surface waters by providing the fluid an opportunity to soak into the ground or be saved for later use. These systems can improve the overall water quality in nearby bodies of water as more pollutants are contained rather than being transported across impervious surfaces like roofs, compacted lawn areas, and streets. In the case of rainwater tanks, the collected rainwater can be released in a controlled manner or used for various functions, such as watering plants.
Although useful, rainwater collection systems are commonly known to have several deficiencies. Rain gardens often contain only one inlet area, which can lead to uneven distribution of the rainwater to the plants. Both rain gardens and rainwater tanks are only capable of containing a finite water volume and often lack systems to control overflow. Neither rain gardens nor rainwater tanks function appropriately during winter or frozen condition months and are intended to be taken off-line or will freeze solid. Unfortunately, because these systems are often placed near building structures, heavy rains can lead to overflowing rainwater flooding basement structures as well as the overwatering of plants near-to or within the systems. Additionally, because certain paints and roofing materials contain contaminants, airborne pollutants, and bacteria from birds and small mammals (e.g., squirrels, bats), tend to settle on rooftops, these systems, which often lack means of containing this waste, only serve to delay such unwanted chemicals from eventually entering the groundwater. Rainwater tanks may also allow bacteria to grow due to long-term standing and stagnant water contained within the tanks.
Integration of these systems has also been traditionally cumbersome. Conventional rain gardens require some amount of excavation and as do rainwater tanks that are stored underground. When stored above ground, these large tanks often take up space that could be otherwise be used for storage, recreational area activities, or planting gardens. These systems can be large and difficult to initially transport to the site. Also, rainwater tanks in particular often necessitate that additional piping, pumps, and collection mechanisms are added to the existing structure.
While the known rainwater collection systems described above can provide benefits, problems still exist with their mechanical design and operability. Therefore, it is desirable to provide improved systems and methods for rainwater collection and controlled outflow that overcome the deficiencies described above.

Systems and methods for rainwater collection and controlled outflow


A display apparatus includes a display module having a display surface configured to display an image, and a window member disposed on the display surface. The window member includes a flexible base layer having a plurality of concave patterns defined on an upper portion thereof, and a plurality of hard coating patterns each disposed in a respective one of the concave patterns and having a hardness greater than the hardness of the flexible base layer.

Generally, in a display apparatus, glass is used as a window member for protecting a display panel. In addition, tempered glass is used as a window member for protecting the surface of a display apparatus of a mobile terminal such as a smart phone, a table personal computer (PC), and the like. However, there are disadvantages in that glass and tempered glass may break by an external impact and it is difficult to apply glass and tempered glass to a flexible display. Accordingly, a study for implementing a window member by using a plastic material has been steadily in progress.
Plastic has been applied as an alternative material for glass because plastic is lightweight, shock-resistant, transparent, and the like. A trend of composing a window member by using a plastic material, which is excellent in properties such as weather resistance, scratch resistance for enduring scratches by an external stimulus, shock resistance to an external impact, and machinability, is gradually increasing. A window member composed of plastic may make a display apparatus slim and improve the flexibility of a display apparatus such that a flexible display may be implemented.

Display apparatus and manufacturing method of window member included in display apparatus


An antenna unit includes a dielectric substrate, an antenna layer, a ground layer, and an additional structure; the antenna layer is disposed on a first surface of the dielectric substrate; the ground layer is disposed on a second surface of the dielectric substrate; wherein the first surface and the second surface are opposite surfaces of the dielectric substrate; the additional structure includes any combination of the following structures: a floor meander structure disposed on the second surface and in a same layer as the ground layer to improve isolation of an antenna, a patch meander structure disposed on the first surface and in a same layer as the antenna layer to expand a bandwidth of an antenna, and a branch structure disposed on the second surface and in a same layer as the ground layer to improve isolation of an antenna and expand a bandwidth of the antenna.

Antenna units are widely used in the field of communication such as communication, navigation, and radar. At present, with development of electronic devices, an antenna unit tends to be miniaturized, which making spacing of each structure in the antenna unit more and more compact, and causing a mutual coupling effect. However, an intensive mutual coupling effect will change amplitude and phase distribution of a current of the antenna unit, resulting in poor antenna performance.

Antenna unit, preparation method, and electronic device


The invention is directed to a hand tool for cutting shavings from the surface of a workpiece of wood (or other workable material) to shape and make smooth any three-dimensional surface having concave, flat, and/or convex contours. The thickness of the shavings is modulated by the angular relationship and distance between a blade and a regulating post. An embodiment comprises a combination body and handle holding a protruding cutting blade at an angle of about 30° to the surface of the workpiece, and an adjustable protruding post in front of the cutting edge to limit the effective exposure of the cutting edge as the tool is moved into contact with the workpiece. The embodiments provide a full view of the cutting zone and unrestricted one-hand use on surfaces of any contour.

In the hands of a skilled woodcarver, chisels and gouges are an excellent (and sometimes the only) hand tools that can cut virtually any contour on a workpiece. They are best used to cut specific shapes and details while working to layout lines, and for incising away sizeable chunks of waste material quickly. Often a mallet is used to drive the cutting edge into the wood. These tools are not as well suited to working areas of freeform surfaces to continuously blended finished contours, a task best performed by a tool that merely shaves or planes the surface, rather than cutting deeply into the wood under the skillful guidance, control, and physical effort of the woodcarver.
There are a great many designs and styles of woodworking hand planes and spokeshaves that have been developed over time, all to perform the same basic operation on a workpiece of wood or other workable material. That operation is to remove thin shavings of controlled thickness from a rough and/or uneven surface to render it smooth and even. When a perfectly flat surface is the objective, there are many designs to accomplish this task. From ancient wood-block planes to the most modem metal hand planes in current production, all have the same two features in common: a planar sole surface and a sharp-edged blade (traditionally called an "iron") protruding slightly from the sole surface to shave material only from those areas of the workpiece that can come into physical contact with the sole.
In some cases, a convex surface or a concave surface must be made accurate in form and smooth in appearance. If the surface is cylindrical, a plane having a sole of complementary (matching) cylindrical curvature and a straight-edged iron can be used in the same manner as flat-soled planes are used on a planar surface. There are even some designs for planes with flexible soles that can be adjusted to match a desired curvature, and multi-piece soles whose elements can be positioned in relation to each other so they all will be in contact only with a certain cylindrical surface.
In general, a plane is adapted for work on a given flat, concave, or convex surface by machining its sole (the surface that contacts the workpiece) to have a complementary contour; i.e., flat, convex, or concave respectively. For compound-curved surfaces, the cutting edge of the blade can also be curved. Obviously, planes having flat or concave soles have limited utility on free-form three-dimensional surfaces because they can engage and cut only convex surfaces whose radius of curvature is less than that of the sole or the cutting edge. Work on any given three-dimensional free-form surface requires a plane having both a convex sole and a convex edge, each having a radius of curvature less than or equal to the smallest concave radius of curvature anywhere on the surface.
The cutting conditions on a three-dimensional compound-curved surface are quite different than on either planar or cylindrical surfaces. The sole of the plane is not in full contact with the work surface. Rather, contact occurs only in the vicinity of the mouth, through which the cutting edge of the iron protrudes. In order to maintain smooth cutting conditions, the plane must be guided over the work surface in such a way that the mouth is kept tangent to the work surface at all times. Sight and feel must be relied upon to selectively remove material only from those areas that are proud of the desired finished contour. The curvature of the sole has no influence upon the curvature of the surface of the workpiece unless the sole can come into substantially full contact with that surface.
A plane taking a full-width chip in hardwood, or even most softwood, requires a lot of force to push (or pull). For this reason, bench planes, with irons from 1.75 inches up to 2.63 inches in width, are designed to be held and used with two hands. Block planes are designed to be held and used with just one hand, and their irons are generally 1.38 inches wide, and not more than 1.63 inches wide, in order to limit the maximum force required to push the tool. They are often used to chamfer edges and corners, which limits the width of the chip and thereby minimizes the force required. However, when used to plane a flat surface, a block plane becomes much harder to push and control with just one hand, so the other hand is often needed to assist the gripping hand.
Aside from undesirably high force requirements, planes also have another characteristic that can cause great difficulty. Cutting "with the grain" is a term all woodworkers come to know and understand. This is especially important to the proper functioning of a plane, because cutting "against the grain" causes the iron to dig into the wood, lifting the fibers and splitting them apart ahead of the cutting edge rather than cutting them cleanly. Such a split will always extend below the line of cut, and the finished surface will have a defect (crater) in it that is called a "tear out". In straight-grained woods, cuts can easily be made with the grain by good judgment gained from experience, and so-called "paring cuts" made across the grain at about a 45° angle to either side. However, there are woods having a curly grain pattern, such as Bird's Eye Maple and Tiger Maple, that cannot be planed in any direction without going against the grain in some portion of any cutting stroke. Here it is essential that the plane be able to cut freely and continuously without any tendency to "catch", "dig-in", or "stall in the cut" (common descriptive terms for typical interruptions of the cutting process). Whenever such an interruption occurs, it is likely to produce a tear-out in the surface. It should be noted that the lower the cutting force, the easier it is to control and maintain ideal cutting conditions at the cutting zone.


