An expanding gate valve assembly which includes a gate, a stem for actuating the gate, a segment mounted on one side of the gate, or in an alternate, bidirectional embodiment, two segments with one segment movably mounted on each opposite side of the gate for movement toward seating surfaces within the valve body. Each segment carries two spaced, parallel wedging-camming surfaces which are of a configuration to cooperate with complementary spaced, parallel wedging-camming surfaces on the gate to effect lateral expansion of the segment or segments during closure or opening of the valve. The spacing of the wedging-camming surfaces or legs is such that the movable segments are stably supported during their expansion movement.

Brief Description of the Prior Art
Heretofore, many through-conduit gate valve assemblies with expanding gates have comprised a gate having a female V-surface formed in the upstream side of the gate and having a floating segment mounted on the gate, and carrying a complementary male V-surface which engages and coacts with the female V-surface on the gate. The described gate assembly is positioned adjacent seating surfaces within the valve body, and the gate assembly generally moves in a direction perpendicular to the conduit axis (direction of fluid flow through the valve) and parallel to the seating faces. Sealing during opening and closure is effected by the segment being wedged outwardly from the gate in a direction perpendicular to the axis of the stem to effect sealing engagement with the seat faces. Such expanding gate valves may have the gate formed integrally with the stem, or the gate may be connected to the stem with a floating connection, or the gate may be threadedly connected to the stem.
In expanding gate valves of the type described, movement of the gate in a direction normal to the conduit axis brings the floating segment into contact with a stop or other interfering structure which arrests further movement of the segment with the gate in a direction normal to the conduit axis. This causes the segment to be wedged outwardly in a movement of gate expansion, so that the segment is brought into sealing contact with the valve seat. Such expansion of the segment along the conduit axis and substantially perpendicular to the stem axis results from the wedging action of the cooperating V-surfaces carried on the segment and on the gate.
The wedging action causing expanding movement of the segment occurs in the fully closed or the fully opened position of the valve, and, as indicated, results from predetermined, selectively located fixed stops, such as parts of the valve body, which are interposed in the path of movement of the segment as it moves with the gate. These stops arrest further movement of the segment in a direction parallel to the axis of the gate stem. When the gate is moving between the open and the closed positions, the segment is caused to collapse upon, or nest with, the gate as a result of the complementary interfitting of the engaged V-surfaces.
In order for the valve to be smoothly and easily operable, and to avoid damage to the valve stem or gate, it is essential that the wedging action of the gate segments occur in only the open and/or closed positions, and that the segment remain in the collapsed condition when the gate is moving between the open and closed positions within the valve body. This prevents unnecessary dragging or binding of the gate assembly against the valve seat faces at a time when the high integrity sealing is not required. Moreover, any pre-expansion of the segment during travel, also referred to as back-wedging, may result in excessive torque being applied to the stem in order to operate the valve, thereby causing the valve assembly to jam, or even causing twist-off and failure of the stem.
In a gate assembly in which the gate is connected to the stem with a floating connection, for example, with a T-head, both the gate and the segment expand axially along the conduit (fluid flow) axis at the time of closure and opening of the valve. When the gate is of a non-floating type, however, because of a rigid connection between the gate and the stem, only the segment can expand upon closure and opening of the valve. The restraint of the stem prevents the gate from moving in an axial direction.
As a result of such stem restraint, a bending moment is created on the stem in the plane encompassing its axis and the conduit axis (i.e., in the direction of fluid flow). This makes the valve more difficult to operate, and presents the possibility of jamming the valve assembly. When the load on the gate and stem is relieved, the fluid pressure in the conduit, acting on the segment and aided by centralizing levers and/or torsion springs, often employed in expanding gate valves of the type described, forces the segment to nest or collapse into the gate, thus relieving the pressure on the seat faces. The gate assembly can then travel between the position of opening and closing without dragging or binding due to unnecessary contact with the seat faces.
If the fluid pressure in the conduit on the downstream side of the gate assembly (the side opposite the side of the gate which carries the wedge), should build and act with excessive back pressure on the gate, the nesting or collapsing ability of the gate assembly becomes impaired, thereby causing problems as a result of back-wedging or pre-expansion of the segment. The valve consequently becomes very difficult to operate, and in extreme cases, cannot be operated at all.
For the described reasons, the expanding gate valve assembly having a single V-surface on one side of the gate for the accommodation of the V-shaped male protuberance on the wedge is a unidirectional assembly, and can be mounted in the valve body for operation in only one direction of fluid flow. In other words, the wedge must be located on the upstream or high pressure side of the valve gate in order for the gate assembly to function.
In most prior art expanding gate valve assemblies, the V-surfaces formed in the gate, and projecting from the wedge, have generally consisted of two intersecting inclined surfaces forming a single "V", and the "V" has been formed to a location relatively deep in the gate in order that there is adequate contact surface between the intersecting V-surface on the wedge, and the intersecting V-surface on the gate. Such adequate contact surface provides some stability to the wedge as it moves to its sealing position. The necessity for this relatively large surface area of contact between the wedge and the gate at the interacting V-surfaces has made it necessary to make the gate relatively thick in a transverse sense. Such greater gate thickness, of necessity, causes the valve body chamber to be larger, thus resulting in a larger overall valve assembly. This, in turn, results in increased manufacturing cost for the valve.
Expanding gate valves of the type described, having a gate with a movable segment mounted thereon are shown in U.S. Pat. No. 4,189,127; U.S. Pat. No. 4,531,710; U.S. Pat. No. 4,179,009; U.S. Pat. No. 4,188,014; U.S. Pat. No. 4,188,016; U.S. Pat. No. 4,279,404; U.S. Pat. No. 4,341,369; U.S. Pat. No. 4,334,666; U.S. Pat. No. 3,823,911 and U.S. Pat. No. 4,530,488.
In substantially all expanding gate valves as they are presently constructed, the angle .alpha. which is included between the V-surface and the axis of the stem (the direction of opening and closing movement of the valve gate) is generally of a magnitude of between about 10.degree. and about 18.degree.. As the magnitude of the angle .alpha. is decreased, the ease with which the segment can collapse into the gate following opening and closing is reduced, but a lower operating torque is required to open and close the valve. Conversely, the larger the angle .alpha., the more readily and easily the wedge will collapse into the gate following opening and closing of the valve, but a higher operating torque is required in order to open and close the valve. Moreover, the thickness of the valve must be increased in order to accommodate the single V-notch cut to a deeper location within the gate to afford adequate surface area of contact between the wedge and the gate to stabilize and evenly support the wedge in its expanding movement.
A gate valve is disclosed in Trowe U.S. Pat. No. 1,521,531, and this valve includes two axially movable wedge-shaped segments or valve discs which are caused to move outwardly by a threaded shaft which, when turned, causes an upward movement of a wedge nut. This wedge nut can only be accommodated in its upward movement by an upwardly yielding movement of a wedge member. In other words, the wedge nut, as it moves upwardly, carries with it a wedge member. The wedge nut forces this wedge member upwardly along the axis of the threaded shaft, and as the wedge member moves upwardly, the two opposed valve discs are forced outwardly away from the gate.
The only inclined wedging-camming leg or surface present in the structure of the Trowe valve is the interface of each of the valve discs, each of which, the patentee states, is at a slight inclination to the outer face. It is these inclined faces, however, upon which the wedge member acts during the operation of the valve. The threaded shaft is not touched by the inner inclined interface of either valve disc at any time during operation of the valve. In the Trowe structure, there is actually no gate which corresponds to the gate of this present invention, as such gate coacts with movable segments which are moved out against seats. Rather, there is only the threaded shaft which causes the up-and-down movement of the wedge nut which moves upwardly and downwardly along the axis of the threaded shaft. This action by the wedge nut in turn forces the valve discs outwardly into sealing contact with valve seats disposed on opposite sides of the cavity centrally located in the valve body. While it appears that the valve discs are screwed downwardly as the nut and wedge member are moved upwardly, this downward movement of the valve discs on the threaded stem or gate has nothing to do with the concurrent outward movement of the valve discs. This is caused by, and results solely from, the upward movement of the wedge member.
