A single-reel tape cartridge cooperable with an operatively compatible tape drive including a tape catch member (H) includes a cartridge housing (1) having a tape window (4) defined therein and accommodating therein a single reel (2) with a roll of a length of magnetic recording tape (3) thereon. A leader pin (14) is secured to a free end of the magnetic tape (3) and engageable with the tape catch member (H) when the length of magnetic tape is to be drawn out of the cartridge housing and into the tape drive. A releasable locking mechanism for locking the leader pin (14) in a predetermined posture at a retracted position at which the leader pin is housed within the cartridge housing (1) and positioned adjacent the tape window (4) includes a pair of first locking members (19) and a second locking member (20) cooperable with each other to lock the leader pin (14) at a retracted position.

1. Field of the Invention
The present invention generally relates to a single-reel recording tape cartridge and, more particularly, to the single-reel recording tape cartridge of a kind including a leader piece which is, when in use, captured by a catch member, forming a part of an automatic tape threading mechanism built in the tape drive, so that a length of magnetic recording tape can be drawn out of the cartridge.
2. Description of the Prior Art
The tape cartridge of the kind referred to above is well known in the art and is disclosed in, for example, the Japanese Laid-open patent publications No. 11-7749, published Jan. 12, 1999, and No. 11-232826, published Aug. 27, 1999, and U.S. Pat. No. 5,883,771 issued Mar. 16, 1999. In general, the single-reel recording tape cartridge includes a generally rectangular cartridge housing having a reel chamber defined therein, and a single reel freely rotatably accommodated within the reel chamber and having a roll of a length of magnetic recording tape mounted thereon. The length of magnetic recording tape has one end anchored to a reel hub and the opposite end coupled with the leader piece. When the cartridge is in use having been loaded into a tape drive for data recording or retrieval, a catch member forming a part of an automatic reeling mechanism built in the tape drive captures the leader piece to draw the magnetic recording tape out of the cartridge housing in readiness for data recording or retrieval in cooperation with a magnetic read/write head.
The leader piece disclosed in the publication No. 11-7749 is a generally hook-shaped, plastics-molded leader that is, when the cartridge is not in use, retained at a retracted position in a cantilevered fashion by means of a pair of projections disposed inside the cartridge housing at a location inwardly of a tape window in the cartridge housing.
The leader piece disclosed in the publication No. 11-232826 is in the form of a metal pin having its opposite ends formed with an engagement boss. The leader piece disclosed in this publication is, when the cartridge is not in use, retained at a retracted position with its opposite engagement bosses received within generally U-shaped bearing recesses defined in top and bottom panels of the cartridge. Barrier walls for preventing a spring element from being displaced in position are formed adjacent the associated bearing recesses so as to protrude parallel to the top and bottom panels, respectively. The spring element is in the form of a torsion spring having opposite spring arms, one of which is formed with a generally arcuate portion adapted to engage the corresponding engagement boss when the leader piece is not in use.
As discussed above, the single-reel recording tape cartridge in general makes use of the leader piece to ensure a sure withdrawal of the length of magnetic recording tape out of the cartridge housing in cooperation with the catch member. In order for the catch member to capture the leader piece properly when the cartridge is in use, care must however be taken to allow the leader piece to be kept at the retracted position firmly in a proper posture or substantially in a proper posture within a permissible range in the event of an impact or shock imposed on the cartridge. However, as is well known to those skilled in the art, the single-reel tape cartridge for a specific application, for example, for use in a computer-based information processing environment is generally heavier than the two-reel tape cartridge and, therefore, the single-reel tape cartridge has a relatively large kinetic inertia.
Accordingly, in the event that the single-reel tape cartridge is inadvertently fallen down onto, for example, a floor, the single-reel tape cartridge is susceptible to a relatively high impact. For example, one or more reel locking pawls used to hold the tape reel in a stationary position within the cartridge housing when the tape cartridge is not in use may be instantaneously disengaged from the reel or damaged detrimentally, resulting in loosening of the length of magnetic recording tape that has been firmly wound around the reel hub. Loosening of the length of magnetic recording tape may be in turn accompanied by an undesirable displacement of the leader piece from the retracted position or separation of the leader piece out of the cartridge housing.
The retracted position for the leader piece is generally defined within the cartridge housing and at a location adjacent to and inwardly of the tape window defined in a part of the peripheral wall of the cartridge housing. The tape window is selectively opened or closed by a door member so that when the door member is in a closed position, the reel chamber can be protected from potential sources of harm such as dust and particulate contaminants that would give rise to damage to the magnetic tape within the reel chamber.
Accordingly, in the event that the tape cartridge is inadvertently fallen onto the floor with the leader piece consequently displacing from the retracted position and/or departing from the proper posture, no one can ascertain whether or not the leader piece has displaced or departed, unless one looks into the reel chamber externally through the window by opening the door. In most cases, however, unless the tape cartridge housing including the door is physically deformed and/or damaged in its appearance even though the leader piece inside the cartridge housing would have displaced from the retracted position and/or departed from the proper posture, such tape cartridge is provided for actual use in the tape drive. The outcome would be that the catch member, forming a part of the automatic tape threading mechanism built in the tape drive, fails to catch or grab the leader piece. This is indeed detrimental to obtainment of consistently smooth tape winding within the tape drive preparatory to data recording or retrieval.
Accordingly, the present invention is primarily intended to provide an improved, highly reliable single-reel tape cartridge including the leader piece that is held firmly at the retracted position in a proper posture regardless of whether or not the impact acts on the tape cartridge, to thereby ensure obtainment of consistently smooth tape winding within the tape drive preparatory to data recording or retrieval.
In order to accomplish this and other objects of the present invention, there is in accordance with the present invention provided a single-reel tape cartridge cooperable with an operatively compatible tape drive including a tape catch member, which cartridge includes a cartridge housing having a tape window defined therein, and a single reel rotatably accommodated within the cartridge housing and having a roll of a length of magnetic recording tape coaxially mounted thereon. The length of magnetic recording tape has one end anchored to the reel and the opposite end provided with a leader member that is positioned adjacent the tape window. The leader member is engageable with the tape catch member when the length of magnetic tape is to be drawn out of the cartridge housing and into the tape drive. A releasable locking mechanism is provided, including a pair of first locking members and a second locking member cooperable with each other to lock the leader member at a retracted position at which the leader member is housed within the cartridge housing and positioned adjacent the tape window. The first locking members are secured to top and bottom panels of the cartridge housing adjacent the tape window for receiving the leader member at the retracted position in a predetermined posture whereas the second locking member is positioned adjacent the tape window and cooperate with the first locking members to lock the leader member at the retracted position.
According to the present invention, because of the use of the releasable locking mechanism in the single-reel tape cartridge, even though the leader member undergoes a motion under the influence of impact imposed on the tape cartridge as a result of the tape cartridge being, for example, fallen onto a floor, the leader member can advantageously be retained and locked at the retracted position without substantially displacing in position. Accordingly, when the length of magnetic tape is desired to be drawn out of the tape cartridge, no misalignment of the catch member on the part of the tape drive with the leader member in the tape cartridge will occur substantially. Thus, the present invention is effective to ensure a sure engagement of the catch member with the leader member.
In a preferred embodiment of the present invention, the leader member is in the form of a leader pin having a hooking arm connected to each of opposite ends of the leader pin so as to extend generally perpendicular to the leader pin. The hooking arms on the respective ends of the leader pin can cooperate with the catch member to allow the latter to engage the leader member when the length of magnetic tape is to be drawn out of the cartridge housing.
In such case, the second locking member may include an elongated lock body supported by the cartridge housing, and a biasing spring housed within the cartridge housing for urging the elongated lock body in a direction required for the elongated lock body to engage the leader pin. The second locking member may be either pivotally supported or fixedly supported in the cartridge housing.
More specifically, the second locking member may include a bearing boss journalled by and within the cartridge housing for angular movement about its own longitudinal axis, an elongated lock body formed integrally with the bearing boss so as to extend in a first direction generally perpendicular to the longitudinal axis of the bearing boss, and a lock release piece formed integrally with the bearing boss so as to extend in a second direction counter to the first direction, said elongated lock body applying a retaining force to the leader pin to lock the leader pin at the retracted position in cooperation with the first locking members.
Alternatively, the second locking member may include a bearing boss disposed within the cartridge housing with its own longitudinal axis perpendicular to a lengthwise direction of the magnetic tape, an elongated lock body formed integrally with the bearing boss so as to extend in a first direction generally perpendicular to the bearing boss, said elongated lock body including at least one lock arm having a free end thereof bifurcated to define a pair of elastically deformable embracing pieces for receiving the leader pin 14 therein, and at least one receiving arm having a free end thereof formed with a hook for holding the leader pin, and wherein a direction of detachment of the leader pin relative to the lock arm and a direction of detachment of the leader pin relative to the receiving arm lie at an angle to each other.
Again alternatively, the second locking member may include a bearing boss disposed within the cartridge housing with its own longitudinal axis perpendicular to a lengthwise direction of the magnetic tape, an elongated lock body formed integrally with the bearing boss so as to extend in a first direction generally perpendicular to the bearing boss, said elongated lock body including a pair of receiving arms for engagement with opposite ends of the leader pin in a direction outwardly of the cartridge housing and a lock arm for receiving a portion of the leader pin intermediate between the opposite ends thereof.
The number of one or both of the receiving arms and the lock arms may not be limited to one, but two or more of them can be employed.
Preferably, the cartridge housing may have a pivotally supported door for selectively closing or opening the tape window and having an inner side face leading towards an interior of the cartridge housing, in which case the inner side face of the door is preferably configured to retain the leader pin at the retracted position when the door is in position to close the tape window.
Further scope of applicability of the present invention will become apparent from the detailed description given hereinafter. However, it should be understood that the detailed description and specific examples, while indicating preferred embodiments of the invention, are given by way of illustration only, since various changes and modifications within the spirit and scope of the invention will become apparent to those skilled in the art from this detailed description.

