A process for producing a resin-coated pigment capable of providing an ink and a paint being superior in dispersion stability of a pigment and having rapid drying property, high gloss and density without containing those such as an organic solvent and a salt that cause the lowering of performance of pigment dispersion, characterized in that a pigment is dispersed in an aqueous solution in which an anionic group-containing resin is dissolved in the presence of a basic compound and then, the anionic group-containing resin is precipitated on the surface of the pigment by removing the basic compound in the aqueous solution, using an ion exchange means.

As a colorant for various inks and paints, dyes are used in a field requiring higher level of sharpness and printing or coating property and on the other hand, pigments are used for a field requiring water resistance and light resistance, and in particular, the tendency is remarkable in the field of an ink for ink jet recording. A conventional ink jet recording system has been developed from the viewpoint that the maximum problem to be solved is how superior image sharpness and stable spouting property can be imparted to ink. However, the number of prevailed digital cameras has been greatly increased recently because of easy handling and high image quality and the target of ink jet recording extends to the field of silver salt photography. Accordingly, the impartation of light resistance is going to be a problem on par with the sharpness so that color is not faded nevertheless long preservation. Therefore, conventional dyes are going to be rapidly converted to pigments as the colorant of ink, but there remain many problems that must be solved when pigments are utilized.
For example, since a dye is dissolved in dispersion medium in molecular state, it affects little flowability and re-dissolving property dominating the spouting property of the ink even after elapsed time or a concentrated state and can keep high spouting stability. However, a pigment existing in particle state easily causes phenomena such as coagulation, sedimentation and solidification, and such phenomena lower flowability and re-dissolving property and as a result, the spouting stability is deteriorated. In particular, an organic pigment superior in sharpness must be dispersed as fine particles in aqueous medium in the ink jet recording system requiring high sharpness, whereby the area of hydrophobic surface is increased to inevitably cause coagulation.
For dispersing a pigment in an aqueous medium, methods for wetting the hydrophobic surface of the pigment using a dispersant and stably dispersing it in the aqueous medium are usually used. Among them, a method of adsorbing a surfactant or a polymer compound on the surface of a pigment is widely used. However, a strong adsorption force is required for keeping the dispersion state of the pigment and there are little dispersants exhibiting good pigment dispersibility for a long period. Further, since a large quantity of a dispersant is necessary for improving the dispersibility of a pigment by the method, the disengagement speed of the aqueous medium from the system becomes slow and when it is applied to the above-mentioned ink for ink jet recording, there are problems that the drying property of ink is lowered, the pigment is diffused in the inside of a printed article and printing density is also lowered.
Consequently, a method of coating the surface of a pigment with a film forming resin to obtain a resin-coated pigment is proposed as a method of improving the dispersion stability of the pigment and not causing the lowering of drying property and density of a printed article. For example, there are disclosed methods including a method of coating an anionic group-containing resin on the surface of a pigment by a phase transfer emulsification method (JP 10-046075 A and JP 10-140065 A) and a method of coating an anionic group-containing resin on the surface of a pigment by an acid precipitation method (JP 10-140065 A and JP 09-031360 A). In the phase transfer emulsification method, a dispersion in which a pigment is dispersed in an organic solvent solution of an anionic group-containing resin neutralized with a basic compound is prepared, the dispersion is mixed with a large quantity of an aqueous medium, and then, the organic solvent is removed if necessary, to obtain an aqueous pigment dispersion containing a resin-coated pigment. In the acid precipitation method, a pigment is dispersed in an aqueous solution in which an anionic group-containing resin has been dissolved in the presence of a basic compound, and then an acidic compound is added to adjust pH to neutral or acidic condition, thereby coating the surface of the pigment with the anionic group-containing resin to obtain a pigment cake, and then, the resin-coated pigment is dispersed again using a basic compound, to obtain an aqueous pigment dispersion with good dispersibility.
However, when the phase transfer emulsification method is used, the resin is really interacted with only an organic solvent in dispersing a pigment; therefore the expected effect of dispersing the pigment is not obtained. Further, since a large quantity of organic solvent remains in the system, storage stability is lowered and on the other hand, if excessive organic solvent is removed, there is a problem that it is not economically advantageous. When the acid precipitation method is used, the system contains the salt of acid and base which causes the lowering of various performances that are required for the ink for ink jet recording, and there is a problem that adequate washing is required for removing the salt.

Process for producing resin-coated pigment, resin-coated pigment, aqueous pigment dispersion and aqueous colorant composition containing the same


The receiver is provided which comprises a mixer, a low pass filter coupled to the mixer and a plurality of gain controllers serially coupled to an output of the low pass filter (LPF). A plurality of analog-to-digital converters (ADCs) is coupled so that an input of a first of the ADCs is coupled to the output of the LPF. An input of each of a remaining portion of the ADCs is individually coupled to a corresponding output of each of the serially coupled gain blocks. An output path traced from the output of the LPF to an output of each of the analog-to-digital converters may be referred to as a processing path. Each processing path may comprise a gain controller and an ADC, except for the first processing path, which may have an ADC coupled directly to the output of the LPF.

In packet-based wireless communication systems, a transmitted packet may be received with a large range of signal strengths, that is, a wide dynamic range. For example, in an 802.11 system, there may be as much as a 100 dB difference in signal strength between packets received at receiver A sent from transmitter B versus a packet received by receiver A sent from transmitter C. Factors accounting for this variation include path loss and fading characteristics of a RF propagation channel, for example. Path loss may include attenuation losses incurred due to the distance existing between a transmitter and a receiver. Fading characteristics of the RF propagation channel may include multipath interference destructively combining to reduce the strength of the signal received at the receiver. A well-designed communication transceiver must perform reliably given these impairments that are characteristic of wireless media. In this regard, a goal of a well-designed communication transceiver is to mitigate these characteristic impairments. In order to achieve this goal, a practical receiver may make use of automatic gain control (AGC). Automatic gain control can be described as an algorithm that may be adapted to automatically adjust signal size in order to maximize some parameter.
FIG. 1 is a block diagram of a conventional receiver system that utilizes gain control. Referring to FIG. 1, the conventional receiver comprises a mixer 102, a gain block 104, analog-to-digital converter (ADC) 106 and gain control block 108. The conventional receiver may be part of a packet-based wireless system, which is adapted to receive a signal that is transmitted at a particular carrier frequency.
In operation, the mixer 102 receives an input received signal and mixes the received signal with a tuning frequency to generate a baseband signal. The gain block 104 applies an initial gain Ginitial to the baseband signal, and the AGC algorithm will apply a final gain output gain Gfinal to the data portion of the packet. The analog to digital converter (ADC) 106 converts the analog signal to digital samples, which are subsequently processed.
A good AGC algorithm that may be implemented in the gain block 108, is adapted to choose or provide a final gain value Gfinal dB to apply to the data portion of the packet such that the signal to quantization noise ratio out of the ADC is maximized. Additionally, the final gain value Gfinal dB is chosen so that it is not too large as to cause an overflow to occur at the ADC during reception of the packet. The first criterion maximizes the signal to quantization noise ratio (SQNR) for the packet, and the second criterion prevents the packet from almost certainly being received with errors due to signal distortion. A well-designed gain block 108 is configured to execute an AGC algorithm that will accomplish this task.
Referring to FIG. 1, in L1 and L2 represents the limits of the ADC 106. In case 1, Gfinal is too small and the resulting analog signal, which is an input to the ADC 106, does not optimally utilize the limits L1 and L2 of the ADC 106. Accordingly, the AGC algorithm would have made a poor decision or choice. In case 2, Gfinal is too large and the resulting analog signal, which is an input to the ADC 106, does not optimally utilize the limits L1 and L2 since these limits of the ADC 106 are exceeded. Since the limits L1, L2 of the ADC are exceeded, clipping of the signal occurs. Accordingly, the AGC algorithm would have made a poor decision or choice. In case 3, Gfinal is ideal and the resulting analog signal, which is an input to the ADC 106, optimally utilizes the limits L1 and L2 of the ADC 106. In this case, no clipping of the analog signal occurs. Accordingly, the AGC algorithm would have made an ideal decision or choice.
For 802.11 orthogonal frequency division multiplexing (OFDM) systems, the gain Gfinal is calculated and applied during the preamble portion of the packet. The preamble of the packet is relatively short in time compared to the overall packet length, and corrections for other system impairments such as frequency offset may also need to be calculated during this portion of the transmission. Thus, the amount of time needed to determine the proper gain setting for the received packet needs to be kept small. For a practical 802.11a/g orthogonal frequency division multiplexing system, this means it is likely at most one intermediate gain setting Gintermediate is allowed during the preamble to determine the final gain Gfinal.
FIG. 2 is a diagram illustrating the application of gain to a packet. Referring to FIG. 2, there is shown a packet 200 having a preamble portion 202 and a data portion 204. The leftmost portion of the packet 200 is the demarcation of the start of packet (SOP) and the rightmost portion of the packet 200 is the demarcation of the end-of-packet EOP. The gain Gfinal is applied at reference A, which occurs during the preamble portion 202 of the packet 200. In this case, Gfinal is greater than Ginitial (Gfinal>Ginitial).
FIG. 3 is a diagram illustrating the application of gain to a packet. Referring to FIG. 3, there is shown a packet 300 having a preamble portion 302 and a data portion 304. The leftmost portion of the packet 300 is the demarcation of the start of packet (SOP) and the rightmost portion of the packet 300 is the demarcation of the end-of-packet EOP. A gain Ginitial is in effect at the start-of-packet (SOP) where clipping is occurring. A gain Gintermediate is applied at reference B where no clipping occurs but the signal is too small. A gain Gfinal is applied at reference C where no clipping occurs and the signal is ideal. In this case, Ginitial, Gintermediate and Gfinal are applied during the preamble.
In order for a receiver to detect small receiver signal input, the initial front-end gain Ginitial must necessarily be set to a large value. However, if the incoming signal is in fact large, the signal level at the output of the ADC will be clipped, making it difficult to determine the received signal power. That is, if a received signal power of X dBm is enough to cause a clip at the ADC, then all received signal powers greater than X dBm also cause a clip.
Further limitations and disadvantages of conventional and traditional approaches will become apparent to one of skill in the art, through comparison of such systems with some aspects of the present invention as set forth in the remainder of the present application with reference to the drawings.