The handle, stem and other operator devices used in the Trowe patent gate valve are also complicated. A first linkage must be initially manually actuated up or down in order to physically displace, by reciprocation, the entire stem, the threaded shaft, the wedge nut, wedges and valve discs. Once they have been moved up or down into a position where this entire assemblange of multiple elements closes the fluid flow passageway across the valve in a gross or general sense, sealing is then next effected by rotation of an elongated valve stem shaft which passes through a collar carried by the manually actuated linkage previously used. There are thus two operators provided in the Trowe valve with these operators being manually manipulated at two different times during the opening, closing and sealing of the valve.
The gate valve shown in Ladd U.S. Pat. No. 880,674 also has a sequentially manipulated compound operator system. A manually operated linkage is first used to move the entire stem up or down, and with it, the multiple part valve mechanism. After this, the elongated valve stem is rotated about its longitudinal axis to set the valve into a sealing mode. Two discs are located on opposite sides of the threaded shaft or rotatable stem, which is itself reciprocated within the valve body. The patentee refers to these discs as "gates". These "gates" are caused to move in a divergent fashion concurrently with the convergence toward each other of a pair of spreading blocks. As these spreading blocks are moved toward each other by the interaction of the two blocks with oppositely pitched threads formed on the rotatable stem, the two wedge blocks, or spreading blocks, force the so-called gates away from each other on opposite sides of the valve cavity. They are ultimately forced into sealing contact with the seats as a result of the movement of the wedge or spreading blocks toward each other.
As the spreading blocks move toward each other, the inclined planes formed by one frustoconical surface on each spreading block forces a gate segment out into sealing contact with a corresponding seat in the valve body. When the stem is rotated in the opposite direction, the spreading or wedging blocks are moved away from each other. This releases the gates which then unseat and allow the entire stem to be reciprocated upwardly within the valve by means of the extra handle or operator first mentioned above. This upward movement continues until two gates and the cooperating spreading blocks are moved upwardly into the bonnet of the valve, and thus clear the fluid flow passageway through the valve. There are thus no segments in the Ladd valve which are forced by moving, inclined, spaced, wedging-camming legs or surfaces carried on the gate or the stem itself so as to move into sealing contact with seats in the valve body.
In U.S. Pat. No. 4,405,113 to Erwin, a reciprocating expandable gate valve is disclosed. This gate valve has a first main stem which moves the entire multiple part gate as a unit in reciprocation upwardly and downwardly with respect to the fluid flow passageway, or stated differently, transversely across the valve body.
The main stem further has coaxially aligned therewith, a cam drive shaft having first and second oppositely threaded sections which function to respectively engage the main stem and a central gate block. The central gate block carries a plurality of cam surfaces thereon. These cam surfaces are contiguous to each other, and they cooperate with seal blocks which also carry cooperating contiguous cam surfaces which interfit with the cam surfaces on the gate block. The seal blocks are moved outwardly as a result of movement of the central gate block, and the coaxial cam drive shaft is moved by rotation of this shaft after the entire valve assembly has been placed across the fluid flow passageway. The cam surfaces formed on the gate block consist of a plurality of contiguous saw-tooth indentations or triangular steps in the gate block which cooperate with complementary cam surfaces on the seal blocks. The complicated compound or dual stem structure disclosed in this patent is the mechanism by which the upper central gate block is caused to undergo a reciprocating up-and-down movement within a certain limited range previously established by rotation of the main stem to set the gate into position within the valve body.
The canted planar camming surfaces which are carried on the central gate block of the Erwin patent are arranged in a saw tooth array. Each camming surface is immediately contiguous to an adjacent camming surface, and each is defined as a triangular protuberance which includes an acute angle. There are no spaced wedging-camming surfaces having a substantial intervening surface therebetween, and placing the wedging-camming surfaces at a significant distance from each other. Moreover, there is no obtuse angulation, but there is rather an acute angle, formed between any of the contiguous wedging-camming surfaces carried on the gate block.
There are a pair of well spaced, wedging-camming surfaces carried on the gate and segment in the present invention. Therefore, balancing and two point support of the segments, which are in contact with the spaced wedging-camming surfaces at all times during expansion of the segments, assures that such segments will always seat squarely against the seat after they have been wedged outwardly by the wedging camming surfaces with which they are in contact. In other terms, the segments do not rock or cant during their sealing movement, but rather move smoothly and evenly against the seat.
The spacing of the two parallel wedging-camming surfaces or legs in the present invention is by a distance which is at least ten percent of the distance across the fluid flow passageway through the valve, and which is to be sealed, and such spacing distance is preferably at least a major portion of the distance across such fluid flow passageway. In most applications of the invention, the distance across the fluid flow passageway can also be equated to the inside diametric distance across the annular seating surface positioned within the valve body adjacent the central cavity in the valve body and extending around the fluid flow passageway. Described in yet another way, the wedging-camming surfaces on the gate are spaced from each other by a distance such that, at the time the segment is undergoing expansion, it is moved away from the gate so that its sealing face remains oriented in the same angular attitude relative to the seating surface within the valve body against which it is to seal. This orientation, which remains constant, is usually parallel to that seating surface while the segment is being cammed toward it. This assures that there is uniform sealing pressure on the seating surface by the sealing face of the segment when sealing is effected, and the described spacing of the wedging-camming surfaces assures that the necessary stability is realized to accomplish this.
In contrast, in the Erwin patent, there are a series of contiguous, saw tooth-shaped camming elements, with only an acute angle defined at the intersection of each of these camming surfaces. The outer seal blocks, provided as a part of one embodiment of the valve illustrated in the Erwin patent, will frequently ride upon, and bear primarily on, only one or at most two of these triangular camming surfaces. This is because this camming surface is the highest, and projects out further than the others. This relationship will frequently occur simply due to the difficulty of machining precisely identical mating saw-tooth surfaces (of the type shown in the Erwin patent) over all of the gate, and cooperating equally with all the seal block camming surfaces. The seal blocks consequently will frequently ride on, and bear primarily upon, only a single one of the camming surfaces which is higher (that is, projects out further) than the others. It is simply not possible, because of manufacturing tolerances, to predict or reckon which of the triangular wedge teeth will protrude out slightly further than the others. Thus, there will be an unpredictable rocking movement of the gate in relation to the seal block due to this very localized support. By contrast, where there are only two of the well spaced wedging-camming surfaces--spaced transverse to the fluid flow axis--as is true of the invention here under consideration, the two spaced wedging-camming surfaces carried on the gate will always be in mating and supporting contact with two wedging-camming surfaces carried on the segment. Any slight shifting of the segment which is required during sealing will still be accommodated by the two, spaced, parallel wedging-camming surfaces as these are formed on the gate. This allows the segment sealing face to be truly self-aligning with the seat, even where the seat is canted or cocked, either by design or due to manufacturing tolerances, or as a result of extended usage.
Danish Patent 50,251 discloses a gate valve in which the gate remains in one position relative to the fluid flow passageway through the valve body at all times during the operation of the valve. Two segments are carried on the gate and these are threaded downwardly by rotation of the gate until the lower ends of these segments strike a pair of inclined surfaces provided on a pair of wedge elements. These wedge elements are secured to the inner side of the valve body, so that once the segments are screwed down at this location, the lower ends of the segments are deflected outwardly by the wedging action of these inclined surfaces. This outward wedging continues until the segments come to bear against the seats located within the valve body on opposite sides of the central valve cavity.
This action is not caused by any structure carried on the gate, but results instead from the segments being canted or cocked sideways as they come in contact with fixed, or non-moving wedge elements projecting inwardly into the valve cavity from the valve body. Further rotation of the helically threaded gate will ultimately cause the tops of these two segments to also be forced out into contact with the seating surfaces at that location within the valve body. The sealing force applied to the two segments is not even or uniform, and the segments do not move so that their sealing surfaces remain parallel to the seating surfaces carried within the valve body. Neither do they seat with the same force at the same time.
The valve shown in the Danish patent causes inordinately high loading on one, or at most two, threads of the threaded cylindrical gate. Due to the pivoting of the segments at their lower end at the time they encounter the inclined surface on the wedge lugs, the lowest thread on the gate will carry a predominance of the load at that time, thereby causing premature failure of the gate thread at this location.