A connecting assembly comprises a shaft journal with an outer journal groove; a constant velocity universal joint with an inner joint part which, for the purpose of transmitting torque, is connected to the shaft journal in a rotationally fixed way and which comprises a sleeve projection, wherein, in an outer circumferential face of the sleeve projection, there is provided an engagement recess; a securing sleeve for axially fixing the inner joint part relative to the shaft journal; wherein the securing sleeve comprises inner holding portions which engage the journal groove, as well as outer holding portions which engage the at least one engagement recess.

The invention relates to a connecting assembly between a shaft journal and a constant velocity universal joint used, more particularly in the drive line of a motor vehicle. The constant velocity universal joint comprises an outer joint part connectable to a driveshaft, an inner joint part which is engaged by the shaft journal in a rotational fixed way for torque transmitting purposes, as well as torque transmitting elements which are effective between the outer joint part and the inner joint part. The shaft journal can be the input part or the output part of a drive, more particularly of an axle differential or of a transmission, so that the shaft journal is axially and radially fixed. Accordingly, the constant velocity universal joint can be positioned at one end of a propeller shaft. The shaft journal can also be radially elastically supported in an elastic intermediate bearing, with the constant velocity universal joint then being used as the central joint of a two-part propeller shaft.
From DE 10 2004 048 079 A1, there is known a connecting assembly between a constant velocity universal joint which is arranged at the end of the propeller shaft and an axially fixed shaft journal of a gearbox. By means of longitudinal teeth, the shaft journal engages an inner joint part of a constant velocity universal joint in a rotationally fixed way. The propeller shaft comprises a threaded portion on to which there is threaded a threaded sleeve. The threaded sleeve engages a threaded recess of the inner joint part, with a securing ring being arranged in the threaded recess axially fixing the inner joint part relative to the threaded sleeve.
U.S. Pat. No. 4,756,640 proposes a connecting assembly between the inner joint part of a constant velocity universal joint and a shaft journal, using a securing element. The securing element comprises a shoulder which is axially held in an outer annular groove of the shaft journal, as well as a plurality of longitudinally extending elastic fingers which engage an inner annular groove of the inner joint part.
Overall, connecting a constant velocity universal joint to a shaft journal is complicated because, there is available only a limited amount of space and the final assembly stage is also complicated. At the same time, the connecting assembly between the constant velocity universal joint and the shaft journal is subject to optimum safety regulations to prevent disconnection and to ensure minimum adverse effects on the strength of the components.
It is the object of the present invention to propose a connecting assembly between a constant velocity universal joint and a shaft journal, which has s compact design, which permits secure axial fixing conditions and ensures a minimum effect on the shaft strength, with easy assembly and dismantling procedures being ensured as well.
The objective is achieved by providing a connecting assembly, more particularly for use in the driveline of a motor vehicle, comprising a shaft journal with an outer journal groove; a constant velocity universal joint with an inner joint part which is connected to the shaft journal in a rotationally fixed way for transmitting torque, and which comprises a sleeve projection, wherein, in an outer circumferential face of the sleeve projection, there is provided at least one engagement recess; a securing sleeve for axially fixing the inner joint part relative to the shaft journal; wherein the securing sleeve comprises inner holding portions which engage the journal groove, as well as outer holding portions which engage the at least one engagement recess.
The advantage of the inventive connecting assembly is that there are achieved secure axial fixing conditions between the inner joint part and the shaft journal. By means of its sleeve projection, the inner joint part is inserted into the annular chamber formed between the inner holding portions and the outer holding portions of the securing sleeve. This design allows the depth of the journal groove to be minimised, as a result of which the strength of the shaft journal is maximised in the region of the journal groove because the inner holding portions are radially secured against being widened by the sleeve projection of the slid-in inner joint part. The shape of the journal groove can be correspondingly flat, so that the shaft journal experiences only a slight cross-sectional reduction. A further advantage refers to the simple construction of the connecting assembly which comprises only a few parts, which has an advantageous effect on production costs. The connecting assembly requires only a small space, and the components are easily mounted. More particularly, the constant velocity joint can be completely pre-assembled, so that, during the final assembly stage, only the connection with the shaft journal has to be effected.
More particularly, the shaft journal can be the input part or the output part of a drive. If provided in the form of an input part, the shaft journal can be used for example in an axle differential which serves to distribute the introduced torque from the propeller shaft to two sideshafts. If provided in the form of an output part, the shaft journal can be used in a transmission from which the torque is introduced into the propeller shaft. The drive is fitted prior to the driveshaft being mounted, so that the shaft journal is axially and radially fixed in the drive housing.
For mounting purposes, the securing sleeve is slid on to the shaft journal far enough to allow the elastic inner holding portions to engage the journal groove. Then the inner joint part and thus the entire constant velocity universal joint is slid on to the shaft journal until the elastic outer holding portions engage the at least one engagement recess of the sleeve projection. In the slid-in condition, the sleeve projection, by means of its end portion, is arranged radially between the inner and outer holding portions of the securing sleeve. In this way the inner holding portions are prevented from widening radially, so that they are securely held in the journal groove. If viewed in half a longitudinal section, the securing sleeve preferably comprises an approximately C-shaped profile; to that extent, the securing sleeve can also be regarded as an envelope sleeve, with the inner joint part, by means of its sleeve projection being inserted into the annular chamber formed between the inner sleeve portion and the outer sleeve portion. The inner sleeve portion and the outer sleeve portion have a substantially cylindrical shape.
According to a preferred embodiment, there is provided a collar member which is slipped on to the securing sleeve and secures the outer holding portions against radial widening, with the collar member covering part of the sleeve projections of the inner joint part, including the securing sleeve. In its mounted condition, the collar member thus prevents the outer holding portions of the securing sleeve from being elastically bent open or widened radially outwardly, so that the connecting assembly is reliably secured even at high speeds and related centrifugal forces. For fixing the collar member, there can be provided a binding element or a securing ring, with the binding element preferably being designed in such a way that it cannot be closed unless the collar is accurately positioned on the sleeve projection. In this way, secure assembly conditions are ensured.
According to further preferred embodiment, the securing sleeve comprises a radial portion which connects the inner holding portions to the outer holding portions. The radial portion can be provided in the form of a continuous ring or it can comprise radial partial portions which are indirectly connected to one another. The securing sleeve is preferably shaped in such a way that the axial projection of the inner joint part, in the mounted condition, extends as far as the radial portion of the securing sleeve, more particularly, that it can be made to contact same. The radial portion of the securing sleeve thus functions as a stop if axial forces occur between the inner joint part and the shaft journal. The securing sleeve is preferably produced out of plate metal as a formed part. This is advantageous because the securing sleeve can then be produced in a simple way, for example by being turned over out of a circular blank or out of a meander-shaped strip material which is formed into a ring and subsequently welded, or it remains open. Using plate metal is advantageous in that the individual partial portions of the securing sleeve can be flat so that there is required only a small amount of installation space. However, different materials and production methods are also conceivable, such as producing the securing sleeve out of plastics.
According to a first design of the securing sleeve, the inner holding portions are provided in the form of elastic holding fingers which are circumferentially distributed and project from the radial portion in the longitudinal direction. The holding fingers preferably comprise radially inwardly directed engagement projections which are located more particularly at the end of the holding fingers and engage the journal groove. In this way, the inner joint part is axially secured relative to the shaft journal. The outer holding portions preferably comprise elastic holding tongues which engage the at least one engagement recess of the inner joint part. In a concrete embodiment, the outer holding portions each comprise two longitudinally extending side webs and one connecting web connecting same to one another, wherein the elastic holding tongues projecting inwardly from the connecting webs. Thus the circumferentially extending radial portion, the longitudinally extending side webs and the circumferentially extending connecting web form a frame around an aperture into which there extends the holding tongue. The holding tongues are slightly bent inwardly from the connecting web and, by means of their free ends, extend towards the radial portion of the securing sleeve. All the holding tongues engage the engagement recess which is preferably provided in the form of a continuous annular groove. If viewed in a longitudinal section, the profile of the annular groove is approximately adapted to the shape of the holding tongues, with the depth of the annular groove increasing more particularly towards the end of the sleeve projection.
According to a second design, the inner holding portions of the securing sleeve are provided in the form of circumferentially distributed inner holding tongues which extend in the longitudinal direction. The inner holding tongues preferably comprise inwardly directed first projections which engage the journal groove to provide axial security. In half a longitudinal section, the first projections can be provided in the form of bulging portions, preferably arch-shaped bulging portions, with the journal groove then preferably comprising a round or oval profile. The groove depth and the notch effect can thus be minimised, which has a positive effect on the strength of the shaft journal. Accordingly, the outer holding portions are preferably provided in the form of circumferentially distributed outer holding tongues which extend in the longitudinal direction. The outer holding tongues comprise inwardly directed second projections which engage the at least one recess of the sleeve projection to provide axially secured conditions. According to a preferred embodiment, the securing sleeve, in a developed view, is meander-like, with one inner holding tongue following to adjoining outer holding tongues and, accordingly, with one outer holding tongue following two adjoining inner holding tongues. This is achieved in that between each two adjoining outer and inner holding tongues, there are provided longitudinal slots, with the outer longitudinal slots extending into the opposed inner holding tongue and with the inner longitudinal slots extending into the opposed outer holding tongue. In this way, it is possible to achieve an elastic spring effect of the securing ring.
For both designs it is advantageous if the sleeve projection of the inner joint part comprises an inner recess with a preferably cylindrical inner face which delimits a receiving chamber for the inner holding portions of the securing sleeve. The inner holding portions are clamped in between the outer face of the shaft journal and the inner face of the sleeve projection. The inner holding portions are thus prevented from being radially bent open, which could be caused by centrifugal forces or radial forces induced by axial forces, so that the holding portions are securely fixed in the journal groove. At its end, the sleeve projection comprises preferably conical flattened portions in order to permit an easy assembly procedure by inserting the sleeve projection into the securing sleeve. At its outer circumferential face, the sleeve projection preferably comprises a radial projection up to which the outer holding portions, by means of their free ends, approximately extend in the mounted condition of the assembly. The radial projection which can be provided in the form of an annular bead thus forms an axial stop for the securing sleeve. To ensure sealing conditions, it is advantageous if the inner joint part, at its sleeve projection, comprises a continuous annular groove which can be engaged by the inner bead of a sealing member.
The rotationally fixed connection between the inner joint part and the shaft journal is preferably provided in form of a splined connection, other torque-proof connections not being excluded. This applies to all the above-mentioned embodiments. It is proposed that the journal groove which is engaged by the securing sleeve by means of its inner holding portions is arranged so as to axially adjoin the shaft splines. The annular groove is thus easy to produce because it is not positioned inside the shaft splines. The inner joint part comprises a ball track portion in which there are formed inner ball tracks, with the shaft splines axially extending beyond the ball track portion as far as and into sleeve projection. This measure allows the transmission of particularly high torque values.