Method and system for improving dynamic range for communication systems using upstream analog information


An exchangeable plate is suspended on a top plate and held in a lower end position without force by a hydraulic clamps. In an upper end position, it is connected with force fit to, and re-detached from, the top plate as a function of a stripping operation of a scrap web from a V-ring pressure plate. The exchangeable plate is transferred from the lower into the upper end position by movement of a ram, and transferred from the upper into the lower end position by gravity. A sensing distance, adapted to the brake path of the drive system, is provided between the top plate and the exchangeable plate. A sensing device in the V-ring pressure plate outputs a signal to the computer for stopping the drive system and deactivating the hydraulic system. A. sensor detects premature movement of a pressure plate in the exchangeable plate.

The invention relates to a device and a method for preventing a tool from breaking during fine blanking and/or forming in a press. A device for protecting a tool set of a hydraulic fine blanking press is known from DE 24 19 390 C2, in which a ram of a press can be lifted using quick-action cylinder-piston units and a working stroke pressure unit. A sensing gap exists in the press between the ram driving element and a driven ram part. The sensing gap is maintained when a pressure means approaches. The gap closes when a higher pressure load is applied to the parts forming the gap. The state of the sensing gap is monitored with a feeler and with a limit switch until the ram has caused the tools to approach each other to an extent where a proper start of the working stroke is reached. The sensing gap is formed between the ram and the end faces of the piston rods of the quick-action pistons. A pressure means is applied to the sensing gap in sensing cylinders in the ram. The sensing pistons in each case are seated against a partial surface of these end faces.
In this known protective device, the sensing gap in front of the quick-action cylinder-piston unit is associated with the ram and is connected upstream of the ram. This protective device is activated when the sensing gap closes due to an increased pressure load.
It has the disadvantage that stamping scrap, parts or foreign objects in the tool cannot be detected, and consequently damage to the tool cannot be prevented.
DE 69 17 177 U discloses another solution for protecting tools on presses for processing a blank. Two switches, between a first tool moved by the main piston and a second tool that is rigid with the press frame, are actuated in a predetermined sequence so as to interrupt the working stroke when the actuating sequence is reversed. An element is provided, which is used to attach the first tool and can be axially displaced in relation to the main piston. The element is held a small distance in front of the main piston by an elastically yielding means during the working stroke. A first limit switch, which can be set to the target height of the blank to be processed, is actuated by a stop when the piston has traveled a portion of the working stroke thereof that is predetermined by the setting of the first limit switch. A second limit switch is actuated by a further stop when the element has been pushed back by the small distance onto the piston due to impingement of the blank or a foreign object on the second tool.
The element is designed as a lower tool clamping table, which rests on a cylinder. The cylinder together with the main piston, encloses an annular pressure chamber connected to a pressure means line. A blocking means is located in the course of the pressure means line which allows sufficient compressed air to be admitted into the annular chamber, so that the table is practically located in a floating position in front of the piston during the working stroke.
This known solution has the drawback that, in addition to the hydraulic system, a second separate system is required, which operates with compressed air. It thus entails considerable switching and design complexity. In addition, after a foreign object has been detected, there is no option to dissipate the kinetic energy of the drive system.
The prior art from which the present invention proceeds is described in EP 2 258 496 A1, which relates to a device and to a method for preventing a tool, composed of an upper part and a lower part, from breaking during fine blanking and/or forming in a press. The known device comprises a main cylinder, which is disposed in the tine blanking head and in which a V-ring piston located on the stroke axis and multiple V-ring pins disposed coaxially to the stroke axis are accommodated. The V-ring pins are axially guided in a main plate closing the main cylinder and are supported on a V-ring pressure plate. The main cylinder is held in the head piece of the press and is closed in a pressure-tight manner by a V-ring cover. The fine blanking head is connected to a hydraulic system for generating pressures acting on the tool by way of valves that can be actuated by a computer.
A sensing piston is provided between the V-ring piston and the V-ring pin. The piston forms an axially displaceable structure together with the V-ring piston on the one hand, and together with the V-ring pin and the V-ring pressure plate on the other hand. The V-ring piston is associated with a pressure chamber that can be acted on by a preload pressure of the hydraulic system and with a pressure chamber that can be acted on by a sensing piston pressure between the V-ring piston and the sensing piston. The sensing piston is associated with a further pressure chamber that can be acted on by a pressure differential. The pressure chambers in each ease are connected via a connection in the V-ring cover to the hydraulic system for acting on the V-ring piston and the sensing piston counter to the operative direction of the preload pressure.
Moreover, a sensing table is provided, which is held in a suspended and weight-compensated manner at a defined sensing distance by the main plate counter to a clamping means engaging on the main plate. A sensor is associated with the sensing distance, which forwards a signal to the computer to immediately stop the press so as to protect the upper tool part when the sensing distance changes.
This known prior art has the drawback that the sensing table represents an additional component, which results in an increase of the mass to be moved, and thus in reduced sensitivity of the sensing device. By arranging the sensing table below the main plate, moreover the distance of the measuring point for ascertaining stamping scrap, parts that were left behind or faulty adjustments in the tool installation height from top dead center is increased. The result is a higher ram speed, which reduces the sensitivity of the sensing process.

Device and method for preventing a tool from breaking when fine blanking and/or forming a workpiece


The present invention relates to router fixture having a base with a base aperture and a pair of slidably adjustable horizontal guides. The router fixture is designed to receive a precut template which defines the area of movement for a router used on the router fixture. The template fits into the guides and defines the area of separation between the guides and also provides an indication as to the area of a workpiece which is to be cut out on the workpiece.

Power hand held routers have become a common and useful woodworking tool for working edges, making grooves of different shapes and sizes, cutting dadoes, and making rabbit cuts. However, the router can be a difficult tool to use skillfully without a guiding device. Although prior art router jigs have attempted to provide such guiding devices, these prior art router jigs have proved to be cumbersome to use, difficult to set up, and limited in application to specific routers and specifically shaped workpieces.
Two examples of prior art router jigs are illustrated in U.S. Pat. No. 2,957,507 to John Vargo and U.S. Pat. No. 3,967,665 to Allan M. Lund. Both of these patents describe router jigs which provide a means for guiding a router. However, both these structures require awkward and time consuming alignment and set up procedures.
U.S. Pat. No. 3,967,665 to Lund describes a routing template assembly having an adjustable elongated slot which defines the area to be cut on a workpiece by a router bit having a guide bushing. As described in the patent, the procedure for adjusting the elongated slot to the desired width requires several time consuming steps which includes the measurement of the radius of a guide bushing used to guide the router and the measurement of a piece of material which defines the width of the slot to be cut on the workpiece. Each of these measurements requires the relevant adjustment of several parts of the jig and the tightening of several screws.
The structure described in U.S. Pat. No. 2,957,507 to Vargo is a routing jig which provides a fixed rectangular frame which contains the body of the router within a specified area. By containing the body of the router, the frame defines the boundaries of movement for the router and thus defines the area cut on the workpiece. However, the width of the Vargo horizontal guide structures is not adjustable and the initial alignment of this structure is awkward and time consuming. The Vargo device also fails to provide an easy and simple method for aligning the device with respect to the area that is to be cut and also fails to provide the versatility of application with respect to different brands of routers which may have different size bases.


A method which enables easy removal of a magnetic head slider soldered to a suspension and easy reuse of the removed parts. In the method for removing the magnetic head slider, heat is applied to a suspension to which at least a part of the magnetic head slider is joined by solder so as to remove the magnetic head slider from the suspension. The heating is locally applied to the junction area of the magnetic head slider and the suspension, which is joined by the solder.