Single-reel tape cartridge with leader locking mechanism


A liquid crystal display device is provided. The liquid crystal display device comprises a frame, a back light unit, a liquid crystal panel, a first cover and a second cover. The frame is provided with at least one first connecting member. The back light unit is disposed on the frame, and the liquid crystal panel is disposed on the back light unit. The first cover is provided with at least one second connecting member, and it combines with the frame by the engagement between the first connecting member and the second connecting member. The second cover is provided with at least one third connecting member, and it combines with the frame by the engagement between the first connecting member and the third connecting member. The frame, the back light unit and the liquid crystal panel are located between the first cover and the second cover.

1. Field of the Invention
The invention relates to a liquid crystal display device; in particular, the invention relates to a liquid crystal display device with minimized thickness.
2. Description of the Related Art
Referring to FIG. 1, a conventional liquid crystal display device 30 comprises a liquid crystal display unit 31, a rear case 33 and a front case 32. At the side surface of the liquid crystal display unit 31, first screw holes 311a are formed. At the side surface of the rear case 33, second screw holes 331 are formed. The rear case 33 combines with the liquid crystal display unit 31 by screws 34 that are locked to the first screw holes 311a and the second screw holes 331.
Referring to FIG. 2, the liquid crystal display unit 31 comprises a first frame 311. On the first frame 311, a reflector 3121, a light guide 3122, a protection sheet 3123, a first prism sheet 3124, a second prism sheet 3125, a diffuser 3126, and a liquid crystal panel 313 are stacked sequentially. The reflector 3121, the light guide 3122, the protection sheet 3123, the first prism sheet 3124, the second prism sheet 3125. The diffuser 3126 generally consists of a back light unit 312. At the side surface of the first frame 311, the first screw holes 311a are formed.
In order to join the plastic first frame 311, the back light unit 312 and the liquid crystal panel 313, a second frame 314 made of metal is mounted at the side surface of the first frame 311. At the side surface of the second frame 314, third screw holes 314a, corresponding to the first screw holes 311a respectively, are formed.
Referring to FIG. 3, a notebook computer 2, having the above liquid crystal display device 30, is shown. The liquid crystal display device 30 is rotatably disposed on a body 40.
During the assembly of the conventional liquid crystal display device 30, all parts of the liquid crystal unit 31 are firstly joined together. Then, the liquid crystal unit 31 combines with the front case 32 and the rear case 33. Thus, the first frame 311 and the second frame 314 are necessary parts in the conventional liquid crystal display device 30. Due to all of the necessary parts in the conventional liquid crystal display device 30, the thickness of the conventional liquid crystal display device 30 cannot be minimized furthermore.
In order to address the disadvantages of the aforementioned liquid crystal display device, the invention provides a liquid crystal display device of minimized thickness. As well, this invention does not follow the conventional design concept of liquid crystal display device in that the design of the covers is independent.
Accordingly, the liquid crystal display device of this invention comprises a frame, a back light unit, a liquid crystal panel, a first cover and a second cover. The frame is provided with at least one first connecting member. The back light unit is disposed on the frame, and the liquid crystal panel is disposed on the back light unit. The first cover is provided with at least one second connecting member, and it combines with the frame by engagement between the first connecting member and the second connecting member. The second cover is provided with at least one third connecting member, and it combines with the frame by engagement between the first connecting member and the third connecting member. The frame, the back light unit and the liquid crystal panel are located between the first cover and the second cover.
Furthermore, the first connecting member is provided with a first slot and a second slot. The second connecting member is a first protrusion corresponding to the first slot, and the third connecting member is a second protrusion corresponding to the second slot. The first cover combines with the frame by the engagement between the first slot and the first protrusion, and the second cover combines with the frame by the engagement between the second slot and the second protrusion.
Furthermore, the first protrusion, engaging with the first slot, is not in contact with the second protrusion engaging with the second slot.
Furthermore, the first connecting member is made of plastic.
Furthermore, the back light unit comprises a reflector, a light guide, a first diffuser, a first prism sheet, a second prism sheet and a second diffuser. The reflector is disposed on the frame, and the light guide is disposed on the reflector. The first diffuser is disposed on the light guide, and the first prism sheet is disposed on the first diffuser. The second prism sheet is disposed on the first prism sheet, and the second diffuser is disposed on the second prism sheet.
In a preferred embodiment, this invention provides a notebook computer that comprises a body and the above liquid crystal display device rotatably disposed on the body.


A method and a device for analyzing a sensor device, in which the sensor device forms an electric resonator in an oscillating circuit energized with an external energization voltage. The current in the oscillating circuit is detected in the range of the resonant frequency, and then the current thus detected is multiplied by the external excitation voltage. Finally, the signal obtained by this multiplication is averaged.