Connecting assembly between a shaft journal and a constant velocity universal joint


An epoxy resin composition for semiconductor encapsulation in producing surface mount lead-less thin semiconductor devices. The epoxy resin composition for surface mount lead-less semiconductor device encapsulation which device comprising an encapsulating resin layer and, encapsulated therein, a substrate, a semiconductor element mounted on the substrate, two or more conductive parts disposed around the semiconductor element, and wires which electrically connect electrodes of the semiconductor element to the conductive parts, wherein the bottom face of the substrate and the bottom face of each conductive part are exposed without being encapsulated in the encapsulating resin layer, and the epoxy resin composition used for forming the encapsulating resin layer has the following properties (α) and (β): (α) a melt viscosity of 2-10 Pa.s at 175° C.; and (β) a flexural strength of cured state of 130 MPa or higher at ordinary temperature.

In the package mounting of semiconductor integrated circuits, individual parts such as transistors and diodes, and especially recently, LSIs, there are desires for package size reduction, thickness reduction, and integration degree increase. LSI mounting techniques include the packages of the type having lead terminals incorporated in the package, and this type of packages, which is represented by QFNs (quad flat non-leaded packages), is one of the package types which are especially attracting attention from the standpoints of size reduction and integration degree increase. A process which is especially attracting attention in recent years among processes for QFN production comprises orderly arranging chips for OFNs on a die pad in a package pattern region of a lead frame, en bloc encapsulating the chips in the cavity of a mold with an encapsulating resin material, and then cutting the molding into individual QFN structures to thereby greatly improve the productivity per unit lead frame area. On the other hand, for attaining improved connection reliability in the mounting of semiconductor devices on substrates such as mother boards, there is a desire for a semiconductor device having the so-called standoff, i.e., a semiconductor device in which the conductor on the mounting side partly projects from the encapsulating resin.
Furthermore, semiconductor devices of a lead-less structure have been developed recently for the purpose of thickness reduction. The following process has, for example, been proposed as a process for producing such a lead-less semiconductor device. First, a metal foil is laminated to a base and etched so that the metal foil remains in given areas to form a die pad part 23a and conductive parts 23b on the base 20 as shown in FIG. 7. Subsequently, a semiconductor element 21 is bonded to the die pad part 23a through an adhesive layer 24, and the semiconductor element 21 is then electrically connected to the conductive parts 23b with wires 25. The resultant structure is subjected to transfer molding with a mold to thereby resin-encapsulate the structure so that only the space in which the semiconductor element 21 is electrically connected to the conductive parts 23b is filled with an encapsulating resin layer 26. Thereafter, the base 20 is separated from the encapsulating resin layer 26 to thereby produce a package including the encapsulated semiconductor element as shown in FIG. 8 (see document 1). In this process, since a die pad part 23a and conductive parts 23b are formed on a base 20, the conductive parts can have a reduced thickness. In addition, when such packages thus obtained through resin encapsulation with an encapsulating material are separated into individual packages, there is no need of cutting a lead frame. This process hence has an advantage that blade wear by dicing is slight.
Document 1: JP-A-9-252014

Epoxy resin composition for semiconductor encapsulation, semiconductor device using the same, and process for producing semiconductor device


A toy doll, posable and simulating stances or positions and movements of a skater, dancer or the like. The device includes a torso with arms and leg which may be frictionally pivotably connected to the torso to enable posing the doll in a wide variety of positions. The doll is supported atop a self-propelled base by engagement of a foot or skate, such as an ice skate, roller skate, roller blade or the like, with a platform which forms a portion of the upper surface of the base. The base is supported by a front wheel and by two spaced apart rear wheels. The base is propelled by one rear wheel and steered by a replaceable profile cam-guided front wheel. The platform is rotated along with the doll about an upright axis as the base is propelled over a horizontal surface through a repeated geometric pattern defined by the particular profile cam selected.

1. Scope of Invention
This invention relates generally to movable toy dolls, and more particularly to a posable toy doll mounted on a self-propelled base which moves the doll to simulate as for example, an ice skater or a dancer.
2. Prior Art
Posable toy dolls are well known wherein the arms and legs of the doll are positionable in an almost infinitely variable number of positions, those selected positions then held by a frictional pivoting joint between the limbs and the torso of the doll. One such device is shown in U.S. Pat. No. 4,186,516 invented by Ensmann. This invention simulates skating movements of an ice skater wherein the doll is mounted on a turntable of a support stand. As to the support stand is manually moved over a flat surface, the turntable is made to rotate by a freely rotatable roller offset from the axis of rotation of the turntable which also engages the horizontal surface. One of the legs is freely pivotable so that torso is free to rotate about that leg as the device is manually propelled and the toy doll spins with the turntable.
A radio toy is disclosed in U.S. Pat. No. 1,763,788 invented by Jobe, Sr. This device is directed to the combination of an audio frequency circuit of a radio receiver and miniature figures and puppets positioned on a playing surface which are moved to simulate dancing. The puppets and figures are caused to move by vibration of the playing surface.
A carousel-type toy is disclosed in U.S. Pat. No. 5,078,386 invented by Hou. This device simulates the movement of a full-size carousel, the carousel figures being supported and caused to both reciprocate vertically and revolve around a central vertical support axis as the carousel itself rotates.
Koper has invented a mechanical toy as disclosed in U.S. Pat. No. 1,516,300. This toy also simulates a carousel having a novel drive means for rotating the platform at uneven speeds.
Another toy carousel is disclosed in U.S. Pat. No. 2,457,447 invented by Cohn. This invention includes an invented first hemisphere interconnected to a separate side-oriented second hemisphere. The first hemisphere rotates about its vertical axis by a spring wound motor, supported from side rotation by the second hemisphere.
A roundabout is disclosed in U.S. Pat. No. 753,043 invented by Cleal. A number of figures are mounted on a platform which are given movements independent of that of the platform. Mirrors are mounted on upright walls to project an image of an increased number of figures.
Spiegel has invented a moving figure toy roundabout as disclosed in U.S. Pat. No. 3,854,716. This roundabout provides the appearance of an amusement park having a plurality of individually connectable and selectively operable roundabouts driven by a common motor.
None of these above-referenced inventions, however, are completely independently self-propellable and offering the simulation of a toy doll dancing or skating across a horizontal surface in a controlled geometric pattern while the doll rotates on the self-propelled base.