1. Field of the Invention
The present invention relates to a method and an apparatus for removing a magnetic head slider and, more specifically, to a method and an apparatus for removing a magnetic head slider from a suspension in a head gimbal assembly which is judged as being a defective product in an assembling process thereof.
2. Description of the Related Art
As high-speed, highly reliable, and low-cost recording devices, hard disk drives (HDD) are widely used for reading/writing digital data. With an HDD, reading/writing of data to/from a magnetic disk is carried out by using a thin film magnetic head. This magnetic head comprises a suspension and a magnetic head slider. This magnetic head slider comprises an electromagnetic conversion element which carries out reading/writing of data. The suspension holds the magnetic head slider through fixing it by adhesive or solder to a gimbal spring part of a flexure which constitutes the suspension.
When manufacturing the magnetic head, an inspection for checking a reading/writing property of the magnetic head can be performed only after the magnetic head slider and the suspension are assembled. Thus, defective products are found after the assembling. The defective rate thereof is extremely higher than the defective rate found in the suspension alone so that a strict inspection is required after the assembling. With this, it eliminates a risk of having the detected defective products remained in shipping products so as to improve the quality.
However, if the above-mentioned defective product as a whole is to be dumped, the suspension is also dumped along therewith even though, for example, there is only reading/writing malfunction generated in the electromagnetic conversion element of the magnetic head slider. Since the suspension is usually more costly than the slider, the cost for manufacturing the magnetic head becomes strikingly increased. On the other hand, in the case where the magnetic head slider can be reutilized even though the suspension is defective, there causes a waste of parts as in the above-described case. Thus, the manufacturing cost is increased.
Therefore, in order to achieve a reduction in the manufacturing cost of the magnetic head, it is desired to carry out an inspection for checking the reading/writing property after assembling the suspension and the slider once, then, if there is a defective product found, the suspension and the magnetic head slider are separated so as to reutilize the fine magnetic head slider or suspension.
For satisfying the demand as described above, Japanese Patent Unexamined Publication No. 2002-150734 discloses a technique for removing a magnetic head slider from a suspension. The technique disclosed in JP-A 2002-150734 is to remove an assembled magnetic head slider, which is joined by an adhesive resin to a flexure that constitutes a suspension, by controlling a cure state of the adhesive resin through temperatures.
In the meantime, in a head gimbal assembly, solder is used for connecting a connection pad of the magnetic head slider and a lead trace formed on the flexure. Also, there may be cases where the magnetic head slider is fixed to the flexure as the suspension by solder. In that case, it is not possible to deal with the solder fixation by using the technique for removing the magnetic head slider, which is disclosed in JP-A 2002-150734. In the case where, as described above, the magnetic head slider is removed form the flexure in the head gimbal assembly in which parts are joined by the solder, it is necessary to melt the solder by applying heat. As described above, conventionally, a method which is to heat the entire magnetic head up to a melting point of the solder has been employed.
However, with the above-described method, the temperature of the entire magnetic head may be increased as high as the melting pint of the solder or more thus damaging the electromagnetic conversion element of the magnetic head slider. That is, there is a risk of breaking the electromagnetic conversion element since the general melting point of the solder is at about 230° C., while the critical temperature of a reading element (MR element) is at about 250° C. When that happens, it cannot be reutilized even though there is no defect in the suspension, which results in wasting the parts. Further, the suspension is also heated entirely so that the rigidity of the suspension may be affected by the heat.
Furthermore, the above-described method simply removes the magnetic head slider by melting the solder. Thus, there may be the solder remained attached to the magnetic head slider or the suspension. In that case, before reutilizing the magnetic head slider or the suspension, it is necessary to carry out processing for removing the attached solder. Therefore, there may cause a problem that manufacturing procedures are increased and the time and cost thereof are increased as well.

Method for removing a magnetic head slider


A fuel cell system is provided, including an HFR measurement device in electrical communication with a fuel cell stack. The HFR measurement is used online to measure an HFR of the fuel cell stack suitable for calculation of a d(HFR)/d(RH) ratio. A humidity regulator is provided in fluid communication with the fuel cell stack. A controller periodically changes stack operating conditions to perturb an RH of the fuel cell stack, process the HFR response, and compute the d(HFR)/d(RH) ratio. A method for online identification and control of the fuel cell stack humidification is also provided. The d(HFR)/d(RH) ratio is an auxiliary measurement of membrane hydration which is used as a feedback for hydration control.

A fuel cell has been proposed as a clean, efficient, and environmentally responsible energy source for electric vehicles and various other applications. In particular, the fuel cell has been identified as a potential alternative for the traditional internal-combustion engine used in modern vehicles. One type of fuel cell is known as a proton exchange membrane (PEM) fuel cell. Individual fuel cells can be stacked together in series to form a fuel cell stack. The fuel cell stack is capable of supplying a quantity of electricity sufficient to provide power to a vehicle.
As is well understood in the art, the membranes within the fuel cell stack must have a certain relative humidity (RH) for efficient performance. Measures are often taken to maintain the membrane hydration within a desired range that optimizes proton conduction across the membranes. For example, in U.S. Pat. No. 6,376,111, hereby incorporated herein by reference in its entirety, a controller utilizes feedback to control the humidity of a fuel cell assembly. Humidifiers or water vapor transfer (WVT) devices are commonly used to humidify inlet reactant gases provided to the fuel cell stack. Thermal control strategies based on a relationship between RH and fuel cell temperature, as measured by the coolant temperature, for example, have also been employed in controlling membrane hydration. Other fuel cell parameters, such as stoichiometry and pressure, are further known to affect fuel cell humidification.
The level of humidification in fuel cell systems of the art has been controlled in response to a variety of feedback indicators including inlet RH, outlet RH, temperature, pressure, flow rate, and electrical current measurements. However, typical sensors employed in measuring these indicators often exhibit drift and may be unreliable. Relative humidity sensors, in particular, are known to have limited use in fuel cell applications due to corrosion and swelling of the sensors with repeated exposure to liquid water. Thus, typical sensors have not been desirably effective for purposes of humidification feedback-control in fuel cell systems.
High frequency resistance (HFR) has previously been used as an offline lab diagnostic technique for indirectly measuring MEA hydration in the fuel cell. Typical HFR sensors measure an AC resistance of the fuel cell based on a high-frequency ripple current. HFR is particularly sensitive to changes in RH. However, HFR is also highly sensitive to other fuel cell conditions, such as individual differences in overall membrane resistance, plate resistance, and contact resistance. Absolute HFR measurements are particularly susceptible to variation in contact resistance. Since the contact resistance of a fuel cell stack varies during operation with changes in compression force, due in part to swelling and contracting of membranes, absolute HFR measurements have heretofore not been employable in online hydration measurements of operating fuel cell stacks.
There is a continuing need for an online system and method for reliably measuring humidification of the fuel cell stack in operation. Desirably, the online system and method employs HFR measurements for monitoring and feedback control of fuel cell stack humidification.

On-line system identification and control of fuel cell humidification via HFR measurements


The present invention is directed to a method of manufacturing an electrical box to reduce the amount of scrap material therefrom. More particularly, the present invention provides a metallic electrical outlet box that is formed from a sheet of material and folded into an electrical box.

Electrical boxes are constructed in a variety of ways for housing electrical wiring devices such as electrical receptacles or outlets, switches, etc. Electrical boxes can be constructed of either metal or plastic depending upon the desired application for the electrical box.
Many electrical outlet boxes are formed of metal. These metallic outlet boxes typically include a back wall, perimetrical side walls and an open-front face defining a box interior through which a switch or receptacle is placed. The boxes are typically constructed from multiple walls which are assembled together.
One common technique for forming boxes is to fold a stamped planar sheet of metal into a box configuration. In one folding technique a U-shaped configuration is formed as to define the top, bottom and back walls. Side walls may be attached to the U-shaped member to form the box. Other folded box techniques include cutting the sheet metal into a cross-shape where side walls of the box extend from each edge of the back wall. Each side wall is bent perpendicular to the back wall and the edges of the side walls are connected to each other by tack welding, for example.
In either technique, material around the folded portions is disposed of as scrap. The large amount of scrap metal increases the cost of manufacturing of the box.
It is therefore desirable to produce a more efficient way to manufacture a box with the least amount of scrap material produced therefrom.

Method for manufacturing electrical boxes


In one embodiment, a method of manufacturing a semiconductor device includes forming, on a semiconductor substrate, a sacrificial semiconductor pillar having a pillar-like shape extending in a first direction perpendicular to a main surface of the semiconductor substrate, and being formed of a first semiconductor material. The method further includes forming, around the sacrificial semiconductor pillar, a channel semiconductor layer having a tube-like shape extending in the first direction, and being formed of a second semiconductor material different from the first semiconductor material. The method further includes removing the sacrificial semiconductor pillar after the channel semiconductor layer is formed. The channel semiconductor layer is formed on electrode layers via an insulator, the electrode layers being formed on the semiconductor substrate.

In general, a cell transistor of a conventional semiconductor memory device includes its channel in a semiconductor substrate. On the other hand, it has been recently considered to propose a cell transistor including its channel in a semiconductor layer formed on a semiconductor substrate. For example, a cell transistor of a bit cost scalable (BICS) flash memory includes its channel in a semiconductor layer which has a tube-like shape extending in the vertical direction.

Semiconductor device and method of manufacturing same


A method of calculating coordinate data of a desired point in a subject to be examined is disclosed. A phantom image is obtained by integrally photographing a second frame, a frame coordinate phantom, and a second indicator phantom by using a computed tomographic apparatus. A subject image is then obtained by integrally photographing a first frame, the subject, and a first indicator phantom at the same position assumed when the phantom image is photographed. Coordinate data is obtained by correcting the deviation between the coordinates of the subject on the real space and the coordinates of the subject on the image photographed by the computed tomographic apparatus.