The present invention relates to a method and a device for analyzing a sensor device, the sensor device forming an electric resonator in an oscillating circuit energized by an external excitation voltage.
Although applicable to any sensor devices, the present invention as well as the principles on which it is based are explained here with respect to a viscosity sensor device.
Piezoelectric thickness-mode shear transducers made of quartz, for example, have been used for measuring viscosity for some time now (see, for example, S. J. Martin et al., Sens. Act. A 44(1994) pages 209-218). When such a thickness-mode shear transducer is immersed in a viscous liquid, the resonant frequency of its natural oscillation and its attenuation vary as a function of the viscosity and density of the viscous liquid.
FIG. 4 shows an equivalent circuit diagram of a known viscosity sensor having a quartz resonator. R in FIG. 4 denotes the viscosity sensor or xe2x80x9cresonatorxe2x80x9d in general. In the electric equivalent circuit diagram, TA denotes the dry component and FA the liquid component. Dry component TA has a series circuit composed of a capacitor C1, an inductor L1 and a resistor R1. The liquid component has a series circuit of an inductor L2 and a resistor R2. Dry component TA and liquid component FA are bridged by an additional capacitor C0.
In liquid component FA, resistance R2 is proportional to {square root over (xcex7xcfx81)}, where xcex7 is the dynamic viscosity and xcfx81 is the density of the viscous liquid. R2 represents the viscous attenuation by the liquid. L2 produces the frequency shift due to the viscous liquid, which is also proportional to {square root over (xcex7xcfx81)}. In the case of rough resonator surfaces, L2 also contains components generated by xe2x80x9ctrappedxe2x80x9d liquid components in the rough resonator surface. In the case of a known or sufficiently constant density xcfx81, the quartz resonator may therefore be used to determine viscosity xcex7.
According to the publication by S. J. Martin et al. cited above, these variable electric parameters R2 and L2 may be detected by using resonator R as the frequency-determining element in an oscillator. As an alternative, the impedance spectrum may be determined in the vicinity of the resonant frequency (see Lec et al., Proc. IEEE Ultrasonics Symp. (1997) pages 419-422).
FIG. 5 shows such a known analyzer circuit for the known viscosity sensor according to FIG. 4.
A voltage controlled oscillator VCO is used, which supplies resonator R which is immersed in a liquid, namely oil in this case. The output signal of resonator R is mixed with a reference signal REF in a multiplier M.
Finally, the d.c. component of the resulting signal is determined via a low-pass filter TP. The curve of this output signal over the frequency of voltage controlled oscillator VCO is ultimately used to evaluate the oil viscosity.
This evaluation is performed in a computer 100, which also controls voltage controlled oscillator VCO.
One disadvantage of the known approaches described above is that in characterizing highly viscous liquids, resistance R2 increases greatly, so that in the vicinity of the series resonant frequency the impedance of the resonator is determined to a great extent by capacitance C0 and by leakage capacitance CS in parallel to it also. This makes it difficult to determine the relative equivalent parameters by using an oscillator or impedance spectroscopy. One possible expedient is connecting an inductor in parallel to compensate for C0 and CS in the vicinity of the series resonant frequency of the resonator. One disadvantage here is the required balancing plus the fact that leakage capacitance CS varies under some circumstances.
The method according to the above publication by Lec et al. allows at least partial compensation for the effects of C0 and CS, depending on the nature of the reference branch, but it does not yield an output signal corresponding to viscosity, but instead it is used only to determine a characteristic frequency response which is determined by viscosity.
The method according to the present invention and the corresponding device have the advantage over the known approach that the corresponding circuits are also suitable for measurement of highly viscous liquids. The sensor output signal is an easily processable direct voltage as a measure of the viscosity of the liquid.
The present invention is based on the idea that the interfering influence of static resonator capacitance C0 and leakage capacitances CS is eliminated by determining the amplitude of the resistive in-phase component of the resonator current at the series resonant frequency.
According to a preferred embodiment, the current is detected by a measuring shunt connected to ground.
According to another preferred embodiment, the amplitude of the resistive component of the resonator current is determined by multiplying a signal which corresponds to the resonator current by the external excitation voltage and then filtering the result to form an average value.
According to another preferred embodiment, the external excitation voltage is wobbled, and the peak value of the signal corresponding to the average value is retained with a time constant which is greater than the period of the wobble frequency.
According to another preferred embodiment, the external excitation voltage is frequency modulated (e.g., with a small square-wave signal). This produces amplitude fluctuations in the signal corresponding to the average value. The signal corresponding to the average value is used together with the modulation signal to regulate the excitation mid-frequency to the resonant frequency.
According to another preferred embodiment, the sensor device is a viscosity sensor and has a determination device for determining viscoelastic effects based on the output signal of the first low-pass filter and the output signal of the regulating device.
According to another preferred embodiment, at least one of the multiplication devices is implemented in the circuitry by a switched inverter.
According to another preferred embodiment, the detection device for detecting the current in the oscillating circuit is a transimpedance amplifier.

Method and device for evaluating a sensor device


A wheel suspension system for a three-wheeled motorcycle or “trike” includes parallel wheels mounted on vertically pivoting suspension arms governed by hydraulic pistons. The pistons have upper liquid reservoirs that are interconnected through a valve system, which interconnects the upper reservoirs when the trike is in motion, allowing opposing vertical wheel movements when banking through turns, and prevents liquid exchange when the trike is stopped, thereby holding the motorcycle upright, Embodiments include a manual and/or automatic valve control. A threshold switching speed for an automatic controller can be factory set and/or user adjustable. The pistons can include directly interconnected lower fluid reservoirs. A shock-absorbing reservoir can allow transient vertical movement of both wheels to absorb shocks. A cover system can emulate the appearance of saddle bags and can appear to be covering only a single wheel.

Motorcycle riding is an activity that can be enjoyed by a wide variety of riders having different ages and skill levels. For many, the thrill and excitement of riding a motorcycle is unparalleled by any other activity. And motorcycle riding can be enjoyed by riders who lack the physical fitness and stamina required by many other forms of outdoor recreation.
Nevertheless, motorcycle riding does require some physical ability on the rider's part, especially when the motorcycle is standing still. While a motorcycle may be easy to balance and control while it is in motion, it can be very difficult to manage and even dangerous when stopped or nearly stopped. This can make it very difficult for some riders to operate a motorcycle, especially riders who are senior in age, physically impaired, short in stature, or who simply lack the required physical strength to hold a heavy motorcycle upright while stopping, dismounting, and deploying the kick-stand. As a result, many physically impaired riders, senior riders, women, and others must be content to ride a very light bike, or not to ride at all.
One approach for riders who have difficulty managing a standard motorcycle is to ride a three-wheeled motorcycle, sometimes referred to as a "trike," which has been designed to stand on its own when stopped, thereby eliminating most or all difficulties associated with managing a stopped 2-wheel motorcycle. In some cases, a conventional 2-wheel motorcycle can be converted to a trike, thereby saving cost and providing a wider selection of models available for three-wheel riding.
However, a trike that has been designed to remain upright when standing still presents inherent problems while riding. Specifically, when turning it is desirable for a motorcycle to "bank" into the turn, i.e. to tilt or lean inward so as to counteract the centripetal turning force and maintain the rider's apparent center of gravity above the wheels. Banking during turns improves riding performance and safety, and is also one of the more enjoyable aspects of riding. However, if the two side-by-side parallel wheels of a trike are fixed in height relative to each other, then one of them will tend to lift off of the ground when the trike goes around a curve.
So as to mitigate this problem, some trikes provide a suspension that allows the trike to tilt during a turn without lifting a wheel. One approach is to mount the two parallel wheels on separate lever arms that pivot vertically so as to allow the wheels to separately move up and down when needed. Typically, control rods are connected to the lever arms, whereby the control rods control the vertical movements of the wheels. In some of these designs a "rocker arm" connects the two control rods to each other, thereby requiring that the wheels always move symmetrically in opposite directions. This approach effectively couples the wheel movements to each other, but is generally bulky and difficult to retro-fit to existing 2-wheel motorcycles.
Other lever arm designs use a pneumatic or hydraulic piston mounted on each control rod to manage the vertical movements of the wheels. In some of these designs the hydraulic reservoirs of the pistons are connected to each other, so that an upward movement of one of the wheels forces the other wheel downward. However, these designs do not always cope well when both wheels are lifted off of the ground, for example during servicing, since they can allow both of the parallel wheels to drop down simultaneously to the maximum extensions of the control rods.
In other pneumatic or hydraulic designs the control rods are managed by a processor that uses sensors to determine a speed, handlebar orientation, acceleration, frame orientation, and/or other status parameter of the vehicle, calculates an appropriate tilt angle, and then adjusts the pneumatic or hydraulic system accordingly. However, this approach can be complex, costly, and somewhat unnatural, since the tilt responds to a sensor-based calculation, rather than responding directly to the actual forces encountered by the trike while in operation.
Of course, if the trike is to stand upright on its own, either a conventional "kick-stand" must be provided, or the tilting suspension must provide some mechanism to lock the wheels in place when the trike is not in motion. In some mechanical designs, the suspension is simply locked in place when a manual control is actuated. However, this requires an extra step on the part of the rider. Other designs automatically adjust the suspension to hold the frame "vertical" when certain conditions are sensed, such as a low speed, a straight handlebar orientation, slippage of a wheel, or a sustained frame tilt. However, this approach can require a complex control and sensing system to avoid undesirable results, such as tilting the trike at an unsafe angle when on a hillside.
In addition to the issues described above, riding a "trike" can also carry with it a certain social stigma, so that a rider's enjoyment of riding a trike may be diminished by his or her concern regarding how he or she may be perceived by nearby riders of 2-wheel motorcycles.
What is needed, therefore, is a wheel suspension system for a three-wheeled motorcycle or "trike" that will allow the trike to bank naturally when turning but will hold the frame vertical when the trike is not in motion, is simple in design and yet responds appropriately to hills and roadway depressions, can be retrofitted to existing 2-wheel motorcycles, and can emulate the appearance of a 2-wheel motorcycle, so as to minimize any perceived stigma of riding a trike.

Wheel cover system for a 3-wheeled motorcycle


A circuit includes a memory array comprising K number of rows. The circuit further including a reference column. The reference column includes M cells of a first cell type configured to provide a first leakage current, K-M cells of a second cell type different from the first cell type, the K-M cells are configured to provide a second leakage current, and a reference data line connected to the cells of the first cell type and the cells of the second cell type. The circuit further includes a sensing circuit configured to determine a value stored in a memory cell of the memory array based on a voltage of the reference data line.