A safety marker includes an hollow frusto-conical body; a base having an bowl-shaped main portion and a resiliently flexible skirt for yieldably stabilizing the marker against tipping relative to a supportive surface, the body being connected in upstanding relation to an inner portion of the base and concentric therewith, the base being formed to clear the cone defined by the inside surface of the body, the bowl being sufficiently large relative to the body and the base being weighted sufficiently that the marker is self-righting, the skirt being sufficiently flexible to be deflected against the bowl for preserving the self-righting capability of the marker. A flag supported relative to the body is movable between a deployed position projecting from the body and a storage position extending proximate the outer surface of the body, the flag being biased into the deployed position, whereby the storage position is attained and maintained in the stacked condition by the adjacent marker and the deployed position is attained and maintained upon unstacking of the adjacent marker, identical counterparts of the safety marker being stackable with the outside body surface of one marker being in proximate contact with the inside body surface of an adjacent marker.

The present invention relates to safety markers of the type used at highway construction sites, for warning vehicle drivers of obstructions, dangerous conditions, etc.
Many of the safety markers in common use are molded from brightly colored synthetic rubber or other plastic, in the form of elongate, truncated hollow cones having a relatively small opening at the top and an outwardly extending flange at the bottom. See, for example, U.S. Pat. No. 2,333,273 to Scanlon. These conventional marker cones are stackable for compact storage, and they can be delivered from a stack upright onto the ground from a moving vehicle; however, they are subject to being knocked over or blown over by high winds, and they are not self-righting. Also, they are undesirably heavy and bulky when made sufficiently large to be effective as a safety marker.
As a result of the above, a number of different marker configurations have been proposed. U.S. Pat. No. 3,386,409 to Dawson discloses a self-righting traffic cone having a hollow frusto-conical body and an outwardly and upwardly curved base rocker portion, the cone being self-righting and stackable. U.S. Pat. No. 2,275,711 to Ybanez discloses an axially collapsible cone that is pivotally connected and releasably latched to a platform base, a flag projecting upwardly from the cone. U.S. Pat. No. 4,925,334 to Beard discloses a traffic marker cone having a hangar for supporting an upwardly and outwardly projecting flag, the flag and the hangar being storable within the cone. None of the safety markers of the prior art is entirely satisfactory; for example:
1. The cone of Dawson can easily be blown partially over by the wind, being then subject to being rotated on its axis blown along for considerable distances out of position; PA1 2. The safety signal of Ybanez requires complicated manual operations for deployment and collapsing, and is not self-righting; and PA1 3. The marker of Beard suffers from the disadvantages of the device of Ybanez, and further that it is not stackable together with the hangar and flag.
Thus there is a need for a safety marker that is both stable and self-righting, having a large attention-commanding presence but a compact stackable configuration, and that can be easily deployed and stacked without manual assembly or disassembly.


At least one live conductor and one neutral strap are provided for an electricity meter, the respective inlets and outlets of the live conductor and of the neutral strap being disposed inside the meter housing parallel to one another and being coplanar. A metal bar connected to neutral is disposed inside the meter housing in the vicinity of and at a short distance from the inlet and/or the outlet of the live conductor to define a gap in which a controlled arc between the live conductor and the metal bar can propagate in the event of a surge.

This disposition of live conductors and of the neutral in the housing is typical for electricity meters of the kind used, for example, on the European market. A sudden change in current on the grid can give rise to a surge on one of its phases. If the surge is large enough, the surrounding air becomes ionized, thus becoming conductive, and an electric arc is struck between one of the phases and neutral. The very high energy of the arc, as maintained by the electricity mains, heats the air and can cause the housing to explode. This risk increases with increasing volume of air that is heated.
In conventional meters, the problem of a surge on one of the live phases is often handled by using a varistor between the phase and neutral, the varistor being placed at the inlet to the meter so as to protect its electronic circuits. Below a predetermined threshold voltage, the varistor is normally non-conductive. If the voltage exceeds the threshold, then the varistor becomes conductive and the surge is diverted to neutral.
An example of another protection system of that type is given in U.S. Pat. No. 5,282,108. Each live inlet is connected via a cable to an electrode located immediately above a metal plate which is grounded via a resistor in the form of a block. In the event of a surge, the current between the electrode and the plate is conducted to ground via the resistor.

Electricity meter provided with a system for protection against surges


The optical properties (absorption, reflection, transmittance, transparency) and physical attributes (hardness, friction, durability, etc.) of metal oxides, nitrides, or films that combine these materials can be modified by adding fluorine to the deposition mixture. The extent of change in properties depends on the amount of fluorine incorporated. Contrary to previous information, the presence of fluorine does not prevent adhesion of overlayers such as hard carbon, hydrogenated carbon, or diamond-like carbon. Considering for example massive silicon oxynitride hardcoat layers which are part of wear resistant composite windows for visible spectral applications, preferably fluorine is incorporated in a relatively very thin surface-adjacent region or layer of the hardcoat on the side thereof on which a carbonaceous layer such as DLC is formed. As a result, the index of refraction of the very thin surface region is reduced, the surface region can be used as an effective interference layer, absorption is reduced, reflectance is reduced, transmittance and transparency are improved, and durability is maintained. These fluorine-modified films can be used in many optical designs, including windows or wear resistant coating for laser scanner windows and ophthalmic applications.

A. Field of the Invention
The present invention relates to wear or abrasion resistant windows or composites which include optical thin films and have visible spectral applications and, in particular, to such windows which include carbonaceous films.
As used here in reference to the present invention, the term wear or abrasion resistant window or abrasion resistant glass window, refers to a window which is used in applications such as laser bar code scanners and which is transparent over applicable portions of the visible spectrum. The wear resistant window is a composite which comprises a transparent substrate of material such as glass or silicon oxide and one or more thin film coatings which enhance physical and/or optical properties of the substrate such as durability and transparency for visible radiation. The word "window" is used here to denote the substrate on which the thin film coating(s) are formed and as a shorthand reference to the overall coated substrate composite. Also, "index" is used as shorthand for index of refraction.
B. Description of the Related Technology
1. Non-Fluorine-Containing Wear Resistant Glass Window
Wear resistant windows are used in applications such as laser bar-code scanners in point-of-sale (POS) equipment. In some applications such as in the POS equipment used in groceries and convenience stores, wear resistant windows are subjected to severe mechanical abrasion by moving bottles, cans, and other merchandise. Glass windows which are or include ordinary glass typically are quickly scratched beyond usefulness by short periods of use in such an environments. Although crystalline or polycrystalline aluminum oxide (sapphire) is superior in that it is much harder than glass, sapphire is unsuitable for most commercial applications because it is extremely expensive.
High transparency is essential in laser bar-code scanner windows. Ordinary glass has a refractive index of 1.52 and a transmittance of about 92% for the red laser wavelengths which are of primary interest. Sapphire has an index of refraction of about 1.67 and a transmittance of about 88% over the same range of wavelengths. Coated wear resistant windows such as the above product are slightly absorbing, and are less transparent than uncoated glass or uncoated sapphire. Higher transmission is desirable in some cases in order to consistently meet the transmittance specifications. For example, an exemplary minimum transmittance for laser bar code scanner windows is 78% over the 600-650 nm (nanometers) portion of the visible spectrum. Under continuous use (i.e., subjected to mechanical abrasion), minimum transmittance must be maintained for scanner windows to avoid misreads. Therefore, one must balance transparency and resistance to mechanical abrasion in the selection of materials or coatings, to obtain a fully functional product.
Wear resistant window glass coatings are also described in U.S. Pat. Nos. 5,135,808 and 5,268,217. These patents teach that DLC (diamond-like carbon) will not adhere to sublayers containing fluorine and that the material of the layer immediately adjacent to the DLC coating must be a substantially optically transparent material devoid of alkali metal atoms and fluorine. Previous work (e.g., National Bureau of Standards Spec. Pub. 638 (1981) and Proceedings of the DARPA Workshop on DLC Coatings (1982)) discusses the adhesion of DLC to fluoride materials for primarily infrared applications. The literature also discusses the use of fluorine additions or dopants to enhance the electronic properties of metal oxide films, but does not focus on their optical characteristics, or other material properties such as hardness, adhesion to other materials, or film degradation.
2. Exemplary OCLI Abrasion Resistant Glass Window
Optical Coating Laboratory, Inc. previously developed a coated glass wear resistant window that exhibits durability approximating that of sapphire, and is less costly. The wear resistant window comprises two layers coated onto the exposed surface of a strengthened, i.e., tempered glass window or base. The first layer deposited on the glass is a relatively thick or massive silicon oxynitride (SiO.sub.x N.sub.y) layer prepared by reactive sputtering of silicon in the presence of a gas containing oxygen and nitrogen. The silicon oxynitride layer is approximately five micrometers (50,000 Angstroms) thick. The proportions of oxygen and nitrogen are adjusted during deposition to provide a suitable balance of stress, adhesion, hardness and transparency. The second or top layer is diamond-like carbon (DLC) which is approximately 200 Angstroms (0.02 micrometers) thick. The massive silicon oxynitride "hardcoat" layer imparts a high level of hardness or impact resistance to the window composite, while the DLC overcoating or overlayer contributes low friction or lubricity/lubriciousness.
3. Properties of Abrasion Resistant Glass Window (Window+Hardcoat+DLC Overcoat (FIG. 3))
The family 31 of curves, FIG. 3, depicts the measured spectral transmittance of five non-fluorine-containing windows of the type described above. The data for these windows are the first five entries in Table 1. All windows meet or exceed the minimum acceptable 78% average transmittance for the 600-700 nanometers range. In spite of its small thickness, the DLC layer is quite absorbing and lowers the transmittance of the abrasion resistant window from that of the hardcoat itself. As with the hardcoat layer, the optical performance of the DLC is a consequence of optimized mechanical properties. Deposition process parameter variations that result in increased transparency (lower absorption) diminish the critical mechanical properties of stress, adhesion and friction or lubricity.
The measured values for fifteen production samples (including those from FIG. 3) are listed in Table 1. The data in the last column (average transmittance over the 600-700 nanometers wavelength range) is also shown in the family 41 of data depicted in FIG. 4.
TABLE 1 ______________________________________ Measured Transmittanae for 15 Abrasion Resistant Glass Production Samples Sample Measured Transmittance (percent) number 400 nm 632 nm Avg 600-700 nm ______________________________________ 1 56.78% 78.11% 79.02% 2 57.39 80.52 79.42 3 56.56 79.30 79.30 4 56.01 79.21 79.21 5 56.95 79.17 79.17 6 56.89 79.36 79.28 7 56.83 78.21 79.46 8 56.72 80.10 79.42 9 55.94 76.97 78.98 10 55.54 77.79 79.11 11 57.83 80.54 79.47 12 54.29 80.08 78.64 13 54.58 77.75 78.79 14 55.89 78.46 78.76 15 54.60 76.87 78.63 ______________________________________