1. Field of the Invention
The present invention relates to an apparatus for calculating coordinate data of a desired point in a subject to be examined which is required when stereotaxy (stereotactic surgery) or the like is to be performed by using a computed tomographic apparatus such as an MRI apparatus (Magnetic Resonance Imaging Apparatus), and a method of calculating coordinate data of a desired point in a subject to be examined by using the same.
2. Description of the Related Art
Coordinate data of a desired point in a subject to be examined is used, for example, for stereotaxy surgery as one of operations of neurosurgeon. In stereotaxy, the position of a morbid portion in the brain of a patient is identified with the aid of an image, and an operation is performed, e.g., inserting a biopsy cannula in the identified portion so as to remove the morbid portion. As the image, an X-ray image (Roentgen image) obtained by an X-ray diagnosing apparatus has been used. Recently, however, CT stereotaxy using an X-ray CT apparatus as a computed tomographic apparatus and MRI stereotaxy using an MRI apparatus as a computed tomographic apparatus have been performed.
MRI stereotaxy is conventionally realized by the coordinate calculation step of calculating the coordinate value of a morbid portion in a subject to be examined, and the step of operating a stereotactic apparatus on the basis of the calculated coordinate value, i.e., the operation step. FIG. 1 shows an apparatus used in the coordinate calculation step and a subject to be examined. FIG. 2 shows an apparatus used in the operation step, i.e., a stereotactic apparatus and the subject.
As shown in FIG. 1, in the apparatus used in the coordinate calculation step, a head portion 40A of a subject 40 to be examined is held in an annular frame 20. In this case, an indicator phantom 21 is mounted on the frame 20 in order to indicate X-, Y-, and Z-coordinates. The frame 20 is placed at a predetermined position in a photographable region of a computed tomographic apparatus (not shown) while the head portion 40A is held by the frame 20, and a photographing operation is performed to obtain, e.g., an axial plane image. By observing this image, the position of the morbid portion appearing on the image is recognized and identified with X-, Y-, and Z-coordinates by referring to the indicator phantom 21. The indicator phantom 21 is detached from the frame 20, and a stereotactic apparatus 22 is mounted. Thereafter, for example, a biopsy cannula 22A of the apparatus 22 is pierced into the head portion 40A to reach the position coordinates of the morbid portion obtained in the above described step as a target, and the morbid portion is removed.
In the execution of the above-described stereotaxy, since a surgical operation is to be performed for a brain, high positional precision is required in identification of a morbid portion.
In an MRI apparatus, however, because of the characteristics of static and gradient fields, field distortion is abruptly increased with an increase in distance from the field center, and following this field distortion, image distortion is abruptly increased. Example, image distortion corresponding to 5 mm may be caused at a position near the frame, thus posing a problem in execution of stereotaxy requiring high positional precision.

Apparatus for calculating coordinate data of desired point in subject to be examined


A decorative article that is attached to a nursing bra strap as an indicator of which breast an infant last fed from or will feed from next. The decorative article is suspended pendant like from a parrot clasp and is moved from a strap fastener on one nursing bra strap to the other as a nursing breast system indicator.

1. Field of the Invention
The present invention relates generally to indicators and, more specifically, to a decorative article that can be attached to a nursing bra strap as an indicator of which breast the infant last feed from or will feed from next. In either case, the decorative article can be moved from one nursing bra strap to the other as a nursing breast system indicator. Shown in the prior art, breast nursing system indicators are apparatus that are included as an integral part of the nursing bra. Also known in the prior art are systems as simple as using a safety pin selectively attached to the strap or cup as a breast feeding system indicator. Both of these methods are utilitarian in nature and do not disclose the use of a nursing breast indicator as a piece of jewelry or similar article that is desirous of public display. Furthermore, the instant invention's indicator can be treasured as an heirloom or placed on any bra strap or undergarment as an item of jewelry, as well as, a bikini thong.
2. Description of the Prior Art
There are other indicator devices designed for nursing bras. Shown in the prior art are breast nursing system indicators comprising apparatus that are included as an integral part of the nursing bra. Also known in the prior art are systems using a safety pin attached to the strap or cup as a breast feeding system indicator.
While these indicators may be suitable for the purposes for which they were designed, they would not be as suitable for the purposes of the present invention, as hereinafter described. Therefore it is felt that a need exists for a nursing bra breast feed indicator comprising releasably fastenable strap fasteners incorporating a releasably attachable decorative element that can be moved from one strap to the other as desired.


Provided is a temperature controller for an industrial heating apparatus adjusting a soak time on the basis of the variation of the thermal energy. Accordingly, since a temperature equilibrium time point of the center is determined by reflecting a temperature tolerance in the chamber and a soak time is corrected and since the temperature equalization time point is set on the basis of a full load state in which the variation of the input thermal energy per time is the smallest, the temperature at the center falls within an allowable upper/lower limit range even if a partial load state is applied, whereby the temperature control apparatus and method for an industrial heater applicable regardless of the amount of heating targets may be provided.

A heat treatment process using various industrial furnaces, surface treatment equipment, food processing equipment, and cooking equipment (hereinafter, referred to as "heating apparatus") includes a combination of a ramp stage to heat (temperature increasing) or cool (temperature decreasing) the chamber to be heated to a predetermined temperature and a soak stage to maintain for a certain time at the predetermined temperature. Control technologies of various heating apparatuses commercialized in modern times have significantly advanced and the degree of controlling temperatures is excellent.
However, in an industrial heating system, a heater, which is a heating element, is installed at the outer side due to restrictions of space in the chamber, and thus, the center of the chamber takes more time to reach the predetermined temperature than the periphery.
In addition, in a case where the chamber is partially loaded as necessary, for example, when only 300 kg or 500 kg with respect to 1 ton capacity is loaded, setting a soak time with respect to 1 ton may involve a waste of time and increase energy and an exhaust gas.
Here, the soak time, in other words, a time for which an indication value of a control temperature sensor reaches a set value and the chamber is maintained at the temperature, refers to the sum of a temperature equalization time required for the center or the like, to which heat is transferred the most late, to reach the set temperature and an additional time for a reaction after the temperature equalization as necessary. Here, since the temperature equalization time (time point) which is varied according to the amount of the load (heating target) cannot be conveniently measured in real time, an excessive time is typically set with respect to a normal capacity of a heating apparatus, resulting in waste at the soak stage.
In order to solve this problem, a technology for measuring a thermal equilibrium time and reducing the soak time by monitoring a thermal energy supply amount according to temperatures detected at the center was developed.
In this regard, in Korean Patent Registration No. 10-0931783 (Title of invention: Heating apparatus having a function of measuring time required for temperature equalization and a control method thereof) discloses a heating apparatus having a temperature equalization time point measuring function which determines a required temperature equalization time by input energy, enabling accurately determining the required temperature equalization time point regardless of charging conditions, thereby preventing a waste of energy, shortening a heating time to improve productivity, and preventing some parts of the load(heating targets) from being heated for a longer period of time than necessary.
However, in the actual process, a temperature difference of an upper and lower limit range compared to a set temperature is allowed, and in the case of a steel heating furnace allowing a large temperature difference between the periphery and the center, a temperature at the center may need to reach a lower specification limit, and thus, if a soak time is determined as a time required for reaching a thermal equilibrium state, i.e., a perfect temperature equalization, the soak time may be longer than a soak time of an existing process. Therefore, in order to more efficiently shorten the soak time in the heating process, calculation of a variation (the amount of change) of thermal energy applied per unit time at the lower specification limit is required during a soak operation after the temperature rises (ramp-up) for determining a temperature equalization time point reflecting the temperature tolerance, or calculation of a variation of thermal energy applied per unit time at an upper specification limit is required at a soak operation after the temperature falls (ramp-down). Further, a technique for automatically diagnosing when a heater, heat insulation of a heating chamber, or a temperature sensor is abnormal is required.

Temperature control apparatus and method for the industrial heater having auto-correction of soak time and self-diagnosis of abnormal heating function


A method to provide a dopant profile adjustment solution in plasma doping systems for meeting both concentration and junction depth requirements. Bias ramping and bias ramp rate adjusting may be performed to achieve a desired dopant profile so that surface peak dopant profiles and retrograde dopant profiles are realized. The method may include an amorphization step in one embodiment.

Plasma doping systems are known and used for forming shallow junctions in semiconductor wafers and for other applications requiring high current with relatively low energy ions. In plasma doping systems, a semiconductor wafer is placed on a conductive platen, which functions as a cathode and is located in a plasma doping chamber. An ionizable doping gas is introduced into the chamber, and a voltage pulse is applied between the platen and an anode or the chamber walls, causing formation of a plasma containing ions of the dopant gas. The plasma has a plasma sheath in the vicinity of the wafer. The applied pulse causes ions in the plasma to be accelerated across the plasma sheath and to be implanted into the wafer. The depth of implantation is related to the voltage applied between the wafer and the anode. Very low implant energies can be achieved. Examples of such plasma doping systems are described in U.S. Pat. No. 5,354,381 to Sheng, U.S. Pat. No. 6,020,592 to Liebert et al., and U.S. Pat. No. 6,182,604 to Goeckner. In the above described plasma doping systems, the applied voltage pulse generates a plasma and accelerates positive ions from the plasma toward the wafer. In other types of plasma systems, a continuous plasma is produced, for example, by inductively-coupled RF power from an antenna located internal or external to the plasma doping chamber. The antenna is connected to an RF power supply. At intervals, voltage pulses are applied between the platen and the anode, causing ions in the plasma to be accelerated toward the wafer.
Dopant gas species used for plasma implantation may decompose or dissociate during the implant process into atomic or molecular fragments which may be deposited on the surface of the wafer. Atomic or molecular fragments that result from dissociation of dopant gas molecules are referred to herein as "neutral particles." Examples of dopant gas species which dissociate during the implant process include AsH3, PH3, BF3, and B2H6. For example, arsine gas AsH3 may dissociate into As, AsH and AsH2, which may be deposited on the surface of the wafer being implanted. These deposited surface layers can cause a number of problems, including dose non-repeatability, poor dose uniformity and dose measurement problems. In particular, the neutral particles that form the deposited surface layers are not measured by the dose measurement system. Further, the depth profile of the dopant is altered by the deposited surface layer itself and by its effect on implanted ions. In addition, the deposited surface layers can cause contamination of other equipment, such as annealers, when the wafers are subsequently processed in such equipment.
Accordingly, there is a need for providing a profile adjustment solution in plasma doping applications to meet both concentration and junction depth requirements.