A depth limiting device for a drill includes a main body, an axial braking structure, and a limited shrinking structure. The axial braking structure is attached to the main body. The limited shrinking structure surrounds a drill rod of the drill, is slidably attached to the main body, and is in a home position or a compressed position. The axial braking structure axially brakes the drill rod such that the drill rod moves together with the depth limiting device. When the drill rod enters into a subject, the limited shrinking structure is pressed against the subject, moves from the home position to the compressed position, and stops the drill rod from entering further into the subject.

Field of the Invention
The present invention relates to a depth limiting device used for a drill and a drill that includes the depth limiting device.
Discussion of the Related Art
A drill is a tool used for drilling a hole in a subject. For example, a bone drill can be used for drilling a hole in a bone in a surgery. When a drill is used for drilling a hole in a bone, a surgical doctor holds the drill and pressurizes for drilling. After the drill breaks through the bone substance completely, the electric drill falls through, and it is often difficult and even sometime impossible for the surgical doctor to stop pressurizing at the same time, so the drill may drill forwards continuously. In the drilling process, damages of tissues may be resulted; and if vessels and nerves existing in the heading direction of the drill are damaged, serious consequences may be resulted. In addition, measurement of the depth of the drilling hole is also needed for determination of a suitable screw after the hole drilling process is finished. Existing drills, however, only have a hole drilling function, so the surgical doctor needs to measure the drilling hole by inserting a depth measuring device in the drilled hole. There is a need for improved drill that will reduce the damages to tissues, vessels, and nerves during the drilling process.


Only a limited number of organic or silicone liquid phase thermal exchange fluid types are suitable for operation over a wide range of hot and cold temperatures and these have an undesirable property of degrading at high temperatures. It is accordingly desirable to subject the thermal exchange fluid to high temperature only to the extent and times required by users. The present invention includes intermittent users which occasionally are required to attain maximum working temperatures at which thermal degradation of thermal exchange fluid occurs at a significant rate and a hot reservoir at the minimum working temperature. A stable heat transfer fluid transfers heat from the hot reservoir to the degradable thermal exchange fluid through a common intermediate heat exchanger. The degradable thermal exchange fluid is heated to a temperature just sufficient to satisfy the maximum current setpoint temperature of the intermittent users by controlling circulation of the stable heat transfer fluid. Lifetime of the degradable thermal exchange fluid is thereby extended without compromising effective heating of the intermittent users.

This invention relates to a system for transferring heat from a hot reservoir to a user by a thermal exchange fluid and having the particular freezer of extending lifetime of the thermal exchange fluid which is thermally degradable.
The invention has particular application to a system of domestic appliances wherein a single liquid phase thermal exchange fluid exchanges heat between the appliances and both a hot reservoir and a cold reservoir. The appliance system combines heating and cooling capability in simple appliance units and accumulates energy at off-peak hours and at low power levels for subsequent rapid release during peak use periods. These and other characteristics of the appliance system are described in more detail in the cited related applications and in the following patents. U.S. Pat. No. 3,888,303 describes a system of houseware units which are connectable to a source of thermal exchange fluid. U.S. Pat. No. 4,024,904 describes a range which exchanges heat between a pot or pan surface and a thermal exchange fluid in a heat exchanger by forced air convection.
Representative conditions to be satisfied by a thermal exchange fluid include a temperature range of -20.degree. F. to 575.degree. F. and a lifetime of more than 25 years without skilled preventive maintenance. The users operate intermittently with infrequent excursions to maximum working temperatures. Several commercial thermal exchange fluid types having generally satisfactory heat transfer characteristics over the cited temperature range have been designed for thermal stability, but even the most stable organic compounds change chemically at high temperatures over long periods. Undesirable effects which result from oxidation, cracking, and formation of higher polymers at high temperatures include vapor loss, viscosity increase and geling, and formation of flow and heat impeding deposits.
Thermal degradation over long periods is estimated conventionally from rates of undesirable effects occuring at higher temperatures over shorter periods. The scaling relation is an Arrehenius equation, D=Ae.sup. E/RT, where the constants A and activation energy E are determined from a range of degradation rates D at temperatures T. Once the constants are determined, degradation rates at lower temperatures are calculated. A representative accelerated test of a thermal exchange fluid is based on measurements over a period of several weeks of degradation products formed at temperatures ranging from about 600.degree. F. to 700.degree. F. At 650.degree. F., the more stable thermal exchange fluids have a degradation rate of approximately 1% per week. Most thermal exchange fluids have an activation energy such that their degradation rate is doubled for every 18.degree. F. increase in temperature. Accordingly, the following annual degradation rates are expected for lower temperatures: 600.degree. F.--6.5%/yr; 550.degree. F.--0.68%/yr. 500.degree. F.--0.056%/yr; 450.degree. F.--0.0036%/yr. At 450.degree. F., the degradation over 25 years is less than 0.1% so that continuous long term operation at such lower temperatures would be satisfactory. For cooking appliances, however, the higher temperatures are occasionally required within the appliance and are useful for compensating for thermal impedances in the system to attain desired high temperatures rapidly. A preferred maximum temperature of the thermal exchange fluid would be between 600.degree. F. and 550.degree. F.


An optical interconnection circuit includes a fixed number (N) of interconnected circuits (C1 to C16). Each circuit has an optical emitter (E1 to E16) and at least one optical receiver (R1, R16). The emitter outputs an optical wavelength which is specific to the circuit on which it is located. An optical coupler (CE) connects the emitter in each circuit to all receivers in the other circuits and each circuit (C1 to C16) has an address for identifying that particular circuit. The value of this address is applied to the emitter to adjust the optical wave length at which the emitter operates.

This invention concerns an optical interconnection system, particularly applicable to the interconnection of several electronic circuit boards to allow them to communicate between each other.
Information exchange in optical form between electronic boards is attractive due to the transmission speed that increases the throughput, and because it eliminates all constraints on distances between boards and is immune to parasites.
Telecommunications links within a campus area**** are served mainly by dedicated Subscriber Connection Units called hubs, located in technical rooms on the sites to be connected. These hubs interconnect subscribers, mostly at 10 Mbits/sec. at the present time, in clusters of 10 to 100 (1 to 16 boards each handling 8 to 16 or more subscribers). Since access technologies are improving, the binary throughput available in practice is tending to increase (proposals for 25, 50 and 100 Mbits/sec.). The effect of this situation is to incite a need for global exchanges in hub back panels, increasing from 300/500 Mbits/sec. (current situation) to 2/10 Gbits/sec. (1995 situation). Induced exchanges take place between hub boards in a manner which is not very predictable (standard implementation); each board can generate up to 500/1000 Mbits/sec at peak flow, and exchanges may be multicast (several boards receiving at the same time). Current implementations (up to 4 Gbits/sec.) prefer "all electric" solutions on bus 1 to N, each board transmitting alone on part of the bus (statically), while all others are listening. The electrical technology can carry between 20 and 50 Mbits/sec. through each connector point, and problems of back panel characteristic impedance become severe as the throughput increases; in practice it is necessary to connect high density miniature connectors with several hundreds of pins, and a large area of copper for implementation of line drivers/receivers.
Technically, the interconnection need is waiting for a renewal of these solutions in the form of an optical emission architecture in the back panel enabling the interconnection of 16 boards, each capable of sending up to 1 Gbits/sec. to one or several other boards at a given instant.