In various approaches, data from a bit cell (e.g., a memory cell) is read by detecting the logic level at a corresponding read bit line (e.g., a read bit line RBL). A P-type Metal Oxide Silicon transistor (PMOS transistor) implemented as a feedback keeper is used to compensate the leakage current from unselected bit cells and thus improves "read one" operations, e.g., reading a logic high level (a High), at read bit line RBL. In "read zero" situations, e.g., reading a logic low level (a Low) at read bit line RBL, however, the PMOS keeper slows down the RBL discharge speed. In some situations, if the PMOS keeper sinks a lot of current (e.g., the PMOS transistor has a high conductivity) and/or the cell current is not high enough, the cell current cannot discharge (e.g., pull) read bit line RBL from a High to a Low. As a result, the read operation fails. Variations in the semiconductor manufacturing process also cause the cell current to vary at different voltage and temperature conditions, which also increases the failure rate when the read bit line RBL is read.
Like reference symbols in the various drawings indicate like elements.

Taiwan Semiconductor Manufacturing Company, Ltd.


A valve comprising an inlet housing, an outlet housing, an elastomeric valve element having a generally dome-shaped configuration with a central integral stem positioned substantially concentrically therewith, the inlet housing and outlet housing being fastened together at a joint with the elastomeric valve element positioned therein and the valve element including a plurality of longitudinal ribs formed along an outer annular periphery of a lower end of the dome-shaped configuration that define flow channels that allow fluid flow from across an upper surface of the dome-shaped configuration through the flow channels.

1. Field of the Invention
This invention relates to check valves, and relates more specifically to a check valve for needleless medical usage.
2. Description of the Background Art
Presently, there are many types of check valves which are designed to control the one-way flow of a fluid therethrough. One common type of check valve comprises a valve element, such as a ball or spring biased valve stem, reciprocatingly positioned within a valve body providing a fluid passageway. The flow of fluid in one direction through the valve body is permitted upon displacement of the stem as it flows around the valve stem to exit the valve body. In the opposite direction, however, the fluid pressure along with the spring forces the valve stem against a valve seat, thereby inhibiting, or checking the flow of fluid therethrough. In this manner, this type of check valve effectively provides that fluid can flow only in one direction through the check valve. An example of this type of valve is found in U.S. Pat. No. 5,349,984, the disclosure of which is incorporated by reference herein.
Check valves employing an elastomeric stem without the use of a spring are described in U.S. Pat. No. 3,831,629, the disclosure of which is incorporated by reference herein. Other check valves employing umbrella or disk-like elastomeric elements are described in the following U.S. Pat. Nos. 5,992,462; 4,499,916 and 4,369,812, the disclosures of which are incorporated by reference herein. Some check valves employ elastically deformable diaphragm-like elements as described in U.S. Pat. No. 6,390,120, the disclosure of which is incorporated by reference herein. Another check valve employing conical or hollow elastomeric elements where fluid flow is arranged to pass through the element itself is described in U.S. Pat. Nos. 5,573,516 and 5,746,414, the disclosures of which are incorporated by reference herein. Some of the designs described above allow for bi-directional fluid flow if accessed by the appropriate connector such as a luer fitting commonly used in the medical fluid delivery field.
There is a need in the industry to provide a reliable and economical check valve providing a reliable seal when checked by very low back pressures such as low fractions of pounds per square inch (PSI) while sealing at high back pressures, preferably in the range of 10-100 PSI. There is also a need for check valves that allow for an economical way to accommodate various preset opening or cracking pressure conditions. Most prior art valves of this nature employ springs that have varying spring properties, resulting in a check valve that provides different opening pressures without any component change.
More particularly, current pressure relief valves employ metal springs for accurate opening pressure settings. The presence of metal in an I.V. line presents possible contamination dangers from corrosion or metallic particles. Elimination of metal springs is therefore highly desirable. Check valves equipped with non-metal resilient sealing elements are designed for a specific opening pressure. The variability of this valve characteristic is therefore not easily achieved.
Most valves that are designed to seal at low pressures, such as disc valves, do not normally allow for high flow or bi-directional flow. Therefore, there exists a need in the industry to provide a check valve that accommodates relatively high fluid flow when unchecked.
Further, some valves with elastomeric elements where fluid flow is arranged to pass through the element itself have a possibility of particulate contamination. Molding of small check valve elastomeric components commonly include small openings for fluid to pass through. Such openings are created by cores of very small dimensions. These core features could be relatively easily damaged and could therefore cause flash and result in small particles of flash potentially breaking off and contaminating the fluid flow.
Therefore, it is an object of this invention to provide an improvement which overcomes the aforementioned inadequacies of the prior art devices and provides an improvement which is a significant contribution to the advancement of the check valve art.
Another object of this invention is to provide a check valve employing an elastomeric valve element that is economical to manufacture and assemble to achieve valves with different possible cracking pressure.
Another object of this invention is to provide a check valve that allows bi-directional high fluid flow when cracked.
Another object of this invention is to provide a check valve that maintains a seal when checked even at very low back pressures.
Another object of this invention is to provide a check valve that maintains a seal when checked even at high back pressures.
The foregoing has outlined some of the pertinent objects of the invention. These objects should be construed to be merely illustrative of some of the more prominent features and applications of the intended invention. Many other beneficial results can be attained by applying the disclosed invention in a different manner or modifying the invention within the scope of the disclosure. Accordingly, other objects and a fuller understanding of the invention may be had by referring to the summary of the invention and the detailed description of the preferred embodiment in addition to the scope of the invention defined by the claims taken in conjunction with the accompanying drawings.


An attitude control device for an in-space propellant depot. A propellant height sensor generates a measured propellant height. A sloshing frequency calculation unit calculates a sloshing frequency based on the measured propellant height. An attitude angle sensor generates a measured attitude angle. A frequency analysis unit generates a plurality of frequency spectra of the measured attitude angle. A dominant flexible mode calculation unit calculates a dominant flexible mode based on the plurality of frequency spectra. A modal coordinate calculation unit calculates a modal coordinate of the dominant flexible mode. A control torque parameter generator calculates a control torque parameter minimizing spectral amplitude of the plurality of frequency spectra. A control torque generator calculates a term of a control torque until the spectral amplitude of the plurality of frequency spectra no longer exceeds a predetermined value.

The present invention relates to an attitude control device for in-space propellant depot that controls an attitude angle of an in-space propellant depot while suppressing a disturbance torque such as the one due to solar radiation pressure.
In-space propellant depots are generally represented as a nonlinear time varying system with nonlinearlity of its mechanical structure and time-varying inertial moment due to sloshing of propellant, and exhibit subharmonic resonance, superharmonic resonance and parametric resonance together with primary resonance when exposed to the disturbance torque containing a frequency near a resonance frequency of the in-space propellant depots.
U.S. Pat. No. 7,957,854 B2 discloses an active vibration damping system for precision pointing spacecraft that identifies a plurality of system parameters in a transfer function of a spacecraft characterizing dynamics thereof applying a known excitation signal, and generates a control torque for suppressing a vibration of the spacecraft using a reaction wheel based on the plurality of system parameters identified.
The prior art in U.S. Pat. No. 7,957,854 B2, if applied to an in-space propellant depot as in U.S. Pat. No. 7,575,200 B2, introduces undesirable vibration of frequencies near resonance frequencies other than primary resonance frequencies of the in-space propellant depot, and thus fails to suppress effectively the vibration induced by the disturbance torque as a result of its negligence of a plurality of types of resonance causing the vibration.

Attitude control device for in-space propellant depot


A joint fitting for a vehicle seat with a forward tiltable seat back. The joint fitting has a first fitting part, a second fitting part and a pivot joint pivotally joining these two fitting parts. A locking cam is hinged to the first fitting part and is pivotal about a cam axle, the locking cam has a first end region located in proximity to the cam axle and a second end region. A locking bight is configured on the second fitting part and is provided with a first locking side and with a facing second locking side, the distance between these locking sides matching the distance between the two end regions. An actuation device acts on the locking cam at a distance from the cam axle so that the locking cam may be moved from a locking position into a release position. In the locking position, the first end region of the locking cam abuts on the first locking side and the second end region of the locking cam abuts on the second locking side.