Profile adjustment in plasma ion implanter

Varian Semiconductor Equipment Associates, Inc.


The present invention provides a liquid surface detection device 1 in which corrosion is restrained even when liquid having conductivity is used so that a longer lifespan is achieved, including a liquid surface detection sensor 2 that outputs a signal indicating a variation in liquid level as a variation in resistance value by the sliding movement of a contact point 2a on an electrode connected to a resistor 2b, and a control unit 4 that controls supply and stops a supply of electric power to the liquid surface detection sensor 2 at predetermined intervals, in which a vehicle state determination unit that determines a state of a vehicle is provided and the control unit 4 controls the duration to stop the supply of electric power to the liquid surface detection sensor 2 when the vehicle state determination unit determines that the vehicle is in a traveling state.

Liquid surface detection devices in the related art include a float arm provided with a float which floats on the liquid surface, a frame for rotatably supporting the float arm, a resistor provided on a substrate which is fixed to the frame, and a contact point which slides on electrodes connected to the resistor in association with the float arm, and detect the position of the liquid surface by detecting electric resistance between the ends of the contact point and the resistor (for example, see Patent Document 1)    Patent Document 1: JP 2004-20538 A


This invention relates to an oil-in-water-in-oil (O/W/O) type multiple emulsion which contains an inner oil phase, a water phase, and an outer oil phase. The inner oil phase is first dispersed in water to form an oil-in-water (O/W) emulsion. Then, the O/W emulsion is further dispersed in the outer oil phase to form the O/W/O type multiple emulsion. The outer oil phase contains an organophilic clay mineral, which can effectively prevent the inter-mixing of the inner oil phase with the outer oil phase, thus, producing an O/W/O type multiple emulsion with excellent storage stability. Upon the using of an oil-soluble compound in the inner oil phase, this multiple emulsion system can prevent the oil-soluble compound from being oxidized. In addition, since different kinds of oils can be selected for the making of the inner and outer oil phases, respectively, the O/W/O type multiple emulsion system allows one to present two different kinds of oils, which have different properties independent from each other, in one emulsion system.

Oil-in-water-in-oil type (referred to as "O/W/O type" in the following) emulsion composition in which an oil-in-water type (referred to as "O/W type" in the following) emulsion is further emulsified and dispersed in an oil phase, also known as complex emulsion or multiple emulsion, have become important in various industrial uses such as cosmetics, food products, and medicines. Namely, while normal W/O type emulsions have a configuration in which a water phase is simply dispersed in an oil phase, the particle structure of multiple emulsions is such that, as shown in FIG. 1, an inner oil phase 14 is further dispersed in a water phase 12 which has been dispersed in an outer oil phase 10. Accordingly, they are expected to yield special feel of use and effects which cannot be obtained by simple O/W type and W/O type emulsions.
For example, since the inner oil phase 14 is blocked from the external atmosphere by the water phase 12 and the outer oil phase 10, when an oil-soluble material which is easily oxidized is contained in the inner oil phase 14, its stability against oxidization is expected to be improved as compared with the cases where it is contained in the oil phase of O/W type or W/O type emulsions.
Also, in recent years, silicone type bases such as dimethylpolysiloxane have been widely used as a base for external preparations for skin or cosmetic preparations due to their favorable usabilities such as good spreadability, refreshness, and lack of greasiness, as well as their excellent water resistance and oil resistance which make them resistant to being washed out by sweat and water. In particular, in suncare cosmetics, since they are universally used in summer, refreshing feel of use and those not easily washed out by sweat, sebum, or water are required, whereby such silicone bases are being used more frequently.
Of the oil-soluble agents usually added in cosmetic preparations and external preparations for skin, those hard to dissolve in silicone type oils are not a few, however. For example, of the oil-soluble ultraviolet absorbers added in suncare cosmetic preparations, there are many which have a remarkably low solubility to silicone type bases. Accordingly, in cosmetic preparations containing a large amount of a silicone type base, there has been a problem that, when such an ultraviolet absorber is added therein, crystals of the ultraviolet absorber may deposit over time.
In order to prevent crystals from depositing, it has been necessary to restrict the using amount of oil-soluble agents which are hard to dissolve in silicone type oils or concurrently use a large amount of oils such as polar oils to which the agents have a high solubility. Effect of the agent, however, usually depend on its amount added and cannot be sufficiently obtained when the using amount is restricted. Also, when non-silicone type oils such as polar oils are used in a large amount, the amount of silicone type oils is restricted in emulsion compositions, for example, due to problems in terms of formulation, whereby there are cases in which a large amount of silicone type oils cannot be added to make it difficult to yield satisfactory feel of use and resistance to both water and oil.
Further, since silicone type oils are totally different from the other polar and nonpolar oils in terms of structure and property, when non-silicone type oils added in an oil phase of an emulsion such as W/O or O/W together with a silicone type oil, it is difficult to select an emulsifier, emulsification conditions, and the like, thereby making it quite difficult, in general, to obtain an emulsion having a favorable emulsion stability.
These problems are considered to be solved by application of O/W/O type multiple emulsion. Namely, in an O/W/O type multiple emulsion, since an inner oil phase 14 and an outer oil phase 10 are separated from each other by a water phase 12, it is theoretically possible to make two kinds of oil contents such as a silicone type oil and a non-silicone type oil which have different properties coexist independently from each other in one emulsion system. For example, when an oil-soluble material which is hard to dissolve in a silicone type oil and a non-silicone type oil to which the material is soluble are added in one oil phase, whereas the silicone type oil is added in the other oil phase, the material can be prevented from depositing while these components are made to coexist stably in one emulsion system.
As a method of preparing a multiple emulsion, there has conventionally been known a so-called two-step emulsion technique in which an O/W type emulsion formed by using a hydrophilic surfactant 16 is re-emulsified in an outer oil phase in which a lipophilic surfactant 18 has been dissolved. However, the emulsification stability of thus prepared multiple emulsion may be so low that, over time, the inner oil phase 14 and the outer oil phase 10 can merge with each other or the water phase 12 can be incorporated therein, thereby finally dissociating the oils or water. Since the emulsification stability of the multiple emulsion itself is quite low, the above-mentioned effects expected from the O/W/O type multiple emulsion have not been fully attained.
In order to overcome these problems, various attempts have been made. For example, Japanese Examined Patent Publication No. 55-33294 discloses a method in which a milk protein and cane sugar fatty acid ester are used together, while Japanese Examined Patent Publication No. 3-54709 discloses a method in which polyglycerine fatty acid ester is compounded in the outer oil phase. Also, Japanese Unexamined Patent Publication No. 63-30405 discloses a method in which a specific kind of bentonite and dextrin fatty acid ester are respectively compounded in the water phase and the outer oil phase.
However, even in the O/W/O type multiple emulsions prepared by the above-mentioned conventional methods, the inner oil phase still tends to merge with the outer oil phase, thereby reducing the remaining amount of the inner oil phase over time. Namely, since the inner oil phase 14 and the outer oil phase 10 face each other with the water phase 12 and hydrophilic groups of the surfactants 16 and 18 therebetween, there is only a very small barrier for preventing these oil phases 10 and 14 from merging with each other. Also, since the inner oil phase 14 has to be present, it is difficult, physically or in techniques of manufacture, for the water phase 12 to have a small particle size. Accordingly, the O/W/O type multiple emulsion has a greater number of causes for unstableness as compared with the conventional O/W type or W/O type emulsions. Therefore, the products prepared by the above-mentioned methods have a shortcomings that the characteristics of the multiple emulsion are not sufficiently represented in their physical properties.
Also, while an O/W/O type multiple emulsion in which an ultraviolet absorber or an antioxidant is compounded in its inner oil phase has recently been reported in Japanese Unexamined Patent Publication No. 7-101844, since the conventional technique is used for preparing such a multiple emulsion, its emulsification stability tends to be so low that the emulsion condition may be collapsed during a long period of storage, whereby the stability of the agent compounded in the inner oil phase against oxidization over time can not be improved.
Thus, in the conventional multiple emulsions, those which are stable over time cannot be easily obtained. Also, for example, even when an oil-soluble agent is contained in the inner oil phase at the time of preparation, the inner oil phase may merge with the outer oil phase over time, thereby reducing the remaining amount of the inner oil phase and finally incorporating the inner oil phase into the outer oil phase. Accordingly, the agent and the oil in the inner oil phase may migrate to the outer oil phase, whereby the effects expected from the O/W/O type emulsion composition cannot be sufficiently obtained.
Also, in order to improve the stability of an emulsion, the above-mentioned conventional methods include a step for rapidly cooling and plasticizing the emulsion subsequent to the heating step during its preparation. In this case, the heating and rapid cooling steps necessitate a special apparatus and, accordingly, it is quite difficult for thermally unstable ingredients such as vitamins to be compounded.