An audio time stretch method and associated apparatus is provided. The method includes steps of calculating an energy level according to amplitudes of a plurality of received data, and determining whether the audio data requires audio time stretch according to the energy level. Audio data with lower energy level and volume are selectively time-stretched to alleviate audio quality degradation.

1. Field of the Invention
The invention relates in general to an audio time stretch method and associated apparatus, and more particularly to a method for audio time stretch by utilizing audio data with low energy and associated apparatus.
2. Description of the Related Art
Internet real-time audio/video transmission techniques, e.g., Voice over Internet Protocol (VoIP), offer people immediate and realistic multimedia services, and are thus one of the most important research and development targets for information technology developers.
In Internet real-time audio/video transmission, a transmitting end samples, digitalizes and encodes audio to be transmitted into a plurality of digital audio data each corresponding to an amplitude sample of the audio. A certain number of audio data are packaged in an Internet packet, which is transmitted to a receiving end. Upon receiving the packet at the receiving end, the packet is de-packetized, decoded and demodulated to the original digital audio data. The digital audio data are digital-to-analog converted to restore the original analog audio data that are then played.
At the transmitting end, each audio data corresponds to a predetermined sampling time sequence. Therefore, at the receiving end, it is essential that the audio data be digital-to-analog converted according to the same sampling time sequence, so as to reconstruct the audio to be transmitted by the transmitting end. In order to perform digital-to-analog conversion according to the predetermined time sequence, the receiving end needs to provide the audio data to the digital-to-analog converting mechanism according to a specific time sequence. However, since the audio data are obtained from the packets, the quality of audio played at the receiving end is undesirably affected in the event that the time sequence of the packets transmitted to the receiving end is irregular.
The time sequence of packets transmitted in the Internet real-time audio/video transmission is in fact affected by various factors, e.g., jitter and clock drift. When the packets are transmitted via the Internet, the packets arrive at the receiving end after being routed through different paths due to Internet protocols, such that the packets do not arrive at the receiving end according to the time sequence based on which they are transmitted—such is referred to as "jitter". Further, different reference clocks utilized by the transmitting end and the receiving end may also lead to differences in the packets transmitted. For example, suppose a packet length according to a predetermined protocol is 10 ms, the transmitting end transmits an audio packet every 10.01 ms, and the receiving end plays a packet every 9.99 ms. In a period during which 100 packets are transmitted, an acknowledgement time difference between the two ends reaches as high as 2 ms—such is referred to as "clock drift".
At the receiving end, in order to provide audio data to the digital-to-analog conversion mechanism according to a predetermined time sequence, audio time stretch is required by the time sequence. When the receiving end fails to in time acquire the audio data from the packets, additional audio data needs to be inserted; in contrast, the receiving end removes/discards a certain amount of audio data when the packets provide more audio data than the receiving end can buffer.
However, inappropriate time stretch may degrade the quality of audio playback such that noticeable audio imperfections are observed by a listener at the receiving end.

Audio time stretch method and associated apparatus


A kitchen trash container system wherein a trash container is covered when it is within a kitchen sink cabinet enclosure and wherein the cover automatically opens when the trash container is caused to move outwardly from the cabinet. A latch type member is positioned at the lower portion of the housing, activation of the latch member by a user causing the trash container to move outwardly from the cabinet along a rail member, the cover portion opening during movement of the trash container. When the trash container reaches its outward extent, the cover is in the full open position and enables trash to be deposited in the container. Thereafter, the user pushes the trash container preferably with a knee back into position within the cabinet, the cover automatically closing on top of the trash container.

1. Field of the invention
The present invention provides a waste collection system wherein a covered waste container is stored in a movable draw-like member positioned within a kitchen sink cabinet and which moves outside of the cabinet upon activation of a switch member by a user, the cover automatically opening as the member moves outside the cabinet.
2. Description of the Prior Art
A typical kitchen sink cabinet incorporates a waste receptacle under the sink. The waste receptacle includes an area in which a waste container is positioned to receive and store accumulated waste. The receptacle is usually mounted on a sliding mechanism such that the user can withdraw the receptacle hands free from the cabinet and place waste in the container. The receptacle can be withdrawn automatically by a user depressing a foot pedal, the pedal in turn controlling a latch member. The trash container is typically not covered, the smells and contamination associated with an open trash container being obvious.
What is thus desired is to provide a kitchen trash container system wherein the trash container is covered when it is within the kitchen sink cabinet and automatically opens when the container is caused to move outward from the cabinet.

Hands free waste container having a closed cover that automatically opens when the container is moved outside its cabinet enclosure


Systems and methods provide automatic messaging to a client on behalf of a healthcare treatment professional by setting up one or more computer implemented agents, each specializing in a disease state, with rules to respond to a client condition; during run-time, receiving a communication from the client and in response selecting one or more computer implemented agents to respond to the communication; and automatically generating a response to be rendered on a client mobile device to encourage healthy behavior.

This invention relates generally to methods and apparatus for communicating health instructions to users.
Healthcare costs around the world have been rising. One reason is that, obesity is common, serious and costly. A Duke University study suggests that by 2030, about 42% of Americans will be obese, which is up from 36% in 2012 and will cost about $550 billion dollars. Even small reductions in obesity prevalence "could result in substantial savings," wrote the authors. Obesity-related conditions increase the odds of heart disease, stroke, type 2 diabetes and certain types of cancer, some of the leading causes of preventable death. In 2008, medical costs associated with obesity were estimated at $147 billion; the medical costs for people who are obese were $1,429 higher than those of normal weight.
Obesity affects some groups more than others. Non-Hispanic blacks have the highest age-adjusted rates of obesity (49.5%) compared with Mexican Americans (40.4%), all Hispanics (39.1%) and non-Hispanic whites (34.3%). Among non-Hispanic black and Mexican-American men, those with higher incomes are more likely to be obese than those with low income. Higher income women are less likely to be obese than low-income women. There is no significant relationship between obesity and education among men. Among women, however, there is a trend—those with college degrees are less likely to be obese compared with less educated women. Thus, education appears to be key. Between 1988-1994 and 2007-2008 the prevalence of obesity increased in adults at all income and education levels.
A government solution has been suggested. For example, a ban on the use of trans fats in NY restaurants has sharply reduced the consumption of these unhealthy fats among fast-food customers. However, the government and regulation may not be the best way to solve the problem.
To treat obesity in a cost effective manner, coordination is needed among different service providers such as dieticians, doctors, and exercise coaches. However, planning information, alerts and reminders may be haphazardly and intermittently distributed to doctors, clinicians, or their staff with existing healthcare appointment and scheduling systems and do not support multi-vendor calendaring system that shares information among the different providers. This occurs in other treatments as well. For example, in the case of a patient scheduled for radiation therapy, an existing system may be aware of a necessary number of appointments and treatment orders, but these numbers typically are not compatible with the (e.g., one or more) treatment plans involved. Consequently, a clinician needs to work out a referral connection manually for each appointment. The existing systems also require manual coordination of appointments with treatment plan goals and treatment plan results which occupies a significant amount of clinician time in gathering, collating and analyzing information.
One way to monitor the impact of obesity is to monitor blood pressure. As discussed in U.S. Pat. No. 6,514,211, three well known techniques have been used to non-invasively monitor a subject's arterial blood pressure waveform: auscultation, oscillometry, and tonometry. The auscultation and oscillometry techniques use a standard inflatable arm cuff that occludes the subject's brachial artery. The auscultatory technique determines the subject's systolic and diastolic pressures by monitoring certain Korotkoff sounds that occur as the cuff is slowly deflated. The oscillometric technique, on the other hand, determines these pressures, as well as the subject's mean pressure, by measuring actual pressure changes that occur in the cuff as the cuff is deflated. Both techniques determine pressure values only intermittently, because of the need to alternately inflate and deflate the cuff, and they cannot replicate the subject's actual blood pressure waveform. Occlusive cuff instruments of the kind described briefly above generally have been effective in sensing long-term trends in a subject's blood pressure, but they have been ineffective in sensing short-term blood pressure variations.
The '211 patent discloses blood pressure measurement by determining the mean arterial blood pressure (MAP) of a subject during tonometric conditions. The apparatus has one or more pressure and ultrasound transducers placed over the radial artery of a human subject's wrist, the latter transmitting and receiving acoustic energy so as to permit the measurement of blood velocity during periods of variable compression of the artery. During compression, the ultrasound velocity waveforms are recorded and processed using time-frequency analysis. The time at which the mean time-frequency distribution is maximal corresponds to the time at which the transmural pressure equals zero, and the mean pressure read by the transducer equals the mean pressure within the artery. In another aspect of the invention, the ultrasound transducer is used to position the transducer over the artery such that the accuracy of the measurement is maximized.