Fluorine-containing abrasion-resistant optical thin film devices


A graphics system comprising a format processor for receiving display data including pixel data and color-blending information for at least two (2) separate display layers, a color blender and color processors. The pixel data includes color information for the display layers. The color-blending information determines weighting factors for use in blending the colors of the display layers. The format processor outputs separate streams of pixel data, one for each display layer, as well as the weighting factors. Each stream of pixel data outputted by the processor is inputted into a corresponding color processor that assigns colors to a particular display layer according to the color information in the corresponding pixel data. The color blender blends the colors assigned to the display layers according to the weighting factors.

1. Field of the Invention
The present invention pertains to computer graphics systems.
2. Problem to be Solved
In many computer graphic systems, such as Graphical User Interfaces (GUI), Computer Aided Design (CAD), Computer Aided Engineering (CAE) or Image Processing, multiple layers of display information are used. In particular, there is a main application layer or window and at least one overlay layer or window. Display information is presented in layers or windows defined by software. The overlay layer may be used to provide on-screen selection from a number of control options pertaining to the underlying main application layer. Common uses of overlay layers or windows include "Pop-Down Menus", "Help Menus", Control Panels and other data for providing information and control functions.
A computer graphics system generally comprises a Graphics Controller, Graphics Memory, and a Palette DAC. (The Palette DAC is sometimes referred to by such names as "RAMDAC" or as "LUT-DAC" or incorrectly as simply "DAC".) The computer graphics system is connected to the rest of the computer system over the System Bus. The Graphics Controller provides the interface of the computer graphics system to the System Bus. The Graphics Memory is loaded with graphics data supplied by or via the Graphics Controller. The graphics data stored in the Graphics Memory is provided to the Palette DAC, which processes and converts that graphics data, providing the results of that processing and conversion to the Display Device for presentation as a visual image.
The input to the Palette DAC typically comprises a serializer, which receives graphics data serially from the Graphics Memory. That data is typically several pixels wide and provided at a frequency that is some fraction of the display pixel frequency. The output of the serializer is typically one (1) pixel wide at full pixel frequency. The pixel frequency may be as high as 250 MHz and, in some special cases, much higher than 250 MHz. The output of the serializer is continuous and in synchronism with the Display Device. The output of the serializer satisfies the real time data needs of the Display Device. The output of the serializer typically contains at least two types of data: a Window Identifier (WID), and the pixel data for at least two display layers. The display layers will at least consist of a main display layer and an overlay display layer.
The WID is a pointer used to locate window attributes from a Window Attribute Table (WAT). The attributes are typically loaded into the WAT by software. The attributes define the format of the pixel data, the presence and number of display layers associated with that pixel data, how that pixel data is to be partitioned between the display layers, the type of processing to be applied to the pixel data of each display layer, and the criteria for the decision of which of the layers is to be displayed. The criteria for that decision may be based on a selection made directly within the attributes or be made dependent on the value of the pixel data (pixel-based criterion) within any given display layer. In all cases, at any given pixel location, only pixel data from the selected layer is displayed, and pixel data from all other layers will not be displayed and will be effectively obscured from view.
The pixel data outputted from the serializer is inputted into a processor which separates and formats the pixel data according to the window or pixel attributes stored in the WAT. As stated above, the window or pixel attributes determine which portions of the pixel data are to be associated with each display layer. After separation and formatting, an original color is assigned to the pixel location of each layer. The color assignment process can take any one of a number of forms including the use of Color Look-Up Tables, Direct Color Bypass, Algorithmic Conversion, or Color Space Conversion.
Typically, there are many pixel locations where an overlay layer and an underlying layer interact, i.e. the overlay layer and the underlying layer are defined by the same pixel locations. Since only one color value can be displayed at any one pixel location on the display screen, a multiplexer selects a color value of a pixel location from either the underlying layer or the overlaying layer. The multiplexer output is then inputted into a three (3) channel digital-to-analog-converter which converts the digital signal representing the selected color into three (3) analog signals representing the primary colors red, green and blue for use with a display device.
Thus, graphical information from either the underlying layer or the overlay layer is displayed on the display device. If the graphical information is selected from the underlying layer, then the overlay layer is said to be "transparent". If the graphical information is selected from the overlay layer, then the overlay layer is said to be "opaque". The overlay layers are typically rectangular in shape and are formed from solid colors. When an overlay layer is displayed over an underlying layer, the solid colors assigned to the pixel locations of the overlay layer are used to replace (on a per-pixel basis) the assigned colors to the pixel locations of the underlying layer. Thus, the solid colors of the overlay layer obstruct the user's view of the underlying layer. Typically, the underlying layer is often a main application display layer or window. Furthermore, the overlay layer or window often obstructs the main application window at the precise area to which the information provided by the overlay layer pertains. This feature has undesirable side-effects which cause inconvenience to the user, and also provide an uncomfortable aspect and feel to the user interface. Such negative aspects ultimately result in a reduction in user acceptance of the graphics system and degradation in productivity.
Thus, bearing in mind the aforementioned problem of conventional graphics systems, it is an object of the present invention to provide a graphics system that provides a user with a clear and unobstructed view to the graphic information provided by all the display layers.
It is another object of the present invention to provide a process for displaying at least two (2) display layers wherein the user is provided with a clear and unobstructed view to the information provided by both overlay and underlying display layers.

Graphics system and process for blending graphics display layers

International Business Machines Corporation


A chemical/biological wastewater treatment plant method and apparatus employing rapid sludge chemical dewatering technology in conjunction with an environmental biological system for treating the separated treated wastewater by land applying it for plant consumption, and/or passing it through aqueous plant or microbial reduction of the dissolved solids and ammonia for BOD compliance to produce water of sufficient quality to meet open stream and ocean effluent discharge requirements; and disposing of the high BTU low moisture solids.

1. Field
This invention comprises a rapidly installed wastewater treatment plant solids and liquids recovery system apparatus and method employing chemical dewatering and biological treatment technology.
2. State of the Art
Various sewage treatment methods and plants are known. Most large municipal systems employ a series of settling ponds sequentially concentrating the solids contained in wastewater either with or without polymers for separation from liquids via mechanical separation means, such as belt presses. In order to produce a clean effluent that can be safely discharged to watercourses, wastewater treatment operations use three or four distinct stages of treatment to remove harmful contaminants; according to the United Nations Environmental Programme Division of Technology, Industry, and Economics Newsletter and Technical Publications Freshwater Management Series No. 1, "Biosolids Management: An Environmentally Sound Approach for Managing Sewage Treatment Plant Sludge" which goes on to say: "Each of these stages mimics and accelerates processes that occur in nature.
Preliminary wastewater treatment usually involves gravity sedimentation of screened wastewater to remove settled solids. Half of the solids suspended in wastewater are removed through primary treatment. The residual material from this process is a concentrated suspension called primary sludge, which will undergo further treatment to become biosolids.
Secondary wastewater treatment is accomplished through a biological process, which removes biodegradable material. This treatment process uses microorganisms to consume dissolved and suspended organic matter, producing carbon dioxide and other by-products. The organic matter also provides nutrients needed to sustain the communities of microorganisms. As microorganisms feed, their density increases and they settle to the bottom of processing tanks, separated from the clarified water as a concentrated suspension called secondary sludge, biological sludge, waste activated sludge, or trickling filter humus.
Tertiary or advanced treatment is used when extremely high-quality effluent is required, such as direct discharge to a drinking water source. The solid residual collected through tertiary treatment consists mainly of chemicals added to clean the final effluent, which are reclaimed before discharge, and therefore not incorporated into biosolids.
Combined primary and secondary solids comprise the majority of material used at municipal plants for biosolids production. Careful management throughout the entire treatment process allows plant operators to control the solids content, nutrient value and other constituents of biosolids.