O/W/O type multiple emulsion and method of preparing the same


A runout and braking device, particularly for medium steel rolled sections, includes a run-in roller table and a braking device arranged laterally offset and parallel to the run-in roller table, wherein the run-in roller table and the braking device form a runout and braking system. The runout and braking device of the above-described type includes a braking device with a rigidly arranged braking trough with a bottom which is outwardly inclined relative to the horizontal direction. The run-in roller table includes a lifting bottom forming a plane, wherein conveying rollers mounted below the lifting bottom protrude above the plane of the lifting bottom. Pivoting devices are provided for pivoting the run-in roller table together with the lifting bottom and the conveying rollers arranged below the lifting bottom about a laterally offset pivoting point into an inclined position toward the braking trough.

1. Field of the Invention
The present invention relates to a runout and braking device, particularly for medium steel rolled sections. The device includes a run-in roller table and a braking device arranged laterally offset and parallel to the run-in roller table, wherein the run-in roller table and the braking device form a runout and braking system.
2. Description of the Related Art
The development of rolling mills has resulted, within short intervals, in increases of the rolling speeds. Consequently, increasing quantities of rolling stock have been supplied to the finishing departments and, when the capacities of the finishing departments could no longer keep up with the rolling capacity, the finishing departments represented a bottleneck for the entire flow of material. This resulted in the requirement that the finishing departments had to be further developed and adapted in such a way that an ever increasing rolling mill production can be handled on-line, with the tendency being toward more efficient solutions in order to increase the capacity by improved automation and simultaneously to reduce the relatively high cost of personnel.
The primary goal is to increase the speed of the entire flow of material and to provide means and measures for an orderly deposition of rolled bars in corresponding cooling bed lengths. Of particular importance is the positionally accurate deposition of individual rolled rods; specifically, predetermined cut lengths of the rolled bars must come to rest on the cooling bed in bundles with a number of commercial lengths, wherein the front ends or rear ends of the bars are aligned. In order to achieve this, controllable, fully automatic runout and braking devices are usually required between the runout of a rolling mill and the entry of a cooling bed.
A device of this type is known, for example, from DE-0S 2 218 041. In this device, a rolled bar emerging from the rolling train passes initially a cutting device for cropping the useless front ends of the rolled bar and is then conducted onto a runout roller table. In the runout roller table, a braking roller table which can be lifted on one side is activated and the braking action of the rod moving on the table is initiated. In the known device, such a braking roller table is composed of conveying rollers arranged with a slight inclination relative to the rolling axis, wherein the conveying rollers displace the rolled bar over the entire length toward the cooling bed side. As soon as the rolled bar is moved laterally out of the area of the runout roller table and onto the braking roller table, the braking roller table is lowered and the runout roller table is again available for receiving another rolled bar. Depending on the section type of the rolled bar, the braking roller table is controlled in such a way that cropping of the front end of the bar can be carried out in the cutting device in a predetermined length or, if the rolled bars do not have to be cropped, a final position is reached which is located in front of the cutting device. If the rolled bars are to be straightened, they pass a straightening machine and are subsequently supplied through the run-out roller table to the cooling bed. In the known device, as shown in FIG. 1, the braking device in the form of a braking roller table is arranged parallel to the runout roller table.
In accordance with other known solutions for constructing a runout area together with braking devices, braking slides may be arranged within a roller table or wipers for laterally wiping rolled sections in the form of a dropping movement into the side wall may be provided.
Braking slides have the disadvantage that, in the case of relatively low rolling speeds, a quick and safe transverse movement does not take place on the braking slides which are being raised. On the other hand, the use of wipers has the disadvantage that pull rods for the common pivoting movement of the wipers, which are subjected to thermally caused length changes, may lead to undesired pivoting movements. Moreover, an abrupt wiping to the side and the resulting rough dropping movement into the side wall may lead to deformations, particularly in the case of thin-walled I-beam sections.

Runout and braking device particularly for medium steel rolled sections


A universal cell phone security band for displaying cell phones of various sizes includes a band that is placed around the phone. The band has a first end and a second end with notches extending from its edges. The band""s second end is received in an adjustable slide at a slot including a wide portion configured to receive the notched second end and a narrow portion configured to receive the portions of the band between the notches. The adjustable slide also has an opening that is configured to receive a threaded connector that is disposed on the band""s first end. The opening and the threaded connector are secured with a security-type fastener having a recess that requires the use of a tool other than a traditional flathead or Phillips head screwdriver to rotate the security fastener. A cable can secure the universal security band to a display.

This invention relates to a universal cell phone security band. In particular, it relates to a band for securing handheld wireless telephones of various sizes for display in retail stores.
Recently there has been an explosion in the use of wireless telephones, commonly called cellular telephones, or just cell phones. To fill the need of consumers, there has been a corresponding increase in the number of manufacturers and styles of cellular telephones. Improvements in technology have enabled manufacturers to produce cellular telephones that are very small in size. Producers and retailers of cellular telephones obviously need to display their products for sale to consumers. However, because the products are highly desirable and very small, they are prone to theft. Of course, various techniques have been employed to secure cellular telephones to display areas. Due to the many varying sizes, up to this point each method of securing cellular telephones to a display area has been uniquely designed for the particular phone being displayed. The method of securing the phone to the display must also be capable of allowing a potential purchaser to hold the phone in his or her hand to simulate its use, and it also must be secure enough so that the product cannot be easily stolen.
Thus, an improved means for securely displaying cellular telephones, and one that is adaptable for use on a variety of styles of phones is desired.
The cell phone security band that includes a band adapted to wrap around cell phones of various sizes is provided. More particularly, the universal cell phone security band disclosed herein includes an elongated band having a first end and a second end with notches extending from the edges of the second end of the band. The second end of the band is received in a slot that forms an adjustable slide. The slot includes a wide portion configured to receive the notches on the second end of the band, and a narrow portion configured to receive the portions on the second end of the band between the notches.
The adjustable slide also has an opening that is configured to receive a threaded connector that is disposed on the first end of the band. The security fastener is secured to the opening of the adjustable slide with a security fastener having a recess. The recess requires the use of a tool other than a traditional flathead or Phillips head screwdriver in order to rotate the security fastener. Such a tool has an end that is complementary to the recess in the fastener. For example, the fastener is a bolt with a star-shaped recess, and the tool has an end that is complementary to the recess.
A cable can be secured on one end to the universal security band and on the other end to a display to secure the cell phone to the display. Preferably, the cable is secured to the threaded fastener of the universal security band.
A method of using the universal security band is also provided. It includes the following steps. A band is wrapped around the item. The second end of the band is inserted through a wide portion of a slot of an adjustable slide. The second end of the band is pulled through the adjustable slide until a hole on the adjustable slide is aligned with the threaded connector on the first end of the band. A cable is secured to one of the band, the threaded connector, and the adjustable slide. A security fastener is inserted through the hole in the adjustable slide and though the threaded connector. The security fastener is rotated into the threaded connector to secure the item to the display.
Accordingly, a universal cell phone security band for securely displaying wireless telephones of various sizes and configurations is provided. Other objects and advantages of the invention will become apparent from the following description that sets forth, by way of illustration and example, certain preferred embodiments of the present invention.

Adjustable display device for securing cellular phones to a display


A method of forming solder paste on an object is provided. The method includes providing a multilayered stencil, each stencil layer having an aperture formed therethrough from a top surface of the respective stencil layer to a bottom surface of the stencil layer. The method also includes applying the stencil to a surface of the object. The method also includes filling a void space formed by a combination of the apertures in the stencil layers with solder paste. The method also includes removing the stencil layers in a sequential manner to leave the solder paste.

The present disclosure relates to the electrical, electronic and computer fields. In particular, the present disclosure relates to the use of screen printing stencils. Screen printing stencils are used in a wide variety of applications in the electronic substrate fabrication and electronic assembly industry for applying materials such as photo resist or solder paste.
As the size of the features of a semiconductor device continues to decrease, greater precision is required in order to apply viscous material to the surface thereof. This includes the application of solder paste to the surface of a printed circuit board or die for securing, for example, a flip chip thereto. Metal stencils are currently utilized to apply the solder paste onto the surface for connecting the contact pads of surface mounted flip chips. These stencils typically have a plurality of apertures that are formed in the stencil in certain locations that correspond to the pattern of the contact pads on the printed circuit board of choice.
In use, these stencils are positioned near or on the surface of the printed circuit board, the apertures in the stencil are aligned over the contact pads upon which the solder paste is to be applied, the solder paste is then urged mechanically through the apertures via a wiper, and the stencil is removed, leaving small islands of solder paste remaining on the contact pads of the printed circuit board.

International Business Machines Corporation


Swash plate type compressor including a cylinder block having cylinder bores arranged along a circle, a drive shaft aligned with the circle, a swash plate rotated with the drive shaft, and single-headed pistons each including a head portion engaging the cylinder bore, and a neck portion engaging the swash plate, and wherein each piston is reciprocated by the swash plate rotated by the drive shaft, and the head portion includes a circular body portion, and an outer sliding portion and an inner sliding portion which are disposed between the body portion and the neck portion and which slidably engage respective circumferential portions of the cylinder bore which correspond to respective radially outer and inner portions of the cylinder block. Length from the end face of the body portion to the remote end of the inner sliding portion is larger than the corresponding length of the outer sliding portion. The inner sliding portion has a distal sliding part spaced from the end face by at least 40% of the entire piston length and having a central angle of not larger than 120xc2x0 and a length of at least 5% of the entire piston length.