A liquid crystal display device which enables reductions in image sticking and droplet stains caused in production thereof without degradation of properties such as dielectric anisotropy, viscosity, the upper limit of the temperature of nematic phase, and rotational viscosity (γ1); and a method for manufacturing such a liquid crystal display device. The liquid crystal display device is characterized in that a liquid crystal layer containing a liquid crystal composition is disposed between a substrate provided with a common electrode and a color filter layer and another substrate provided with a plurality of pixels each having a pixel electrode, each of the substrates is not provided with an alignment film but provided with an orientation controlling layer composed of at least two polymerizable compounds, each of the pixels has two or more regions having different directions of pretilt, and the liquid crystal composition contains a compound represented by General Formula (I) and a compound represented by General Formula (II).

Liquid crystal display devices have been applied to, for example, clocks and watches, calculators, a variety of measuring equipment, panels used in automobiles, word processors, electronic notebooks, printers, computers, television sets, clocks, and advertising boards. Representative examples of types of liquid crystal display devices include a TN (twisted nematic) type, an STN (super twisted nematic) type, and vertical alignment (VA) and IPS (in-plane switching) types involving use of a TFT (thin film transistor). Liquid crystal compositions used in such liquid crystal display devices need to satisfy the following requirements: being stable to external elements such as moisture, air, heat, and light; having a liquid crystal phase in a wide temperature range mainly including room temperature as much as possible; having a low viscosity; and enabling a low driving voltage. In addition, liquid crystal compositions are composed of several to tens of compounds to adjust, for example, the dielectric anisotropy (Δε) and refractive index anisotropy (Δn) to be optimum to individual liquid crystal display devices.
A liquid crystal composition having a negative Δε is used in VA displays and widely applied to, for instance, liquid crystal TVs. In all types of driving, there have been demands for driving at low voltage, a quick response, and a broad range of operation temperature. In other words, Δε with a large absolute value, a low viscosity (η), and a high nematic phase-isotropic liquid phase transition temperature (TNI) have been demanded. In order to determine Δn×d that is a product of Δn and a cell gap (d), the Δn of a liquid crystal composition needs to be adjusted to be in a proper range on the basis of the cell gap. In addition, a quick response is important in liquid crystal display devices applied to television sets or other apparatuses, which generates a need for a liquid crystal composition having a small rotational viscosity (γ1).
In order to improve the viewing angle characteristics of VA displays, MVA (multi-domain vertical alignment) liquid crystal displays have been widely used, in which protrusions formed on a substrate enable liquid crystal molecules in pixels to be oriented in multiple directions. In MVA liquid crystal display devices, viewing angle characteristics are good; however, there is a difference in the response speed of liquid crystal molecules between part adjacent to the protrusions formed on a substrate and part distant therefrom, and the liquid crystal molecules that are distant from the protrusions and thus show slow response speed cause the response speed as a whole to be problematically insufficient, which results in a problem of decreased light transmittance attributed to the protrusions. In order to overcome this problem, PSA liquid crystal display devices (polymer sustained alignment, including PS (polymer stabilized) liquid crystal display devices) having a different structure from general MVA liquid crystal display devices have been developed as a technique for giving an even pretilt angle in segmented pixels without formation of protrusions, which are not light-transmissive, in a cell. In production of PSA liquid crystal display devices, a small amount of a polymerizable compound is added to a liquid crystal composition, the liquid crystal composition is introduced into a liquid crystal cell, and then an active energy ray is radiated thereto under application of voltage between electrodes to polymerize the polymerizable compound contained in the liquid crystal composition. A proper pretilt angle can be therefore given in segmented pixels; as a result, increased light transmittance leads to an enhancement in contrast, and giving an even pretilt angle enables high response speed (e.g., see Patent Literature 1). In PSA liquid crystal display devices, however, the addition of a polymerizable compound to a liquid crystal composition causes a problem that defective display such as image sticking is caused in active-matrix liquid crystal display devices in which a high voltage holding ratio is required.
Meanwhile, an increase in the size of the screens of liquid crystal display devices causes a great change in a method for manufacturing liquid crystal display devices. In particular, since typical vacuum injection techniques require much time to be taken in a process for producing large panels, production by an ODF (one-drop-fill) technique has been becoming popular in production of large panels (e.g., see Patent Literature 2).
This technique enables a reduction in time taken for injection as compared with vacuum injection techniques and has therefore become mainstream in manufacturing of liquid crystal display devices. A new problem, however, has arisen, in which droplet stains made by droplets of a liquid crystal composition remain in liquid crystal display devices in the form of landed droplets even after the liquid crystal devices have been completed. The term "droplet stains" is defined as a phenomenon in which white stains of a dropped liquid crystal composition emerge in a black display mode. In general, the occurrence of droplet stains depends on liquid crystal materials to be used in many cases, and the cause of it has been still unclear.
A technique for reducing droplet stains has been disclosed; in this technique, a polymerizable compound contained in a liquid crystal composition is polymerized to form a polymer layer in a liquid crystal composition layer, so that droplet stains generated by an effect of an alignment film can be reduced (e.g., see Patent Literature 3). Such a technique, however, has a problem of image sticking caused by the polymerizable compound added to the liquid crystal composition as in PSA liquid crystal display devices, and the effect on a reduction in droplet stains is insufficient. Hence, development of a liquid crystal display device which retains basic characteristics inherent in liquid crystal display devices and in which image sticking and droplet stains are less likely to be caused are demanded.

This patent is subject to a terminal disclaimer.

Liquid crystal display device and method for manufacturing the same


The invention provides a strategy to start a parallel HEV powertrain engine while maintaining a smooth vehicle response to driver demand using the motor while simultaneously closing an engine disconnect clutch. In the preferred embodiment, the strategy starts an engine (based on, for example, driver demand), closes the disconnect clutch, commands a desired motor/generator speed, fuels the engine, calculates a desired engine torque and gradually reduces actual motor/generator torque while proportionally increasing actual engine torque until motor/generator torque is zero while maintaining vehicle velocity using, for example, a proportional plus integral controller. The prediction of a desired motor/generator speed can be: a trajectory comparison based on present and past vehicle velocity and acceleration or on vehicle accelerator position, or a determination of whether the vehicle is in speed control mode. The system can also add additional strategies such as a termination strategy if a vehicle brake is applied.