The invention relates to a joint fitting intended for use in a vehicle seat with a forward tiltable seat back which is provided with a first fitting part, a second fitting part and a pivot joint by way of which said two fitting parts are pivotally joined together.
In automotive vehicles with only two side doors in particular, the front seats usually have a forward tiltable seat back in order to facilitate access to the rear seats. Prior art joint fittings of the type mentioned herein above are described in DE 28 29 701 A, U.S. Pat. Nos. 4,269,446, 6,030,042 for example and have a hook hinged to the one fitting part, with said hook cooperating with a bolt provided at the other joint portion. After the hook is detached from the bolt, the fitting parts may be pivoted relative to each other about the hinge axle. As a result thereof, the seat back may be tipped forward. On tilting it back again, the movement is limited by a mechanical stop located between the first and the second joint fitting. Once this stop is reached, the corresponding angular position is secured between the two fitting parts by hooking said hook up onto the bolt.
Additionally, this type of vehicle seats also has a fitting that permits to adjust the inclination of the seat back relative to the seat carrier. The adjustment of this fitting requires quite a lot of time, though. The joint fitting of the type mentioned herein above permits to achieve a quick adjustment by a greater angle, e.g., 90xc2x0.
The previously known joint fitting is clearance-free because the hook contacts the bolt alongside a hook surface which, as the hook is increasingly pivoted about the bolt, increasingly pulls the bolt toward the pivot axis of the hook.
Normally, the hook is in its locking position. The hook is allocated an elastic means that biases said hook in the locking position. There is provided a traction means that acts on the hook and allows the hook to pivot out of its locking position against the action of the elastic means. The traction means ends in a handle which usually is located in the upper region of the seat back, on the side thereof. By actuating the handle, the hook is pivotally released for a quick adjustment of the seat back.
Said previously known joint fitting has proved its worth. In the known embodiments of the joint fitting, the paths on which the support is carried out are quite long. Accordingly, the lever arms are relatively large.
This is where the invention comes to bear. It is an object of the invention to indicate another construction of a joint fitting, in which the paths for support are short in the locked condition, which is of a compact design and in which the pivot bearing of the part responsible for the locking needs not be used to assist in providing compensation for play.
The solution to this object is embodied by a joint fitting intended to be used in a vehicle seat with forward tiltable seat back which is provided with a first fitting part, a second fitting part and a pivot joint by way of which these two fitting parts are pivotally joined together, said joint fitting being further provided with:
a locking cam pivotally hinged to the first fitting part about a cam axle and having a first end region located in proximity to the cam axle and a second end region located opposite to the first end region,
a locking bight configured on the second fitting part and provided with a first locking side and with a second locking side facing the first looking side, the distance between said locking sides matching the distance between the two end regions, and
an actuation device acting on the locking cam at a distance from the cam axle for moving the locking cam from a locking position in which the joint fitting is blocked into a release position,
wherein in the locking position the first end region of the locking cam buts on the first locking side and the second end region of the locking cam abuts on the first locking side and the second end region of the locking cam abuts on the second locking side and a circle having the pivot joint for center and passing through the cam axle intersects the first locking side, the second locking side being inside said circle.
In this joint fitting, the locking cam forms the stop needed to limit the return movement when the forward tipped seat back is reclined backward. Accordingly, a separate stop as it is provided with the prior art joint fitting is not necessary.
On the other side, in the locking position, the locking cam positions itself with its two end regions lying between the two locking sides of the locking bight. The locking cam, whose function is similar to that of the hook in the joint fitting of the art, not only provides fixation in one pivotal direction, but in the two possible pivotal directions of the seat back. As a result thereof, the pivot axis, i.e., the cam axle, is virtually not loaded, no clamping forces being at any rate introduced into the other fitting part via the cam axle, as this is the case with the prior art fitting. The first locking side may be located in immediate proximity to the cam axle so that the bearing of the locking cam may be simple. The clamping forces are generated by the end regions of the locking cam directly contacting the associated locking sides. In this locking position, the cam axle is no longer needed. It is needed to transmit the force and to move the locking cam into the release position and from there back into the locking position, but not for the locking process itself.
A clearance-free joint fitting is achievable by simple means. As compared to the prior art joint fitting, less parts are needed. Locking is performed with greater accuracy. As a result thereof, the transmission of the joint position of the joint fitting of one seat side to the joint fitting of the other seat side is facilitated and more accurate.
In a prior art joint fitting, the hook is the pivotal locking means. In the locking condition, the hinge axle of said locking means is pulled toward the locking region. With the joint fitting in accordance with the invention, the process is exactly reversed. In the locking condition, the free end of the locking cam pushes the pivot joint away. Since however, a support in the form of the end region located there, i.e., of the first end region, and of the first locking side is located in immediate proximity to the pivot joint, what determines the locking position is not the hinge axle but the fit of the locking cam and of the locking bight.
A circle having the pivot joint for center and passing through the cam axle also intersects the first locking side but remains outside of the second locking side. As a result thereof, the locking cam remains outside of the circular movement described by the second locking side and, more generally, by the locking bight when the seat back is tipped forward. On tilting it back, the first end region abuts on the first locking side, thus forming the described stop for the return movement.
Like in prior art, an actuation device is provided. But now, said actuation device acts onto the locking cam. Normally, the locking cam is in the locking position. By actuating the actuation device, it is pivoted from the locking position into the release position. As a result thereof, it is possible to quickly tilt the seat back forward.
In a preferred development, a torsion bar is arranged on the locking cam, said torsion bar elastically biasing said locking cam in one direction of rotation, which is opposed to the direction of rotation on tilting the seat back forward. As a result thereof, said torsion spring always loads the locking cam relative to the first fitting portion in the locking position and maintains it.
In a preferred development, on tilting the forward tipped seat back backward, the first contact occurs between the first locking region and the first locking side in one point of the first end region which is positioned in such a way relative to the cam axle that a pivoting moment is applied. Accordingly, the first contact causes the second end region to be moved toward the second locking side.
In a further improvement, it is suggested that the first locking side is oriented on a portion of a straight line that passes through the hinge axle. This permits to achieve precise abutment when the seat back is tilted back.
In an advantageous development, the actuation device has a control part which is hinged to the second fitting part. There is provided a traction means which is more specifically configured as a Bowden cable and allows the control part to pivot from its position of rest into a release position. The control part has a release arm that pushes the control cam from the locking position into the release position as the traction means is actuated. The locking cam is actuated in this manner. Although it is possible, in principle, to actuate the locking cam directly, the actuation via the control part has the advantage that the traction means can act on a part that moves together with the same fitting part as the handle of the traction means. Accordingly, it is not necessary to arrange the traction means in such a manner that no pull is exerted onto the traction means when the seat back is pivoted.
In another development, the control part has a retaining lug which engages behind a blocking side of the locking cam in the position of rest of the control part. In this way, the locking cam is mechanically blocked. It cannot be pushed out of the locking position, not even by acceleration forces acting onto the locking cam.

Joint fitting for a vehicle seat with a forward tiltable seat back


A wireless communications device may include a receiver configured to receive a continuous phase modulation (CPM) signal and a demodulator coupled downstream from the receiver. The demodulator may be configured to generate a CPM correlation matrix based upon an expected CPM signal, and generate a temporary correlation matrix. The temporary correlation matrix may include a first copy of the CPM correlation matrix inverted in time, and a second copy of the CPM correlation matrix.