This application is based on Japanese Patent Application No. 11-150448 filed May 28, 1999, the content of which is incorporated hereinto by reference.
1. Field of the Invention
The present invention relates in general to a swash plate type compressor, and more particularly to the configuration of a single-headed piston of such type of compressor.
2. Discussion of the Related Art
There has been used a swash plate type compressor equipped with a plurality of single-headed pistons. The compressor of this swash plate type includes (1) a cylinder block having a plurality of cylinder bores formed therein such that the cylinder bores are, arranged along a circle, (2) a rotary drive shaft having an axis of rotation aligned with a centerline of the above-indicated circle, (3) a swash plate rotated with the rotary drive shaft, and (4) a plurality of single-headed pistons each of which includes a head portion slidably engaging a corresponding one of said cylinder bores, and a neck portion engaging said swash plate. In this compressor, the pistons are reciprocated by the swash plate rotated with the rotary drive shaft. An example of this swash plate type compressor is disclosed in JP-A-9-203378. In the swash plate type compressor disclosed in this publication, the head portion of each piston is formed with a through-hole substantially parallel to the circumferential direction of the cylinder block, so as to reduce the mass of the piston. As described below, the head portion of the piston has a relatively high sliding surface pressure at two circumferential portions of its outer circumferential surface which correspond to respective circumferential portions of the cylinder bore at respective radially outermost and innermost portions of the cylinder block, and a relatively low sliding surface pressure at circumferential portions of its outer circumferential surface which are intermediate between the above-indicated two circumferential portions in the circumferential direction of the cylinder block. This fact permits the above-indicated through-hole to be formed through the head portion, for the purpose of reducing the mass of the head portion.
However, the swash plate type compressor described above suffers from a problem that the head portion is subject to a local wear and has an insufficient degree of durability due to a tendency of inclination of the pistons within the cylinder bores. Where the outer circumferential surface of the head portion of each piston is coated with a coating film such as a film of polytetrafluoroethylene (PTFE), this coating film is subject to a local wear, and is relatively likely to suffer from a peel-off problem. Reference is made to FIG. 10, wherein a resultant force Fo consisting of an inertial force of a piston 200 and a force based on a pressure of a refrigerant gas in the cylinder bore acts on a swash plate 202 through a hemispherical shoe 201 (one of a pair of hemispherical shoes). The resultant force Fo is balanced with an axial component Foxe2x80x2 of a force Fa which acts on the surface of the swash plate 202 in a direction perpendicular to that surface. The axial component Foxe2x80x2 acts on the piston 200 in a direction parallel to the centerline of the piston 200. A radial component Fb of the force Fa which component Fb acts on the piston 200 in the radial direction of the swash plate 202 is called a side force acting in a direction perpendicular to the centerline of the piston 200. This radial component Fb (more precisely, a resultant force consisting of the radial component Fb and a friction force between the swash plate 202 and the hemispherical shoe 201) is balanced with reaction forces Fc, Fd which the piston 200 receives from the inner circumferential surface of a cylinder bore 204. Since the resultant force Fo increases as the piston 200 is moved to its upper dead point in its compression stroke, the reaction forces Fc, Fd are the largest at a point near the upper dead point. In particular, the reaction force Fc is comparatively large near the upper dead point of the piston 200. Accordingly, the coating film such as the PTFE film formed on the outer circumferential surface of the piston 200 is likely to be locally worn or removed.
The present invention was made in the light of the background prior art described above. It is therefore an object of the present invention to provide a swash plate type compressor which has an improved degree of durability while reducing the mass of the pistons. This object may be achieved according to any one of the following modes of the present invention, each of which is numbered like the appended claims and depends from the other mode or modes, where appropriate, to indicate and clarify possible combinations of technical features of the present invention, for easier understanding of the invention. It is to be understood that the present invention is not limited to the technical features and their combinations described below, and that any technical feature described below in combination with other technical features may be a subject matter of the present invention, independently of those other technical features.
(1) A swash plate type compressor including:
a cylinder block having a plurality of cylinder bores formed therein such that the cylinder bores are arranged along a circle;
a rotary drive shaft having an axis of rotation aligned with a centerline of the circle;
a swash plate rotated with the rotary drive shaft; and
a plurality of single-headed pistons each including a head portion slidably engaging a corresponding one of the cylinder bores, and a neck portion engaging the swash plate, each single-headed piston being reciprocated by the swash plate rotated by the rotary drive shaft, the head portion of each single-headed piston including a body portion having a circular shape in transverse cross section, and an outer sliding portion and an inner sliding portion which are disposed between the body portion and the neck portion, the outer and inner sliding portions slidably engaging respective circumferential portions of an inner circumferential surface of the corresponding cylinder bore which correspond to respective radially outer and inner portions of the cylinder block,
and wherein a distance from an end face of the body portion remote from the neck portion to an end of the inner sliding portion on the side of the neck portion is larger than a distance from the end face to an end of the outer sliding portion on the side of the neck portion, and the inner sliding portion has a distal sliding part which is spaced from the end face by a distance of at least 40% of an entire length of the piston in an axial direction of the piston and which has a central angle of not larger than 120xc2x0, the distal sliding part having a length which is at least 5% of the entire length of said piston.
In the swash plate type compressor constructed according to the above mode (1) of the invention, the head portion of each piston includes the body portion, the inner sliding portion and the outer sliding portion. The inner sliding portion has the distal sliding part which is spaced from the end face of the body portion by a distance of at least 40% of the entire length of the piston and which has the central angle of not larger than 120xc2x0 and the length which is at least 5% of the entire length of the piston. This arrangement assures a relatively large distance between the axial positions at which the above-indicated two reaction forces act on the piston. Accordingly, the reaction force Fc corresponding to the given side force Fb can be reduced. Further, the amount of increase of the mass of the piston due to the provision of the inner sliding portion is reduced since the distal length of the distal sliding part and its circumferential dimension (central angle) are minimized to such an extent that assures a surface area of the distal sliding part sufficient to limit its sliding surface pressure to a value not higher than a predetermined upper limit. Accordingly, the durability of the distal sliding part (i.e., the durability of the piston) can be effectively increased while reducing the mass of the piston. Where the distal sliding part is coated with a coating film such as a film of PTFE, the local wear and removal of the coating film can be minimized.
The inner sliding portion may be formed so as to extend from the body portion in the axial direction (such that the outer circumferential surface of the inner sliding portion is continuous with that of the body portion). Alternatively, the inner sliding portion may be formed in spaced-apart relation with the body portion (such that the outer circumferential surface of the inner sliding portion is not continuous with that of the body portion). In the former case, the length or distance from the end face of the body portion to the end of the inner sliding portion on the side of the neck portion is equal to a sum of the axial length of the body portion and the axial length of the inner sliding portion (total axial length of the body portion and the inner sliding portion as measured on the radially inner side of the head portion). In the latter case, the above-indicated distance is larger than the above-indicated sum. The above description applies to the outer sliding portion. Namely, the outer sliding portion may either extend from the body portion, or be formed in spaced-apart relation with the body portion. Further, the relationship described above with respect to the inner sliding portion applies to the relationship between the distance from the end face of the body portion to the end of the outer sliding portion on the side of the neck portion and the sum of the axial lengths of the body portion and the outer sliding portion
The distance from the end face of the body portion to the end of the inner sliding portion on the side of the neck portion is made larger than the corresponding distance of the outer sliding portion, in view of a fact that the durability of the piston can be effectively improved by increasing the above-indicated distance of the inner sliding portion rather than the corresponding distance of the outer sliding portion. In this respect, it is noted that the sliding surface pressure at the end portion of the outer sliding portion on the side of the neck portion is maximized at a point of transition from the suction stroke to the compression stroke of the piston, and that the side force at this point of time is based primarily on the inertial force of the piston, and is smaller than the side force in the terminal portion of the compression stroke. Accordingly, it is more effective to increase the above-indicated distance of the inner sliding portion rather than the corresponding distance of the outer sliding surface.
The circumferential dimension (central angle) of the inner sliding portion may be constant over its entire axial length, or may be smaller or larger at its part nearer to the neck portion than at its part near to the body portion. In the latter case, the central angle of the distal sliding part of the inner sliding portion is made smaller or larger than that of the other part (referred to as xe2x80x9cproximal sliding partxe2x80x9d since it is adjacent or nearer to the body portion of the head portion) of the inner sliding portion. The distal sliding part may be configured such that its central angle is constant over its entire axial length or changes depending upon the axial position. For instance, the central angle of the distal sliding part may decrease continuously or in steps as it extends in the axial direction toward the neck portion. The distal sliding part may be formed integrally with the proximal sliding part, or in spaced-part relation with the proximal sliding part.