1. Field of Invention
The present invention relates generally to a hybrid electric vehicle (HEV), and specifically to a strategy to start an engine in an HEV with minimal torque disturbance to the powertrain.
2. Discussion of the Prior Art
The need to reduce fossil fuel consumption and pollutants from automobiles and other vehicles powered by internal combustion engines (ICEs) is well known. Vehicles powered by electric motors have attempted to address these needs. However, electric vehicles have limited range and limited power coupled with the substantial time needed to recharge their batteries. An alternative solution is to combine both an ICE and electric traction motor into one vehicle. Such vehicles are typically called hybrid electric vehicles (HEV""s). See generally, U.S. Pat. No. 5,343,970 to Severinsky.
The HEV has been described in a variety of configurations. Some HEV patents disclose systems where an operator is required to select between electric and internal combustion operation. In other configurations the electric motor drives one set of wheels and the ICE drives a different set.
Other, more useful, configurations have developed. A series hybrid electric vehicle (SHEV) is a vehicle with an engine (most typically an ICE), which powers a generator. The generator, in turn, provides electricity for a battery and motor coupled to the drive wheels of the vehicle. There is no mechanical connection between the engine and the drive wheels. A parallel hybrid electrical vehicle (PHEV) is a vehicle with an engine (most typically an ICE), battery, and electric motor combined to provide torque to power the wheels of the vehicle.
A parallel/series hybrid electric vehicle (PSHEV) has characteristics of both the PHEV and the SHEV. The PSHEV is also known as a torque (or power) splitting powertrain configuration. Here, the torque output of the engine is given in part to the drive wheels and in part to an electrical generator. The generator powers a battery and motor that also provide torque output. In this configuration, torque output can come from either source or both simultaneously. The vehicle braking system can even deliver torque to drive the generator to produce charge to the battery (regenerative braking).
The desirability of combining the ICE with an electric motor is clear. The ICE""s fuel consumption and pollutants are reduced with no appreciable loss of performance or vehicle range. A major benefit of parallel HEV configurations is that the engine can be turned off during periods of low or no power demand from the driver (e.g., waiting for a traffic light). This improves fuel economy by eliminating wasted fuel used during idle conditions. The motor can then propel the vehicle under conditions of low power demand. In some configurations, the engine can be disconnected from the motor and powertrain when it is not running by opening a disconnect clutch. As power demand increases, the engine can be restarted and reconnected to provide the requested torque.
Developing a strategy to start an HEV engine and transfer primary torque production of the powertrain from the motor to the engine with minimal torque disturbance is needed for successful implementation of a parallel HEV. If the engine is disconnected from the powertrain, starting the engine would involve maintaining the vehicle""s response to the driver""s demand using the motor while simultaneously closing a clutch that connects the engine to the powertrain (disconnect clutch) and start running the engine. Torque supply to the powertrain should be transferred from the motor to the engine smoothly in order to avoid any disturbance to the driver.
Strategies to turn on an HEV""s engine are known in the prior art. See generally, U.S. Pat. No. 6,054,776 to Sumi; U.S. Pat. No. 6,026,921 to Aoyama et al.; and U.S. Pat. No. 5,865,263 to Yamaguchi, et al. Unfortunately, no strategy is known to start a parallel HEV engine while maintaining a smooth vehicle response to driver demand using the motor while simultaneously closing a clutch that connects the engine to the powertrain (disconnect clutch).
Accordingly, the present invention provides a strategy to start a parallel HEV engine while maintaining a smooth vehicle response to driver demand using the motor while simultaneously closing a clutch that connects the engine to the powertrain. In the preferred embodiment, the HEV powertrain has an engine, a motor/generator, a power transfer unit (such as an automatic transmission, planetary gear set, or an electronic converterless transmission), and an engine disconnect clutch.
The strategy starts running the engine (based on, for example, driver demand), connects the disconnect clutch to the powertrain, fuels the engine, and predicts a desired motor/generator speed. Next the strategy calculates a desired engine torque. And finally, the strategy gradually reduces actual motor/generator torque while proportionally increasing actual engine torque until motor/generator torque is zero while maintaining vehicle velocity.
The prediction of a desired motor/generator speed can be a trajectory comparison based on vehicle velocity and acceleration at a present time and at some past time or on a vehicle accelerator position. Predicting the desired motor/generator speed can also include a determination of whether the vehicle is in speed following control mode.
The system can also add additional strategies such as a termination the strategy if a vehicle brake is applied.
The gradual reduction of actual motor/generator torque occurs by proportionally increasing actual engine torque until motor/generator torque is zero while maintaining vehicle velocity using, for example, a proportional plus integral controller.
Other objects of the present invention will become more apparent to persons having ordinary skill in the art to which the present invention pertains from the following description taken in conjunction with the accompanying figures.

Method for starting an engine in a parallel hybrid electric vehicle


An LED light source device having an LED including an LED element as a light emission source and capable of possessing the same light distribution characteristics and luminance distribution as those of a common bulb having a coiled filament as a light emission source is provided. The LED light source device is also capable of providing the same light distribution pattern when it is used for a lighting fixture that utilizes a bulb as a light source, in place of a bulb. LEDs are disposed with respect to first light reflecting surfaces of paired hyperbolic cylindrical surfaces with a common focal line while LED elements of the LEDs are disposed at or near respective positions on the focal lines of the other hyperbolic cylindrical surfaces corresponding to the paired hyperbolic cylindrical surfaces.

Japanese Patent No. 4689762 discloses an LED bulb as conventional LED light source devices of this type, which can include an optical system as illustrated in FIG. 1A.
The disclosed LED bulb can include an LED light emitting element 100 and a reflecting member 101 disposed forward of the LED light emitting element 100 in its light illumination direction. The reflecting member 101 can include a reflecting surface 105 facing to the light emission surface 102 of the LED light emitting element 100 and having a center axis 106. The reflecting surface 105 can be composed of an apex 103 projecting toward the light emission surface 102 of the LED light emitting element 100, and a curved conical reflecting surface 104 that is a side surface extending from the apex 103 and concavely curved toward the center axis 106.
With this configuration, the light emitted from the LED light emitting element 100 can be radially reflected sideward and obliquely rearward with respect to the light illumination direction by means of the curved conical reflecting surface 104 of the reflecting member 101. Then the curved conical reflecting surface 104 can form a pseud light source (E) by the reflected light (F) therefrom. According to the conventional light source device disclosed in the conventional art, the light emission direction of light from the pseud light source (E) can be substantially the same as the light emission direction of light from a halogen bulb with a filament. Consequently, the formed position and the size of the light emission region of the pseud light source (E) can be the same as those of such a halogen bulb.
In the LED bulb disclosed in Japanese Patent No. 4689762, the light from the pseud light source (E) can be reflected by the curved conical reflecting surface 104, so that the reflected light (D) can form the light distribution pattern 107 as illustrated in FIG. 1B with a curved conical shape projected by the curved conical reflecting surface 104. The light emitted from the pseud light source (E) can form distribution light characteristics and luminance distribution different from those of light emitted from a coiled filament with a constant diameter.
In other words, the light distribution characteristics of the pseud light source (E) can correspond to those of a coiled filament (F) that is prepared by winding filament while gradually changing the winding diameter to form a curved conical shape. Therefore, the pseud light source (E) can emit light rays including first light rays emitted from first portions corresponding to those of filament wound with larger diameters and second light rays emitted from second portions corresponding to those of filament wound with smaller diameters. When such a pseud light source (E) is mounted within a lighting fixture having a light distribution control system, the first light rays from the first portions of the pseud light source (E) can be controlled in light distribution characteristics in such a manner that they are spread by the light distribution control system while the second light rays from the second portions thereof can be controlled in light distribution characteristics in such a manner that they are converged to a certain direction.
As a result, the lighting fixture with such a pseud light source (E) installed therein is difficult to obtain the same or similar light distribution characteristics and illuminance distribution as or to those of a conventional lighting fixture including a coiled filament with a constant diameter. In short, even if a bulb is replaced with such an LED bulb, the light distribution characteristics of such a lighting fixture are remarkably different from those of a lighting fixture with a conventional bulb.
Furthermore, the reflecting member 101 having the curved conical reflecting surface 104 that can provide such a pseud light source (E) needs to be supported by a columnar support, and such a columnar support must be arranged in the vicinity of the reflecting member 101 due to the limited space within the lighting fixture. This, however, results in formation of a shadow by the columnar support shielding the light emitted from the pseud light source (E).