Wastewater chemical/biological treatment plant recovery apparatus and method


An image forming apparatus includes a first device to which a first memory is connected; a second device to which a second memory is connected; and a third device to which a third memory is connected. The third device includes a data transfer control unit configured to perform data transfers each for transferring data from one of the first to third memories to a destination memory of the first to third memories, according to direct memory access control in cooperation with the first device and according to an instruction received from the second device. Priorities and orders are assigned to the data transfers. The data transfer control unit arbitrates the data transfers by changing the orders of the data transfers based on the priorities assigned to the data transfers and by changing the destination memory of at least one of the data transfers.

1. Field of the Invention
The disclosures herein generally relate to an image forming apparatus, a control method and a storage medium. Especially, the present invention relates to an image forming apparatus provided with a data transfer function according to direct memory access control for image data between various types of memories connected to various types of devices, such as an engine ASIC (Application Specific Integrated Circuit), a controller ASIC or a processor, a control method for transferring the data for image formation processing and a storage medium.
2. Description of the Related Art
Conventionally, an image forming apparatus with a specification of multifunction peripheral (MFP), i.e. a digital multifunction peripheral, in which plural functions, such as a printer function, a copying function, a scanner function or a facsimile function are combined into a single chassis, is generally configured so that an engine ASIC is connected to a controller ASIC and instruction control for image formation processing is performed from a processor (CPU: central processing unit), which controls an entire apparatus connected to the controller ASIC, via the controller ASIC. For example, a configuration has been known, in which the controller ASIC and the engine ASIC are connected via a PCI interface, a PCI Express (hereinafter, referred to as PCIe) interface or the like, and the controller ASIC and the processor are directly connected by the PCIe interface or connected via a chipset.
Related art for the well-known art area includes, for example, Japanese Published Patent Application No. 2008-310798, disclosing an image processing controller and an image forming apparatus, in which a data transfer path using both PCI interface and PCIe interface can be controlled.
In the related art described in Japanese Published Patent Application No. 2008-310798, in order to improve data transfer performance for image data among the engine ASIC, the controller ASIC and the processor (CPU), availability is enhanced by providing plural interfaces including a PCI interface and a PCIe interface, and the data transfer path using the plural interfaces, such as the PCI interface and the PCIe interface can be controlled. However, a control means for the data transfer path does not take account of priority, so that when the data transfer of image data by the direct memory access control is performed among various types of memories connected to the engine ASIC, the controller ASIC and the processor, the data transfer is not always performed efficiently. Accordingly, there is a problem that a transfer band for other data transfer with higher priority is often reduced.

Image forming apparatus, control method and storage medium


A flow control regulator assembly having a regulator body with an inflow channel that couples an inlet of the regulator body to a flow rate port and an exit flow channel which couples the flow rate port to an outlet port of the regulator body. The minimal cross-sectional area of the exit flow channel is larger than the maximum cross-sectional area of the inflow channel.

Field of the Invention
Devices, systems, and methods consistent with the invention relate to a method and apparatus for providing an integral gas flow regulator and flow meter.
Description of the Related Art
During certain types of welding operations, such as gas metal arc welding (GMAW) a shielding gas is used. These shielding gases can be argon or carbon dioxide, for example. The shielding gases are typically delivered to the welding operation from a high pressure tank or gas source (can be as high as 3,000 psi). Although the pressure of the source of the gas is high, the pressure of the gas needed at the welding operation is considerably lower, typically between 10 and 50 psi. Further, it is typically required that the flow rate of the shielding gas at the weld be controlled to be a constant flow rate. Because of this, it is typically necessary to have a gas flow regulator and gas flow meter in the gas flow line between the source of the gas (e.g., tank) and the welding operation. Typically, each of the gas flow regulator and flow meter are separate components, thus requiring no less than two different devices to be connected to the gas line. This increases the cost and complexity of using gas.

Gas flow regulator with multiple gas flow passages


The invention relates to an apparatus for ballast weighing on a crane, comprising at least two ballasting cylinders that are equipped to lift/lower the ballast and that each comprise at least one pressure transducer in the region of the piston and/or rod side, and comprising at least one evaluation unit that is equipped to calculate the mass moved by the ballasting cylinders from the pressures detected by the pressure transducers on retraction and/or extension of the ballasting cylinders, excluding the friction forces occurring in the ballasting cylinders. The invention furthermore is directed to a method for calculating the ballast weight of a crane by means of a corresponding apparatus.