The proximal and distal sliding parts may have a suitable shape in transverse cross section, which may be generally defined by an arc and a chord, or by a part of an annulus, or may be crescent or generally rectangular. In other words, the surfaces of the proximal and distal sliding parts of the inner sliding portion which slidably engage the inner circumferential surface of the cylinder bore are required to have shapes which follow the corresponding parts of that inner circumferential surface. However, the surfaces of the proximal and distal sliding parts which are opposed to the outer sliding portion may have any shapes, for instance, may be flat surfaces or concave surfaces. Where these surfaces are concave, the mass of the piston is reduced owing to the concavity. The shapes in transverse cross section may be symmetrical or asymmetrical with respect to a plane which passes the centerline of the piston and the centerline of the cylinder block. As described before, a force of friction between the piston and the swash plate also acts on the piston, so that the direction in which a reaction force produced by the inner circumferential surface of the cylinder bore acts on the piston deviates from the plane passing the centerline of the piston and cylinder block, in a direction determined by the direction of rotation of the swash plate. Accordingly, where the swash plate (drive shaft) is rotated in a predetermined one direction, it is advantageous that the inner sliding portion has an asymmetric shape in transverse cross section such that the inner sliding portion has a larger sliding surface on one side of the above-indicated plane on which the above-indicated reaction force deviates from that plane, than on the other side.
The distal sliding part is spaced from the end face of the body portion by a distance which is at least 40% of the entire length of the piston. Preferably, this distance is at least 43% or 46% of the entire length of the piston. An effect of the distal sliding part to prevent the inclination of the piston relative to the centerline of the cylinder bore increases with an increase in the distance of the distal sliding part from the end face of the body. Where the distal sliding part is formed integrally with the proximal sliding part, the weight of the piston increases with the above-indicated distance. It is further noted that the maximum operating stroke of the piston is determined by the outside diameter and inclination angle of the swash plate. Therefore, the axial position of the distal sliding part is desirably determined by taking into account its effect to prevent the piston inclination, the amount of increase of the piston mass and the operating stroke.
(2) A swash plate type compressor according to the above mode (1) , wherein the central angle of the distal sliding part is not larger than 100xc2x0.
While the central angle of the distal sliding part is required to be not larger than 120xc2x0 according to the above mode (1), this central angle is preferably not larger than 110xc2x0 or 100xc2x0, for effectively reduce the mass of the piston. The mass of the piston can be more effectively reduced when the central angle is 95xc2x0 or 90xc2x0 or smaller.
A decrease in the central angle of the distal sliding part increases the sliding surf ace pressure of the distal sling part, but reduces the mass of the piston. Accordingly, the central angle of the distal sliding part is preferably determined by taking into account both the sliding surface pressure and the piston mass. Where the central angle of the distal sliding part is extremely small, for example 20xc2x0, the inner sliding portion having this distal sliding part provides some effect to prevent inclination of the piston relative to the centerline of the cylinder bore, as compared with the inner sliding portion which does not have the distal sliding part. In view of this, the central angle of the distal sliding part may be not larger than 85xc2x0, 80xc2x0 or 70xc2x0.
(3) A swash plate type compressor according to the above mode (1) or (2), wherein the inner sliding portion includes a wide section disposed. on the side of the body portion, and a narrow section which is disposed on the side of the neck portion and which has a smaller circumferential dimension than the wide section.
The narrow section and the wide section may be respectively the distal sliding part and the proximal sliding part which have been described above.
(4) A swash plate type compressor according to the above mode (1) or (2), wherein the inner sliding portion includes a narrow section disposed on the side of the body portion, and a wide section which is disposed on the side of the neck portion and which has a larger circumferential dimension than the narrow section.
The narrow section and the wide section may be respectively the proximal sliding part and the distal sliding part which have been described above. This arrangement permits effective reduction of the sliding surface pressure while reducing the increase of the mass of the piston due to the provision of the inner sliding portion.
(5) A swash plate type compressor according to any one of the above modes (1)-(4), wherein the length of the distal sliding part is at least 8% of the entire length of the piston.
The axial length of the :distal sliding part is at least 5% of the entire length of the piston according to the principle of the above mode (1) of the present invention. In the above mode (5) wherein this axial length is at least 8% of the entire piston length, the sliding surface pressure of the piston can be further reduced. Where the length of the distal sliding part is at least 10%, 12% or 15% of the entire piston length, the piston can be further effectively prevented from being inclined.
Where the inner sliding portion extends continuously from the body portion in the axial direction, an increase in the axial length of the distal sliding part increases the entire axial length of the inner sliding portion and consequently the mass of the piston, if the axial length of the proximal sliding part is unchanged. Accordingly, the percentage of the axial length of the distal sliding part with respect to the entire piston length is desirably determined by taking account of the effect to reduce the sliding surface pressure of the piston, and the amount of increase in the mass of the piston due to the provision of the inner sliding portion.
(6) A swash plate type compressor including:
a cylinder block having a plurality of cylinder bores formed therein such that the cylinder bores are arranged along a circle;
a rotary drive shaft having an axis of rotation aligned with a centerline of the circle;
a swash plate rotated with the rotary drive shaft; and
a plurality of single-headed pistons each including a head portion slidably engaging a corresponding one of the cylinder bores, and a neck portion engaging the swash plate, each single-headed piston being reciprocated by the swash plate rotated by the rotary drive shaft,
the head portion of each single-headed piston including a body portion having a circular shape in transverse cross section, and an outer protrusion and an inner protrusion which extend toward the neck portion from respective radially outer and inner portions of the cylinder block and which slidably engage respective circumferential portions of an inner circumferential surface of the corresponding cylinder bore,
and wherein a total length of the body portion and the inner protrusion in an axial direction of the piston is at least 45% of an entire length of the piston, the inner extension having a central angle of not larger than 120xc2x0 in at least a distal end portion thereof which is remote from the body portion and whose axial length is at least 10% of the above-indicated total length, a distance of extension of the inner protrusion from the body portion being larger than that of the outer protrusion.
In the swash plate compressor constructed according to the above mode (6) of the present invention, the outer sliding portion and the inner sliding portion of the head portion are provided in the form of the outer protrusion and the inner protrusion, respectively which extend from the body portion of the head portion in the axial direction toward the neck portion. The head portion including these outer and inner protrusions has a larger strength than the head portion wherein the outer and inner sliding portions are formed in spaced-apart relation with the body portion.
The distal end portion of the inner protrusion whose central angle is not larger than 120xc2x0 and whose axial length is at least 10% of the total length of the body portion and the inner protrusion corresponds to the distal sliding part described above with respect to the above mode (1). The distal sliding part may be referred to as a sliding distal end part.
(7) A swash plate type compressor including a cylinder block having a plurality of cylinder bores formed therein such that the cylinder bores are arranged along a circle, a rotary drive shaft having an axis of rotation aligned with a centerline of the circle, a swash plate rotated with the rotary drive shaft, and a plurality of single-headed pistons each including a head portion slidably engaging a corresponding one of the cylinder bores, and a neck portion engaging the swash plate, each single-headed piston being reciprocated by the swash plate rotated by the rotary drive shaft,
the head portion of each single-headed piston including a body portion having a circular shape in transverse cross section, and an inner sliding portion including (a) an inner protrusion which extends toward the neck portion from a radially inner portion of the cylinder block and which has a proximal inner sliding surface which slidably engages an inner circumferential surface of the corresponding cylinder bore, and (b) a spaced-apart distal sliding part which has a spaced-apart inner sliding surface spaced apart from the inner protrusion, the spaced-apart distal sliding part being spaced from an end face of the body portion remote from the neck portion, by a distance of at least 40% of an entire length of the piston, the spaced-apart distal sliding part having a central angle of not larger than 120xc2x0 and an axial length which is at least 5% of the entire length of the piston.
In the swash plate type compressor constructed according to the above mode (7), the distal sliding part is the spaced-apart distal sliding part which is spaced from the inner protrusion. For instance, the spaced-apart distal sliding part may be formed on a connecting portion which connects the inner protrusion and the neck portion. The spaced-apart distal sliding part is located at an axial position between the inner protrusion and the neck portion, which axial position is spaced from the end face of the body portion by a distance of at least 40% of the entire piston length, as described above. This mode (7) of the invention provides an increased freedom of design in the position of the spaced-apart distal sliding part.
The above mode (7) may be modified such that the inner protrusion is a connecting portion which does not have the proximal inner sliding surface and which merely connects the spaced-apart distal sliding part and the body portion.
(8) A piston for a swash plate type compressor, said piston having a head portion slidably received in a cylinder bore formed in a cylinder block, and a neck portion engaging a swash plate, the head portion includes:
a body portion having a circular shape in transverse cross section; and
an outer sliding portion and an inner sliding portion which are disposed between the body portion and the neck portion, the outer and inner sliding portions slidably engaging respective circumferential portions of an inner circumferential surface of the corresponding cylinder bore which correspond to respective radially outer and inner portions of the cylinder block,
and wherein a distance from an end face of the body portion remote from the neck portion to an end of the inner sliding portion on the side of the neck portion is larger than a distance from the end face to an end of the outer sliding portion on the side of the neck portion, and the inner sliding portion has a distal sliding part which is spaced from the end face by a distance of at least 40% of an entire length of the piston in an axial direction of the piston and which has a central angle of not larger than 120xc2x0, the distal sliding part having a length which is at least 5% of the entire length of the piston. the each
There is also provided a piston for a swash plate type compressor, which is described with respect to any one of the above modes (2)-(7).

Swash plate type compressor wherein piston head has inner sliding portion for reducing local wear

Kabushiki Kaisha Toyoda Jidoshokki Seisakusho