In a coil winding machine for producing cylindrical coils each having a plurality of coil layers, an insulating bobbin is detachably mounted on a coil winding spindle driven by a driving source. A coil wire supplying device supplies a coil wire continuously onto the bobbin so as to form the coil layers, and an insulating tape supplying device continuously supplies an insulating tape over each coil layer so as to form tape windings partly overlapping each other in the longitudinal direction.

This invention relates to a coil winding machine capable of winding cylindrical coils to be used in electric apparatus such as transformers, induction coils, reactors, and the like.
Heretofore, a cylindrical coil as shown in FIGS. 1(A) and 1(B) of the accompanying drawing has been produced by winding an electrically conductive wire (hereinafter termed coil wire) b around an electrically insulating frame (hereinafter termed bobbin) a of a cylindrical configuration, by a required number of coil layers, and, during the coil winding operation, a corresponding number of interlayer insulating sheets c are inserted between the respective coil layers, simultaneous with the application of coil end insulators d.sub.1 and d.sub.2 onto both ends of the coil layers.
However, the thicknesses of the coil end insulating materials d.sub.1 and d.sub.2 are substantially equal to the diameter of the coil wire b which is far thicker than the thickness of the interlayer insulating sheet c, and therefore two kinds of insulating materials have been prepared for the production of such coils. Where it is necessary to prepare various kinds of insulating materials and it is desired to reduce the number of types of insulating material for the simplification of stock control or the like, an interlayer insulating sheet e as shown in FIG. 2 having two lateral sides e.sub.1 and e.sub.2 folded into a W shape may be has been used instead of a simple sheet of an insulating material.
Regardless of the types of the interlayer insulating sheets c or e, however, when it is used between the coil layers the length of each interlayer insulating sheet c must first be estimated, and the sheets c must be cut beforehand into the estimated lengths in a separate sheet cutter. During the coil winding operation, the interlayer insulating sheets c thus cut into the estimated lengths are inserted successively between the coil layers, and the longitudinal ends of the successive sheets must be joined together in an overlapping relation by an adhesive agent or the like.
For performing these processes, many of the conventional coil winding machines incorporate a sheet cutter cutting the interlayer insulating sheets into the respective lengths, a sheet supplying device supplying the interlayer insulating sheets into the required positions, and a sheet bonding device which joins the longitudinal ends of the interlayer insulating sheets during the coil winding operation, thus complicating the construction, and rendering the maintenance and handling of the machine extremely troublesome. Furthermore, the alternate executions of the coil layer winding steps and the insulating sheet insertion steps have reduced the operating speed of the coil winding machine, caused mass-production of the coils to be extremely difficult.


A conveyor cleaning and residue control system for use with a conveyor includes an air knife and a deflector. The air knife impinges an air stream against the conveyor to blast residue from the conveyor, and the deflector redirects the air stream and the residue loosened by the air stream toward a chute. The flow of the air stream toward the chute causes at least a portion of the air-borne residue in the vicinity of the conveyor to flow toward the chute with the air stream such that the residue becomes supersaturated and forms macro-particles that precipitate out of air suspension. The air knife and deflector thus recycle the residue carried by the conveyor instead of requiring it to be evacuated. In the first embodiment, the deflector includes a pair of non-coplanar blades that are attached to one another. The deflector is both rotationally and translationally adjustable with respect to the conveyor. A second embodiment is disclosed wherein the deflector is curved. A third embodiment is disclosed wherein the deflector includes a servo mechanism that adjusts the orientation of the reflector with respect to the conveyor. A fourth embodiment is presented wherein the air knife and deflector are employed in a new construction material transport system that includes a shroud connected to the chute and an evacuation system connected to the downstream end of the shroud.

1. Technical Field
The invention relates generally to material transport systems and, more particularly, to a cleaning system that removes residue from a conveyor and controls the generation of air-borne residue particles. Specifically, the invention relates to a material transport system having an air knife that impinges an air stream against a conveyor to remove the residue therefrom and a deflector to deflect the air stream and air-borne residue toward a chute or hopper after the air stream has impinged on the conveyor. The invention also relates to the removal of air-borne residue particles from the area surrounding the conveyor.
2. Background Information
Material transport systems are used primarily for transporting materials from one location to another. Material transport systems typically include a conveyor, which may be any of a variety of structures such as endless conveyor belts, chain belts and feeders, vibrating feeder beds, and foldable belts, as well as other devices of the type known and understood in the relevant art. Most notably, material transport systems include a material discharge chute for collecting and sorting material, which chute relates to the present invention.
When the materials transported by the conveyor are of a particulate nature, such as coal or breakfast cereal, the conveyor becomes coated with a residue of fine particles of the particulate material. The residue is produced by the breakage of the particulate materials, friction between the particulate materials and the conveyor, friction between the individual particles themselves, as well as other phenomena. When the particulate material is of a powdered consistency, such as powdered lime, the powdered material itself is the residue that becomes coated on the conveyor.
Such residue sticks to the conveyor as a result of phenomena such as static electricity or trace amounts of oil or water disposed on the conveyor or contained in the air, as well as due to other phenomena. The residue is continuously deposited on the conveyor as a result of conveying the particulate materials and ultimately results in fouling of the conveyor and failure of the material transport system if allowed to remain on the conveyor without cleaning. Moreover, the residue must be removed from the conveyor inasmuch as such residue contributes to an overall dusty environment that is unsafe, unsanitary, and unattractive.
The coating of residue on the conveyor has often proven difficult to reliably and safely remove. Specifically, brushes and scrapers that attempt to frictionally dislodge the residue from the conveyor often are only partly effective and moreover dramatically increase conveyor wear. The need thus exists for a device that removes the residue from a conveyor without increasing the wear of the conveyor.
The residue produced in transporting the particulate materials is typically both air-borne as well as coated on the conveyor. Such air-borne residue is preferably controlled in some fashion to prevent the air-borne residue from fouling the air surrounding the material transport system and settling on the floor, machinery, and other objects around the material transport system. As is understood in the relevant art, a head cover is typically disposed over the terminal end of the conveyor where the particulate materials are discharged into a chute for transfer onto another conveyor or into a packaging system. The head cover typically surrounds the terminal end of the conveyor and includes an evacuation system such as a dust vacuum that draws the air-borne residue away from the terminal end of the conveyor and into appropriate containers for disposal or reintroduction into the system. Such evacuation systems are, however, expensive to operate inasmuch as the disposal or reintroduction of the collected residue requires additional material handling and cost, and results in generation of additional air-borne residue.
Most evacuation systems in existing material transport systems are attached at the uppermost portion of the head cover, with the result that the evacuation system draws air-borne residue in a direction away from the flow of particulate material, thus preventing the air-borne residue from settling out of air suspension and back into the particulate material. While the air-borne residue must be captured for reasons of conveyor reliability, safety, and hygiene, such caption generates an expense that is preferably minimized.
The head cover typically includes a chute disposed at the lower end into which the particulate material is discharged. As the particulate material falls into the chute, the evacuation system removes the air-borne residue from inside the head cover for disposal.
The removal of residue from the conveyor can contribute to the presence of air-borne residue particles. An increase in the quantity of air-borne residue caused during cleaning of the conveyor thus results in increased evacuation requirements. The need thus exists for a device that reliably removes the residue from a conveyor without increasing the quantity of air-borne residue. Such a device preferably reduces the quantity of air-borne residue within the head cover.