Continuous phase modulation (CPM) is a widely used modulation format. For example, the global system for mobile communications (GSM) uses the gaussian minimum shift-keyed (GMSK) modulation format that is based upon frequency, phase, gain/amplitude, and timing recovery feedback loops to achieve a theoretically optimal bit-error rate (BER) performance. Although computationally intensive, a CPM signal may be demodulated with a non-coherent decoder, and may still match the optimal coherent bit error rate. Ultra high frequency (UHF) satellite communications (UHF follow-on (UFO) SATCOM) may severely distort the transmitted signal, thus causing increased loss in power efficiency or bit error rate performance.
Non-coherent decoding of CPM signals typically requires correlation banks that are matched to the expected I&Q signal values over several symbol periods. The received signal is compared to each possible valid combination of symbols across multiple symbol periods. The best correlation may indicate the most likely symbol transmitted. U.S. Pat. No. 7,636,399 to Brown et al. discloses a non-coherent receiver comprising a bank of CPM waveform matched filters for obtaining branch metrics for each consecutive CPM symbol. The device also includes a recursive inner decoder cooperating with the bank of filters.
Non-coherent CPM decoding is based upon the phase being continuous throughout the multi-symbol correlation process. This may not match the definition of traditional "non-coherent" demodulation. Thus, another more appropriate term may be "quasi-coherent." This multi-symbol correlation process may not be based upon the receiver recovering the transmitted phase of the incoming signal, as is typically performed with a phase-lock loop (PLL). A receiver that generates a copy of the transmitted carrier frequency and phase is typically defined as a coherent receiver.
Some communications modes use a burst/packet communications waveform and operate in a harsh interference environment, for example, for communications over a satellite channel. Due to the nature of these communications modes, a coherent receiver may be increasingly difficult to design, as it is typically difficult to recover the transmit carrier frequency and phase.
Accordingly, a receiver that operates in such modes may use the quasi-coherent CPM demodulation technique. However, the distortion and intersymbol-interference induced by a satellite channel, for example, a 5 kHz UHF satellite channel, generally causes an irreducible bit error rate (1E-4 for a FSK receiver, 1E-5 for a non-coherent CPM receiver).
A standard for UHF satellite communications (Integrated Waveform) includes CPM modems that may be used on UHF satellite transponders. IW supersedes Demand-Assigned Multiple Access" (DAMA) MIL-STD-188-182 (A), MIL-STD-188-183 (A) military interoperabilty standards for UHF Follow-On (UFO) Satellite Communications. IW is described in MIL-STD-188-181C, MIL-STD-188-182B, and MIL-STD-188-183B interoperability standards. There are two transponder types that are designed to support two channel bandwidths—25 kHz and 5 kHz.
To meet the bit error rate requirements, terminals or receivers may use least mean square (LMS) equalization. LMS equalization uses an error calculation that is based on the difference between the expected received signal and the actual received signal. If the expected received signal that is generated for this difference does not account for the carrier frequency and phase, or the actual received signal is not modified to remove the carrier frequency and phase offset, the LMS receiver attempts to remove the carrier frequency and phase because it will see it as an error.
Unfortunately, for UFO satellite communications, the LMS linear equalizer cannot simultaneously adequately address both the inter-symbol interference (ISI distortion) caused by the satellite channel and the carrier frequency and phase offset. An LMS equalizer will attempt to adapt to any channel impairment, with some loss due to the inability of a linear filter to accurately model a satellite channel with both linear and non-linear impairments. An LMS equalizer will also attempt to remove phase, frequency, timing, and any other error. However, it is increasingly difficult to measure error in an LMS equalizer.
Error is defined as any difference (typically complex-valued in-phase and quadrature) between the received signal and the expected/desired signal. Thus, a received signal with a frequency offset may appear as an error to the least-mean-squares error calculation and the linear filter that is at the receiver to be used to approximate the channel. This linear filter typically has coefficients that are modified using the LMS coefficient calculation to remove the frequency error. Typically, frequency, phase, and timing errors are not expected, but rather they are known ahead of time.
U.S. Pat. No. 7,088,793 to Mickelson et al. discloses an equalizer for use with complex modulation modems to reduce inter-symbol interference. The equalizer includes an equalizer filter that receives an input data signal and adapts the input signal to compensate for the noisy communications channels to reduce inter-symbol interference. A branch metric computer demodulates the equalizer filter adapted input data signal.

Wireless communications device having temporary correlation matrix with time inversion and related methods


In one embodiment, a method includes determining if a power load requirement associated with a server arrangement is below a threshold. The server arrangement includes at least a first power supply and a second power supply, as well as a capacitor arrangement. The method also includes providing power to the server arrangement using the first power supply and not the second power supply when it is determined that the power load requirement is below the threshold, and providing the power to the server arrangement using the first power supply and the second power supply when it is determined that the power load requirement is not below the threshold.

Server architectures are typically designed to manage power drawn from power supplies based on application loads. Generally, as an application load is increased, the power drawn by a server architecture is increased. Conversely, as the application load is reduced, the power drawn by the server architecture is reduced. When designing a server architecture, servers and their associated power supplies are designed to accommodate peak load estimates. Power supplies used to provide power to servers within a server architecture are often chosen such that a worst case load may be accommodated. For example, blade system power supplies are often designed to support a peak power draw.
Although server designs are sized based on peak load estimates, many server designs often do not operate at or near their peak load estimates. That is, many servers operate at relatively low load, e.g., near idle, conditions for a significant portion of time and, thus, power supplies are not often fully loaded. As the efficiency associated with power supplies decreases as the power drawn from the power supplies decreases, when power supplies are operating at relatively low loads for a significant portion of time, the power supplies are operating with relatively low power efficiency for a significant portion of time.
Multiple power supplies are often used to deliver power within a server architecture, and to share the load substantially equally. While substantially equal load sharing amongst multiple power supplies may enhance the reliability and availability of a server design, efficiency with which power is used may be reduced, as the efficiency associated with a power supply generally decreases as the load or power drawn from the power supply is reduced. Thus, when multiple power supplies are equally sharing a load and are each operating at relatively low loads, the delivered efficiency is compromised.

Method and apparatus for providing power to a server platforms by using a capacitor to provide power during a second power supply transitioning on


A main shaft includes a plurality of elastic engagement pieces arrayed along an outer perimeter of an attachment hole. During and after assembly, the elastic engagement pieces elastically abut at least an outer surface of a tapered shank in a tool holder and deform slightly in a radial direction. The elastic engagement pieces provide uniform engagement force between the main shaft and the tool holder over a broad surface area. An elastic flange provides additional elastic engagement and easy separation from the main shaft. Together, the elastic engagement pieces and elastic flange reliably engage and securely attach the main shaft to the tool holder while aiding disengagement.

1. Field of the Invention
The present invention relates to a tool holder that reliably secures a tool along a main shaft of a machine tool.
2. Description of the Related Art
Conventionally a tool holder is attached to the end of a main shaft to support a tool. This type of attachment is used in various machine tools including drill presses, milling machines, and machining centers.
With conventional tool holders, a main shaft rotates the tool to perform machining on a workpiece. Since the tool holder is removably attached to the main shaft, the main shaft is equipped with a retraction mechanism to draw in and secure a shank of the tool holder.
Conventional tool holders include a tool support section for attaching a tool, a shank including a tapered outer perimeter surface, a pull stud secured to the shank, and a flange having a larger diameter than the tapered hole.
Conventionally, the retraction mechanism pulls in the tool holder and fits and secures the shank to the tapered hole of the main shaft.
Unfortunately, high machining precision, of 1 micron error or less, is demanded from recent machining tools. During use, machining tools must operate while rotating the main shaft at high speeds of 30,000-40,000 rpm.
Consequently, the tool holder and the main shaft (rotating at high speeds) undergo undesirable rotary vibrations, which are a factor in degrading machining precision.
To minimize precision loss, it is desirable to increase securing strength by tightly securing the entire shank of the tool holder against the tapered hole of the main shaft. Unfortunately, due to machining tolerances in the tapered hole of the main shaft and the tool holder, the tool can heat up during use, resulting in detrimental thermal expansion of both the main shaft and the tool holder. Detrimental thermal expansion makes it impossible to secure the entire shank of the tool holder firmly and tightly against the tapered hole of the main shaft.
It is also impossible to abut the flange of the tool holder tightly to the end surface of the main shaft while having the shank of the tool holder tightly secured in the tapered hole of the main shaft. Consequently, conventional tool holders are not designed to abut its flange on the end surface of the main shaft.
Japanese laid-open patent publication number 8-108302 discloses a tool holder which includes a main holder unit having a shank and a flange. A sleeve is outwardly fitted to the shank so that it can move along an axial direction relative to the shank. The sleeve also has an outer perimeter surface with the same tapered shape as the tapered hole of the shank. An elastic member is interposed between the flange and the sleeve.
The sleeve is divided at one section along the perimeter, with the elastic body mounted in the resulting gap. When the retraction mechanism draws in the tool holder, the flange abuts the end surface of the main shaft. The sleeve is elastically pressed by the elastic member toward the base end of the main shaft. The sleeve is narrowed and engages the tapered hole and couples with the shank.
Japanese laid-open patent publication number 9-248727 discloses a tool holder, formed as described above, but instead of the sleeve with a division at one section, a sleeve with an inner groove at one section along the perimeter is used. With both above-described tool holders, the overall sleeve diameter is narrowed when the retraction mechanism pulls in the tool holder. As a result of this narrowing, the tapered outer perimeter surface of the sleeve cannot be tightly fitted and secured against the tapered hole. This makes it difficult to have a uniform contact force over the entire perimeter and provide secure coupling with the inner surface of the tapered hole. As a further detriment to this design, an increased number of parts is required and the structure is correspondingly complex, thus increasing manufacturing costs.
In a tool holder presented in Japanese laid-open patent publication number 7-96437, a ring-shaped groove is formed at the boundary between the shank and the flange. The ring-shaped groove allows a section of the flange to have a reduced thickness. When the tool holder is drawn in by the retraction mechanism, the flange abuts the end surface of the main shaft and is elastically deformed slightly, and acts as a disc spring. This mechanism engages the shank and the tapered hole. Unfortunately, the structure of the shank is the same as previous conventional shank structures, and roughly the same problems therefore exist as in conventional tool holders.