The counterweight or ballast weight provides a moment that counteracts the load carried by the crane. Thus, the counterweight substantially contributes to the stability of the crane. When the crane for example is provided with an automatic load moment limitation, the magnitude of the effective counterweight or the mass and the effective lever arm of the counterweight is used in the calculation of the stability of the crane. The terms mass and weight will both be used here, as it is clear to the skilled person how the respectively necessary variable is to be used or converted.
It is known that the crane driver or other operators of the crane manually enter the data necessary for carrying out the load moment limitation. With this procedure it is problematic that errors can occur when manually entering the necessary data and/or the necessary data cannot easily be retrievable.
Against this background it is the object of the invention to provide an apparatus or a method which reduce corresponding incorrect entries and/or can subject the manual entries of a crane driver or another operator to a cross-check or a plausibility check. According to the invention, a completely autarkically operating method or a completely autarkically operating apparatus can also be provided, which render entries made by a crane driver or an operator superfluous.
This object is solved by embodiments described in this disclosure, which is configured for ballast weighing on a crane and comprises at least two ballasting cylinders that are equipped to lift/lower the ballast. Multiple advantageous configurations are also described herein. Accordingly, there is provided an apparatus in which the ballasting cylinders each comprise at least one pressure transducer in the region of the piston and/or rod side, and which furthermore comprises at least one evaluation unit that is equipped to calculate the mass moved by the ballasting cylinders from the pressures detected by the pressure transducers on retraction and/or extension of the ballasting cylinders, excluding the friction forces occurring in the ballasting cylinders.
Advantageously, components already present on a crane, such as said ballasting cylinders, can be used as part of the apparatus according to the invention for determining the ballast weight. The scope of additional necessary components thus can be reduced. It is also conceivable that the evaluation unit is formed as part of a control/regulating unit already provided on the crane. The exclusion of the friction forces occurring in the ballasting cylinders can be effected for example by means of stored friction values that can be used by the evaluation unit and that can be taken into account when calculating the mass.
In a preferred embodiment it can be provided that the pressure transducers are arranged directly in the ballasting cylinders. Pressure-sensitive regions of the pressure transducers can be exposed directly to the pressure medium contained in the ballasting cylinders and therefor need not be coupled to the ballasting cylinders via additional pressure lines or the like, which otherwise would have to be formed as components different from the ballasting cylinders, such as for example external pressure lines. With such an arrangement of the pressure transducers the measurement accuracy can be increased. The measurement accuracy is increased in that a direct pressure measurement can be carried out in the space of the cylinder, which provides more exact measurement values than is the case with a measurement taking place in a region that is guided out of the space of the cylinder via conduits and hence is spaced apart from the cylinder. The arrangement of the pressure transducers in the ballasting cylinders furthermore reduces the risk of damages, as the pressure transducers are better protected by the structure of the ballasting cylinders than would be the case with pressure transducers not arranged within ballasting cylinders.
It is conceivable that the pressure transducers are arranged within lead-throughs in the walls of the ballasting cylinders in order to provide for a pressure measurement as direct as possible.
In another preferred embodiment it is conceivable that exactly one pressure transducer each is arranged on the rod side and one pressure transducer on the piston side of the ballasting cylinders. Due to the pressure measurement thereby possible on both sides of the ballasting cylinders an exact value of the pressure difference between the two sides of the ballasting cylinders can be determined and a value of the force exerted by the ballasting cylinders as exact as possible can be calculated therefrom.
The invention furthermore is directed to a method for calculating the ballast weight of a crane by means of an apparatus. The method comprises the following steps:
detecting the pressures in the ballasting cylinders; and
calculating the mass held by means of the ballasting cylinders on the basis of the detected pressures and by taking account of the associated surfaces.
Dimensions of the ballasting cylinders required for calculating the held mass or the surfaces on which the pressure medium acts can be stored or entered in the evaluation unit, so that as explained below a calculation of the forces exerted by the ballasting cylinders is possible by means of the surfaces of the ballasting cylinders charged with the corresponding pressures. The term of the held mass can of course also relate to a mass moved by means of the ballasting cylinders.
According to the method, in exactly one space each of the ballasting cylinders the pressure can be detected and on the basis of these pressures the load on the ballasting cylinders and thus the effective ballast weight can be determined or calculated. The space can be the rod-side or piston-side working space of the ballasting cylinders.
In a preferred embodiment it can be provided that
the detection of the pressures in the ballasting cylinders is effected on retraction and/or extension of the ballasting cylinders; wherein in particular
a calculation of pressure differences in the ballasting cylinders is effected on the basis of the pressures detected on retraction and/or extension.
It is conceivable that to increase the accuracy of the calculation pressures are detected in each space of the ballasting cylinders and the pressure detection is effected both on retraction and on extension of the ballasting cylinders. By calculating the pressure differences, the measurement accuracy of the calculation furthermore can be increased.
In a preferred embodiment it is conceivable that the method comprises the following step:
carrying out a plausibility check, wherein the calculated mass is compared with an in particular manually entered mass.
The mass of the ballast weight hence can be entered by an operator into the evaluation unit or into another calculating unit and/or control/regulating unit and/or be checked according to the method. When it is detected according to the method that a difference exists between calculated mass and manually entered mass, which exceeds a limit value, a warning can be issued for example by means of the evaluation unit and/or the operation of the crane can be restricted. What is also conceivable is an automatic entry of the weight or the mass of the ballast, wherein a correspondingly provided detection device detects the weight of attached ballast bodies and provides the same to the evaluation unit or provides the same for carrying out the plausibility check.
A possible division of a ballast recognition can also be included in the plausibility check. For example, weights of 2, 6, 10, 14 or 18 tons can be used as possible ballast weights. When the control or evaluation unit has determined a value of for example 2.4 tons according to the present invention, it can fix the ballast for the load moment limitation or the actual ballast weight at 2 tons. The admissible fuzziness for the allocation of the actual ballast weight in addition can be variable depending on the situation. For example, the influence of the ambient temperature can likewise be included.
In another preferred embodiment it is conceivable that the method comprises the following step:
use of the calculated mass in the load moment limitation of the crane.
The use of the calculated mass and other variables relates to the use of the calculated value of the mass for carrying out further method steps. The load moment limitation can be equipped to inhibit a movement of the crane on exceedance of a particular load and/or to issue warnings in order to avoid unstable conditions of the crane. For this purpose, the load moment limitation must know the effective ballast weight in order to therefrom determine or calculate admissible positions or loads of the crane and prevent the crane from tilting forwards or backwards or from falling back. This can occur for example when the boom is set too steep for the effective ballast.
In another preferred embodiment it is conceivable that the method comprises the following step:
measuring the temperature of the fluid medium and compensating temperature-related influences on the calculated mass.
The temperature of the fluid medium or the hydraulic medium can be measured for example within the ballasting cylinders and/or within lines leading to the ballasting cylinders and/or away from the ballasting cylinders. As different viscosities of the medium at different temperatures of the hydraulic medium can be taken into account, the temperature detection allows to take account of temperature-related influences on the pressure conditions in the apparatus or to determine corresponding compensation values or correction values from stored tables or the like and use the same for correcting the calculated mass or for compensating errors in a further calculation step.
The same applies for an alternative or additional compensation of friction influences on the calculated mass.
In another preferred embodiment it is conceivable that the method comprises the following step:
bracing the ballast with a turntable of the crane after ballasting has been effected.
Bracing can be carried out between the processes of retraction and/or extension or after completion of the retraction or extension of the ballasting cylinders. In the present case, ballasting can be regarded as the method of the invention for calculating the ballast weight.
The invention furthermore is directed to a crane with embodiments of the a apparatus described above.
FIG. 1a is a schematic representation of an apparatus for ballast weighing on a crane. There is shown a left ballasting cylinder 1 and a right ballasting cylinder 1′ for lifting a non-illustrated ballast 2. The ballasting cylinders 1, 1′ each comprise at least one pressure transducer 10, 10′, which each are arranged in the region of the piston and/or rod side of the ballasting cylinders 1, 1′. Further pressure transducers 11, 11′ can be provided on the piston side of the ballasting cylinders 1, 1′. Depending on whether there is a configuration with one pressure transducer or with two pressure transducers per ballasting cylinder 1, 1′, either the pressure difference between the two pressure transducers of a ballasting cylinder 1, 1′ or the absolute pressure measured on an individual pressure transducer can be determined or used in accordance with the invention.
The pressure transducers 10, 11; 10′, 11′ can be coupled with an evaluation unit 3. The evaluation unit 3 is equipped to calculate the mass moved by the ballasting cylinders 1, 1′ from pressures detected by at least two of the pressure transducers 10, 11; 10′, 11′ on retraction and/or extension of the ballasting cylinders 1, 1′.
The counterweight provides a moment acting against the crane load or the load lifted by the crane. Thus, the counterweight substantially contributes to the stability of the crane. A load moment limitation of the crane uses the magnitude of the effective counterweight (mass and effective lever arm) in the calculation of the stability of the crane and can prevent the crane from tipping over backwards or forwards at inadmissible crane positions. Tipping backwards can happen when the boom of the crane is set too steep for the effective ballast. So far, the crane operator has entered the data manually. To avoid incorrect entries here, there will be provided an apparatus that at least subjects the entries of the crane operator to a cross-check or plausibility check. In the best case, the device should be able to operate completely autarkically and render an entry by the crane operator superfluous.
In both ballasting cylinders 1, 1′ one pressure transducer 10, 11; 10′, 11′ each can be mounted on the ring and piston surface. By means of a pressure measurement in particular in the ring and/or piston space (on retraction and extension of the ballasting cylinders 1, 1′) the mass hanging on the ballasting cylinders 1, 1′ can be determined.