The system of the present invention guarantees quality of service with respect to packets transmitted/received between an external network capable of providing differentiated services and a home network. The system includes a packet classifier, a marker, a priority class queue, a scheduler and a token bucket. The packet classifier classifies the packets according to addresses and traffic types. The marker allocates information on priorities to packets transmitted from the home network to the external network. The priority class queue has a plurality of queues classified according to the priorities. The scheduler services packets stored in the priority class queue according to the priorities. The token bucket drops packets, bandwidths of which are above a preset maximum bandwidth, when the packets are generated.

1. Field of the Invention
The present invention relates, in general, to a system and method for guaranteeing quality of service in networks and, more particularly, to a system and method for guaranteeing quality of service with respect to packets transmitted/received between a network capable of providing differentiated services and a home network.
2. Description of the Related Art
Generally, all conventional application programs in the Internet using Internet Protocol (IP) have provided only simple best-effort services. Further, a precedence sub-field and a TOS sub-field exist in a Type Of Service (TOS) region within an IPv4 header so as to provide services corresponding to respective IP datagrams. However, an Internet router providing only best-effort services does not use such sub-field information. Such a conventional Internet environment cannot satisfy various demands of Internet users any longer. Therefore, in order to satisfy the various service demands of Internet users, the provision of a guaranteed Quality of Service (QoS) in the Internet is needed.
Currently, in order to provide various services and guaranteed QoS, various research has been carried out all over the world. The Internet Engineering Task Force (IETF) has introduced various service models and mechanisms providing QoS in response to the demands of the Internet users. For remarkable mechanism of the introduced models, there are Integrated Services (IntServ) and Differentiated Services (DiffServ). The IntServ mechanism reserves end-to-end resources using Resource Reservation Protocol (RSVP) used to reserve resources, and provides QoS to users. However, since the RSVP reserves resources for respective flows, information and states required for resource reservation should be maintained for all flows, so that it is difficult to accommodate the RSVP in a large-scale network. That is, the RSVP is limited in flows, which can be managed by a system on a RSVP path. However, the DiffServ mechanism does not reserve resources for respective flows, but provides differentiated services to users in such a way that, if an edge node classifies data packets according to QoS required by users, a core node of the network differentially processes the classified data packets. Such a DiffServ mechanism improves the priority indication services of IPv4 defined in RFC791, and utilizes basic paradigm capable of providing various QoSs in the Internet using the defined services. Services can be the important characteristics of packet transmission, such as qualitative and statistic periods, throughput, delay, jitter and loss, in a set of one or more unidirectional paths within the network, or can be standardized by relative priorities to access network resources. The differentiation of services is required to allow differentiated prices of Internet services, satisfy various expectations of the users or accommodate different applications.
Services are provided to sets of traffic. For this purpose, a set of useful end-to-end services, which can be required by application programs using specific QoS, is defined in advance in the DiffServ. This set of services is called Per-Hop Behavior (PHB). PHB indicates that resources, such as buffers of routers or bandwidths, are allocated among competing traffic streams. Currently, IETF defines Expedited Forwarding (EF) PHB and Assured Forwarding (AF) PHB as newly differentiated forwarding schemes in a single router, besides default PHB for conventional best-effort services. End-to-end differentiated services are provided by these PHBs and a specific traffic mediator.
In a network providing DiffServ, traffic streams are classified and marked by routers on a progressing path so as to perform a special per-hop transmission. At this time, traffic streams are processed so that traffic control functions, such as complicated classification, marking, policing and shaping, are mainly performed in edges or hosts of the network, and so that input packets are processed depending on contracted services on the basis of marked values within the network. Therefore, the DiffServ mechanism is advantageous in that there is no need to maintain states and information for respective flows in a core portion of the network having a large number of flows. Accordingly, the DiffServ mechanism is advantageous in that the problem of scalability occurring in the IntServ using RSVP can be solved, but it is problematic in that, if the number of users and the amount of traffic flowing into the network increase, a load to be processed by an edge router increases, thus deteriorating the reliability of a QoS guarantee.

System and method for guaranteeing quality of service in IP networks

Electronics and Telecommunications Research Institute


A chain saw chain braking system, positioned in a continuous channel guide through which chain linking elements slide freely during use, unless the slidability is impeded by its operation.