The pressure transducers 10, 11; 10′, 11′ can be mounted directly in the cylinder and need to be connected to the same via lines. The measurement accuracy thereby is increased, so that line losses and temperature errors can largely be avoided.
A temperature measurement and a correction of the pressure values with reference to the temperature values and taking account of a friction factor can likewise be provided.
FIG. 1B shows an embodiment of the invention in which at least one piston rod of the ballasting cylinders 1, 1′ is clamped in the ballast. The symbolically shown center of gravity of the ballast device thereby can be disposed away from the longitudinal axis of the piston rod by the amount a. When using two ballasting cylinders 1, 1′, the center of gravity of the ballast device can lie outside the plane defined by the longitudinal axes of the ballasting cylinders 1, 1′.
In the exemplary embodiment shown in FIG. 1B, the following applies for the retraction of the ballasting cylinder:me*g=PR*AR−PK*AK+F1*μ1+F2*μ2
For the case of extension the following applies:mag=PR*AR−PK*AK−F1*μ1−F2*μ2
Furthermore, it applies:m=(me+ma)/2; F1=F2 and μ1˜μ2; m*g*a=F1*b
wherein m is the weight of the ballast device and the further parameters can be taken from the Figure. Here, the parameters P represent pressure values, the parameters A represent corresponding surfaces of the ballasting cylinder, the parameters F represent forces, and the indices K and R relate to piston-side or ring-side parameters.
FIG. 2 shows the pressure profile in an exemplary embodiment of the invention, in which only one pressure sensor 10, 10′ or pressure transducer 10, 10′ is provided per ballasting cylinder 1, 1′. The pressure profile of the ring side correspondingly is shown by the pressure transducers 10, 10′. Due to asymmetries, the pressure on the left and right is of different magnitude. The diagram is divided into 5 sections. The section 90 shows the region "ballast at the bottom". Here, the ballast rests on the undercarriage. The section 102 shows the region "retract ballast". Here, the ballasting cylinders 1, 1′ are retracted and move the ballast to the top. The section 91 shows a region "standstill", in which ballast hangs on the ballasting cylinders 1, 1′ with its entire weight. The ballast touches neither an uppercarriage nor an undercarriage of the crane. In this region, the pressure measurement is effected by a simplified method for example at 55 seconds. The second section 102 again shows "retract ballast". The section 100 shows the region "ballast is at the top". Here, the ballasting cylinders 1, 1′ press the ballast against the uppercarriage of the crane.
In the following, calculation examples with only one pressure transducer 10, 10′ in each ring space now are indicated with reference to FIG. 2.
1. Measured Values (Measurement Values):
Pressure on ring surface to the right: 57.1 bar
Pressure on ring surface to the left: 51.1 bar
2. Force Calculation:
Force of cylinder to the right [N]:
Pressure on ring surface to the right * ring surface * 10
57.1 bar * 233.26 cm2* 10=133193.3N
Force of cylinder to the left [N]:
Pressure on ring surface to the left * ring surface * 10
51.1 bar * 233.26 cm2* 10=119197.5N
3. Total Force [kN]:
Force of cylinder to the left+force of cylinder to the right
(133193.3N+119197.5N)/1000=252.39 kN
4. Ballast Determination:
Determined mass [to]: total force/9.81
252.39 kN/9.81=25.72 to
5. Difference to Actual Ballast:
Actual ballast 26 to
Determined ballast: 25.72 to
Deviation: 280 kg
In this case it is possible to take account of the pressure in the ring space and the force thereby exerted on the piston. Of course, the above example is applicable analogously when merely one pressure transducer 11, 11′ each is present in the piston spaces of the ballasting cylinders. Depending on the alignment of the ballasting cylinders 1, 1′ relative to the crane, pressure transducers can be arranged in those work spaces of the ballasting cylinders 1, 1′ that are pressurized by the mass of the ballast.
To further increase the accuracy, a sequence of movements of the ballasting cylinders 1, 1′ can be effected automatically. The starting position is a condition in which the ballast to be mounted on the uppercarriage of the crane is stacked on the undercarriage in the mounting position, and the connecting means between ballasting cylinder 1, 1′ and ballast overlap each other to such an extent that the ballasting operation can be terminated by solely retracting the ballasting cylinders 1, 1′. The ballasting cylinders 1, 1′ carry out these movements as soon as the crane operator for example presses the key "lift ballast". The sequence of movements can continue on its own as long as the crane operator keeps the key pressed. An acoustic feedback can be provided.
Initially, the ballasting cylinders 1, 1′ are extended for example for half a second-piston or piston rod possibly are "stuck" the first time. Subsequently, the ballasting cylinders 1, 1′ are retracted and the ballast 2 is pulled up. There is a rise in pressure on the ring surface, until the ballast 2 is lifted from the undercarriage.
When the ballast 2 is lifted from the undercarriage, a constant pressure is obtained. Subsequently, the ballast 2 can be braced, the pressure in the ring surface rising in the process. Shortly before the ballasting operation is completed, the measurement sequence for ballast weighing is initiated.
In the process, the ballast 2 again is extended for a certain time. The ballast 2 hangs freely in the air and is held exclusively by the ballasting cylinders 1, 1′. On extension of the ballasting cylinders 1, 1′ the pressure in the ring and piston surface is measured, e.g. at 15000 ms, as can be taken from FIG. 3. From the measured pressures a differential force is calculated on extension of the ballasting cylinder.
Subsequently, the ballasting cylinders 1, 1′ are retracted again and the ballast 2 is lifted. Here as well, a pressure measurement is effected on retraction in the ring and piston space, e.g. at nearly 25000 ms. From the measured pressures a differential force is calculated on retraction of the ballasting cylinders 1, 1′.
From the differential forces, a mass that represents the attached ballast 2 is determined on retraction and extension.
In both ballasting cylinders 1, 1′ one pressure transducer 10, 11; 10′, 11′ each can be mounted on the ring and piston surface. By means of a pressure measurement in the ring and piston surface (on retraction and extension of the ballasting cylinders 1, 1′) the mass hanging on the ballasting cylinders 1, 1′ can be determined.
One more factor can be taken into account in order to again improve the determined result, similar to the luffing cylinder pressure measurement for the weighing operation. Furthermore, a temperature compensation can also be included in the calculation.
FIGS. 3A and 3B describe the method in which during the pressure measurement in the ballasting cylinders 1, on retraction of the ballasting cylinders 1, 1′ and subsequently on extension of the ballasting cylinders 1, 1′ an improvement can be achieved by deducting the friction in the measurement.
The sections shown in FIG. 3A correspond to the sections shown in FIG. 2. What is new in FIG. 3A is the section 101. Here, the ballasting cylinders 1, 1′ are extended and move the ballast away from the uppercarriage. The two curves 110 show the pressure profile on the ring side of the ballasting cylinders 1, 1′. They are tapped by the pressure transducers 10 and 10′. The two curves 111 show the pressure profile on the piston side of the ballasting cylinders 1, 1′. They are tapped by the pressure transducers 11 and 11′.
The sections shown in FIG. 3B correspond to the sections shown in FIG. 3A. FIG. 3B shows the "weighed ballast" stored in the control unit. At the beginning of the measurement an old value 112 for the "weighed ballast" is present. When the measurement cycle according to the invention starts, i.e. on transition from section 100 into section 101, the old value is cancelled. At nearly 25000 ms, the control unit has determined the new value 113 for the "weighed ballast" by means of the method according to the invention and has stored the same in the control unit. The control unit can of course be identical to the evaluation unit 3.
The force occurring on the ring surface on retraction of the ballasting cylinders 1, 1′ can be calculated as follows by way of example:
Force on ring surface of cylinder to the right [N]: pressure on ring surface to the right * ring surface * 10161.0 bar*40.25 cm2*10=64802.5N
Force on ring surface of cylinder to the left [N]: pressure on ring surface to the left * ring surface * 10161.7 bar *40.25 cm2*10=65084.25N
Total force on ring surface [kN]: force of cylinder to the left+force of cylinder to the right(64802.5N+65084N)/1000=129.89 kN
The force occurring on the piston surface on retraction of the ballasting cylinders 1, 1′ can be calculated as follows by way of example:
Force on piston surface of cylinder to the left/right [N]: pressure on piston surface to the left/right * ring surface * 1023.5 bar*103.87 cm2*10=24409.45N
Total force on piston surface [kN]: force of cylinder to the left+force of cylinder to the right(24409.45N+24409.45N)/1000=48.82 kN
The differential force on retraction of the ballasting cylinders 1, 1′ can be calculated as follows by way of example:
Total force [kN]: total force on ring surface [kN]—total force on piston surface [kN]:129.89 kN−48.82 kN=81.07 kN
The force on the ring surface on extension of the ballasting cylinders 1, 1′ (at 15 sec) can be calculated as follows by way of example:
Force on ring surface of cylinder to the right [N]: pressure on ring surface to the right * ring surface * 10235.0 bar*40.25 cm2*10=94587.5N
Force on ring surface of cylinder to the left [N]: pressure on ring surface to the left ring surface * 10235 bar*40.25 cm2*10=94587.5N
Total force on ring surface [kN]: force of cylinder to the left+force of cylinder to the right(94587.5N+94587.5N)/1000=189.17 kN
The force on the piston surface on extension of the ballasting cylinders 1, 1′ (at 15 sec) can be calculated as follows by way of example:
Force on piston surface of cylinder to the left/right [N]: pressure on piston surface to the left/right * ring surface * 1059.5 bar*103.87 cm2*10=61802.65N
Total force on piston surface [kN]: force of cylinder to the left+force of cylinder to the right(61802.65N+61802.65N)/1000=123.61 kN
The differential force on extension of the ballasting cylinders (at 15 sec) can be calculated as follows by way of example:
Total force [kN]: total force on ring surface [kN]—total force on piston surface [kN]:189.17 kN−123.61 kN=65.56 kN
Determined mass [t]: ((differential force on extension+differential force on retraction)/2)/9.81((81.07 kN+65.56 kN)/2)/9.81=7.47 to
Difference to actual ballast: actual ballast 7.36 to
determined ballast: 7.47 to
deviation: 110 kg
The practical procedure of ballasting can be as follows: Ballast rests on the undercarriage and the signal "ballast at the bottom" is available. The ballast weight calculated last is zeroed.
The operator activates the key "lift ballast" on an operating control unit or on an operating unit (key remains pressed). Initially, the ballasting cylinders are extended for a defined time period—cylinders possibly are "stuck" the first time. Subsequently, the ballast is retracted by the ballasting cylinders (ballast is pulled up). There is a rise in pressure on the ring surface, until the ballast is lifted from the undercarriage.
When the ballast 2 is lifted from the undercarriage, a constant pressure is obtained. Subsequently, the ballast is braced, and the pressure in the ring and piston surface rises. Shortly before the ballasting operation is completed, the measurement sequence for ballast weighing is initiated. In the process, the ballast is extended again for a certain time (ballast hangs freely in the air). On extension of the ballasting cylinder or the ballasting cylinders 1, 1′, the pressure in the ring and piston surface is measured. From the measured pressures a differential force is calculated on extension of the ballasting cylinder. Subsequently, the ballast is retracted again; here as well a pressure measurement is made on retraction. From the measured pressures a differential force is calculated on retraction of the ballasting cylinder. From the differential forces, a mass that represents the attached ballast is determined on retraction and extension.

Device and method for weighing a ballast on a crane and corresponding crane