The present invention relates to chain saws, and more particularly to a system and method for applying braking to a cutter providing chain thereof.
Chain saws are well know means for cutting wood and the like and used properly can greatly reduce work, however, if not used carefully user injury can occur. As a result, safety features are desirable. Critical to safety is the capability of a chain saw system to stop a blade or cutter containing chain from moving when its motor is running, but the chain saw is not being applied to useful work. That is, efficient chain saw chain braking systems provide utility. In that light it is generally disclosed at this point that the present invention is a new braking system and method for braking chain saw chain motion.
With an eye to the present invention a Search of Patents was performed. A U.S. Pat. No. 5,101,567 to Cool was identified and describes a braking mechanism (40) and brake lever (42).
U.S. Pat. No. 3,793,727 describes a system in which two handles must be engaged against the chain saw frame to allow the chain to move. If either is released the chains stops.
U.S. Pat. Nos. 4,924,577 and 4,611,410 are included to show that the Chain Guide can be split in a way that allows extending the length thereof by adding sections.
U.S. Pat. No. 5,445,365 to Forderer shows application of a xe2x80x9cdumbellxe2x80x9d element, but its applied as a connection element, rather than a means to line-up ends of a Slit Chain Saw Chain Guide.
Even in view of the prior art, need remains for additional systems and methods to prevent, or stop chain saw chain motion once initiated.
Chain saws are very low torque, but high speed systems that derive cutting ability by generating high chain speed. That is, at a given torque, the cutting power is directly proportional to chain speed. It is therefore common to stall a chain saw in use due to minor chain pinching, taking too big a xe2x80x9cbitexe2x80x9d of, or causing too much force on, an item being cut. A similar result occurs when too high a chain tension is caused to exist, etc. It is this insight which led to the present invention, which is based in the fact that Chain Saws are constructed so that Blade Containing Links in a Chain Saw Chain are slideably mounted in an essentially centrally positioned Continuous Chain Channel Guide in Upper and Lower surfaces of an Elongated Support, via chain link mating elements, such that in use the Blades or Cutters on said chain can be caused to slideably travel in an elongated xe2x80x9ccirclexe2x80x9d around said Upper and Lower surfaces of said Elongated Support. In use the outer Blades or Cutters are caused to contact something to be cut as said Chain is caused to so move. It is also noted that chain saw chains are comprised of links that are interconnected by means such as rivets and that there is some limited lateral xe2x80x9cplayxe2x80x9d possible between links where adjacent Links are so joined to one another.
Now, the present invention innovation, in its preferred embodiment, involves cutting a Slit into the Continuous Chain Channel Guide Upper or Lower surface, (typically the Upper surface near an oil entry port), so that the centrally located Channel region on one side of the resulting Slit can be, when desired, dislocated with respect to the centrally located Channel region on the other side of said Slit.
The purpose is that so, in use, when it is desired to stop the Chain Saw Chain from moving, causing or allowing the identified central Channel dislocation causes spread of adjacent Chain Saw Chain Links, elements of which adjacent Links then collide with edges of a dislocated central Channel region. This, in combination with general frictional interaction caused between the chain and offset channel regions, one side of said Slit to the other, provides effective xe2x80x9cBrakingxe2x80x9d, thereby causing the chain saw chain to stop motion.
The preferred embodiments provide for the natural positioning of the centrally located Channel region in one resulting side of the cut Upper or Lower surface of the Elongated Support to be dislocated, (ie. not aligned), with respect to the centrally located Channel region in the other side, such that a User must apply central Channel region aligning force to position the centrally located Channel regions on both sides of the Slit to be aligned, thereby allowing the Blade Containing Links in the Chain Saw Chain to slideably travel in an elongated xe2x80x9ccirclexe2x80x9d around said Upper and Lower surfaces of said Elongated Support.
A preferred embodiment provides for a Dumbell shaped element to effect the alignment of centrally located Channel regions by a User applied force which causes said Dumbell element to move from being positioned on one side of the Slit to a position where it straddles the Slit.
One embodiment provides that the Elongated Support be cut in two places, thereby providing a segment thereof which can be positioned such that the centrally located Channel therein is caused to misaligned with centrally located Channel regions on either side of the two slits.
More precisely, the preferred embodiment of the present invention is a chain saw comprising a motor inside a housing, a blade or cutter providing chain saw chain comprised of links which include chain link mating elements, and an elongated support extending outward from inside said housing, said motor and chain saw chain being functionally interconnected such that operation of said motor applies motion producing force to said chain saw chain. While not of Patentable importance to the present invention, it is noted that the motor and chain saw chain typically are functionally interconnected inside said housing by a sprocket means which is affixed to the motor and engages the chain. Continuing, the outer perimeter surface of said elongated support has present an essentially centrally positioned continuous chain channel guide into which said chain link mating elements slideably insert. As with any conventional chain saw, during normal operation wherein the chain saw is used to cut such as wood etc., said chain link mating elements slide essentially freely through said continuous chain channel guide when forced to do so by operation of said motor. A distinguishing attribute of the preferred embodiment of the present invention, however, is that in a present invention chain saw the continuous chain channel guide has at least one slit present therein which allows effecting an offset of said continuous chain channel guide from one side of the slit to the other, said offset, when caused to be present by an operator, serves to impede the free slide-ability of chain link mating elements across said slit, and in combination with other caused friction based braking effects, prevents in the first place, or stops a chain saw chain""s motion.
Again, preferred practice is to have the continuous chain channel guide be in an offset position, from one side of a slit to the other, unless a user purposely, by definite positive action, causes it to be aligned by the operation of an a continuous chain channel guide alignment means, thereby providing a chain saw which impedes the slideability of chain link mating elements across said slit until desired, and specifically effected by a user, and the preferred continuous chain channel guide alignment means is a dumbell shaped element slideably mounted in the elongated support, such that in use said dumbell shaped element causes alignment of the continuous chain channel guide means from one side of the slit to the other, when caused to be located so as to span said slit.
In a modified embodiment the present invention provides that there be a second slit in said continuous chain channel guide which allows effecting an offset of said continuous chain channel guide from one side of said second slit to the other.
Just as for the first slit, preferred practice is to require that said continuous chain channel guide be in an offset position, from one side of said second slit to the other, unless a user causes it to be aligned by operation of continuous chain channel guide alignment means, thereby providing a chain saw which impedes the slideability of chain link mating elements across said slit until desired by a user. While an alignment means which applies to a first slit might be sufficient to align channel regions on either side of two slits, just as for the first slit, when present, the preferred continuous chain channel guide alignment means is a second dumbell shaped element slideably mounted in the elongated support, such that in use said second dumbell shaped element causes alignment of the continuous chain channel guide means from one side of the slit to the other, when caused to be located at and span said slit.
Another modified embodiment of the present invention provides that it is a chain saw comprising a motor inside a housing, a blade or cutter providing chain saw chain comprised of links which include chain link mating elements, and an elongated support extending outward from inside said housing. Again, said motor and chain saw chain being functionally interconnected inside said housing such that operation of said motor applies motion producing force to said chain saw chain. And as before, in the outer surface of said elongated support there being present a continuous chain channel guide into which said chain link mating elements slideably insert, such that during normal operation said chain link mating elements slide essentially freely through said continuous chain channel guide when forced to do so by operation of said motor. Said modified embodiment, however, provides that said continuous chain channel guide has means present therein which allows effecting an impeded chain channel guide, said means which allows effecting an impeded chain channel guide, serving to, when operated, impede the slideability of chain saw chain therethrough. As before, said means which allows effecting an impeded chain channel guide can comprise at least one slit laterally thereacross, but in the modified embodiment comprises any means which allows effecting an impeded chain channel guide, such as at least one collapsible wall region comprised of, for instance, laminations which move when pressure is applied thereto, or perhaps at least one insertional element which is entered thereinto through a means for entering an insertional element, (which means can comprise a separate portion of said wall), or any functionally equivalent means which enables applying friction to a chain saw chain to slow and stop its motion.
The present invention will be better understood by reference to the Detailed Description, in conjunction with the Drawings.
It is therefore a primary objective and/or purpose of the present invention to provide a new braking system for chain saw chains.
It is another objective and/or purpose of the present invention to teach the entering of a slit into an elongated support, in perimeter surfaces of which is located a continuous chain channel guide into which chain link mating elements are slideably inserted.
It is yet another objective and/or purpose of the present invention to teach that the a continuous chain channel guide on one side of a slit should be offset from that on the opposite side thereof, when chain braking is to be effected.
It is another objective and/or purpose yet of the present invention to teach that a preferred continuous chain channel guide alignment means for aligning continuous chain channel guide regions on either side of a slit is a second dumbell shaped element which is slideably mounted in the elongated support.
It is still yet another objective and/or purpose of the present invention to teach the entering of any means which allows effecting an impeded chain channel guide, for use in effecting braking to a chain saw chain which is slideably mounted in said continuous chain channel guide into which chain link mating elements are slideably inserted.
Other objectives and/or purposes of the present invention will be obviated by a reading of the Specification and Claims.


A self-propelled forage harvester is provided having a frame, a chopping drum, an accelerator arranged downstream of the chopping drum and a channel between the chopping drum and the accelerator. The channel has a section in which a conditioning unit or a hollow shell can be selectively inserted. The conditioning unit and the hollow shell are jointly supported on a pivot arm pivotable by way of a displacement drive about a pivot axis running horizontally and transverse to the forward direction. The conditioning unit is mounted on the pivot arm rotatably about an axis parallel to the pivot axis. The conditioning unit cooperates with the frame by way of a positive guide, which has the effect that the conditioning unit rotates about the axis in the same direction as the pivot arm.

Forage harvesters are used for harvesting whole plants or their parts which are picked up from a field by means of a harvester head, pressed together by means of pressing rollers and led to a cutter drum, whose chopping cutters comminute the plants in cooperation with an opposing cutter. Then the comminuted plants or parts are optionally supplied to a conditioning unit and conveyed by an acceleration unit into an ejection chute that loads them onto a transport vehicle. The comminuted plants generally are used as animal feed or for generating biogas.
The conditioning unit generally comprises two or more rollers driven in opposite directions that are pre-stressed against one another by spring force and between which the chopped material is fed. It is required for corn harvesting to beat the kernels contained in the chopped material and improve the digestibility of the feed. Conditioning is not required for grass harvesting, on the other hand, for which reason the rollers of the conditioning unit are either brought into a position in which a sufficiently large gap remains between them, or the conditioning unit is pivoted out of the channel between the chopper drum and the accelerator and a hollow shell is inserted in its place.
Such a forage harvester is disclosed in DE 42 15 696 A1, which is considered class-forming. The conditioning unit is mounted there on a pivot arm, which also supports the hollow shell. The pivot axis of the pivot arm is located above the housing of the accelerator and slightly to the rear of the axis of rotation of the accelerator with respect to the forward direction of the forage harvester. In the non-operating position, the conditioning unit is behind the channel, rising upward toward the rear, between the chopping drum and the accelerator.
In DE 42 15 696 A1, the conditioning unit is moved between its operating position and its non-operating position only about the pivot axis of the pivot arm. In its non-operating position, it projects relatively far backward and upward into the area behind the accelerator and thus requires a considerable space.
The problem underlying the invention is to improve a forage harvester in the sense that the conditioning unit is brought into a space-saving position in its non-operating position.

Forage harvester with a conditioning unit movable between an operating position and a non-operating position