Conveyor cleaning and air-borne residue control system


A fluid-flow measuring ball valve includes a housing and a ball having an orifice. The ball is moved between an open position allowing fluid flow through the orifice and a closed position preventing fluid flow. A first ultrasonic transducer is positioned in the housing upstream of the ball. A second ultrasonic transducer is positioned in the housing downstream of the ball and both are aligned to send and receive pulses. First and second acoustic reflectors are aligned with the transducers to transmit and reflect ultrasonic signals in at least one direction through the ball orifice when the ball is in an open position. The controller determines the fluid velocity based on measured speed of sound and calculates the volume of fluid through the orifice based on the measured fluid velocity and cross-sectional area.

Throughout the world, potable water and gas distribution systems use different types of pipes, valves, and fittings. Most systems, even with their variations, typically include a water or gas flowmeter connected into the system, for example, at a residence or other premises. The flowmeter measures the fluid flow over time, which is then used to bill the premises owner its use of water and/or gas consumed at the premises. There are many different types of pipes, valves, and fittings that may be incorporated in a water or gas distribution system, and different water or gas metering technologies may be used to measure the consumption of water and/or gas depending on the system. Each different type of water or gas distribution system has its own pros and cons and the choice made for any particular flowmeter at a premises is often based on the flowmeter price, flow accuracy, manufacturing process, installation ease, maintenance requirements, and size of its components, relative pipe sizes and placement.
Usually a gas or water distribution system at a premises includes a dedicated fluid flow metering device, which typically operates in conjunction with a manually operated shut-off valve that is located before or upstream of the fluid flow metering device in order to allow a technician to shut off fluid flow and maintain and/or replace the fluid flow metering device when necessary. There are many different examples of gas and water mains that incorporate a shut-off valve adjacent a fluid flow metering device. Usually, a household premises includes either a ball valve or a gate valve in the main gas or water line. Sometimes a yoke box holds a shut-off valve and/or water or gas flowmeter and may incorporate an optional, electronic meter reading iron lid that is removed to access the shut-off valve and/or flowmeter. A domestic water distribution system supply water to appliances such as toilets, faucets, water heaters, and similar devices, and a natural gas distribution system may include a gas main having a shut-off valve and gas flowmeter adjacent or on the house and the gas main connected that branch out into smaller pipe to supply gas appliances such as a grill, lights, pool heater, or similar components. There are problems associated with these more conventional gas and water distribution systems such as size constraints for various valves and fluid flowmeters, unacceptable flowmeter accuracy, and pressure drops that occur in the gas or water distribution system that affect accurate fluid flow metering.
Commonly assigned U.S. Pat. No. 6,923,074 discloses a ball valve with a flow-rate gauge incorporated directly into the ball valve. The ball portion of the ball valve includes a calibrated borehole or orifice and two positionable pressure ports placed before and after the ball respectively, to provide measurements indicative of the flow-rate of the fluid that passes through the ball valve. This ball valve is usually limited to water use. Although it is effective to measure fluid flow at typically higher water flow rates, it has some reduced accuracy at lower water flow rates.
In the past six years, the gas and water metering industry has improved the affordability, performance, and accuracy of ultrasonic flowmeters that use transit time measurements or Doppler Effect measurements. These ultrasonic flowmeters measure the amount of time required for an ultrasonic signal, e.g., an emitted "ping" to pass between two or more fixed points inside the flowmeter. When the ultrasonic flowmeters are calibrated properly for gas and water, they can be used to measure both fluid media. Ultrasonic flowmeters typically incorporate one or more ultrasonic transducers to emit ultrasonic sound waves through the fluid to determine the velocity of the fluid. Because the cross-sectional area of the flowmeter body is a fixed and a known value, when the velocity of the fluid is detected, the volume of fluid passing through the flowmeter may be calculated to a very high accuracy. Also, because fluid density changes with temperature, most ultrasonic flowmeters measure the fluid temperature as a component of the volume calculation and determine fluid flow based on temperature as a variable. When used with ball valves, the ultrasonic flowmeters are connected directly to an existing ball valve or connected into the gas or water pipe to which the ball valve is connected. This may increase the ball valve and its closely connected ultrasonic flowmeter footprint, i.e., make the combination too large for a workable solution, making the flowmeters and valves difficult to install, maintain, and replace.

Integrated ball valve and ultrasonic flowmeter


A target layer with holes is formed on a bottom conducting layer. Nanotubes are formed in the holes from the bottom conducting layer. A flat insulating layer is then deposited on the target layer, the nanotubes passing through the insulating layer. Air gaps are then formed by selective decomposition of the target layer. The decomposition agent and/or decomposition by-products use the walls and the central holes of the nanotubes to pass between the target layer and the outside. After decomposition, the top conducting layer is formed on the insulating layer. The nanotubes then electrically connect the conducting layers.

The invention relates to a fabrication method of a nanotube-based electric connection between two conducting layers, respectively bottom and top, separated by a target layer, a method successively comprising:                formation of the target layer on the bottom conducting layer,        formation in the target layer of at least one hole comprising a bottom,        growth of the nanotubes in said hole,        formation of the top conducting layer electrically connected to the bottom conducting layer by the nanotubes,

Fabrication method of a nanotube-based electric connection having air gaps


This disclosure relates to a system for stabilizing a permanent magnet synchronous motor that does not have a rotor starting cage or windings. The system includes a dc source, an inverter connected to the dc source for converting the dc to a multi-phase ac, and an ac synchronous motor connected to receive the multi-phase ac, the motor being constructed without a starting cage or winding. The system further includes means for sensing variations in the motor power angle, and a control circuit connected to respond to the variations and to cause the inverter output to vary such as to generate an ac component of torque that leads in phase the power angle variations at the natural frequency of the rotor of the motor. The inverter output may be varied by modulating the applied frequency, the dc bus current to the inverter, or the inverter phase angle.

This invention relates to a drive or power system for a permanent-magnet (PM) synchronous motor. In recent years, such systems including dc to ac inverters have become increasingly important, and this interest has been due in part to improved magnetic materials for the permanent magnet rotors and to the reduced costs of solid state switching devices. Such a system has important characteristics that make them highly advantageous in some applications. For example, they are very efficient, simple in construction and dependable, capable of being powered by a dc source such as a solar array, and variable in speed so that the power output may be matched to the available power from the source.
In the past, synchronous motors have normally included a rotor starting cage or windings that are used to bring the motor up to or near synchronous speed. It is, however, desirable to be able to avoid the use of such a cage because it introduces harmonic losses during operation and, of course, a cage requires added expense. To operate such a motor without a starting cage, it is necessary to bring the motor up to rated speed by increasing the applied frequency from a low value to the normal value at a rate sufficiently low that the motor can remain in synchronism with the applied frequency.
However, it has been found that a PM synchronous motor without a starting cage, as described, is not stable except at the lower portion of a typical speed range. Ideally the rotor would turn at a uniform speed which is a function of the number of magnetic poles and the inverter applied frequency, but it has been found in practice that the rotor speed actually oscillates at its natural or harmonic frequency about the equilibrium speed. Such oscillations may be compared with the vibrations of a torsion spring at its harmonic frequency. When such a motor is started at a low speed and the speed is increased by increasing the applied frequency, the motor is stable (i.e., the oscillations are damped) until it reaches approximately one-fourth its rated speed, and then it becomes unstable. At this point the magnitude of the oscillations increases to the point where the rotor drops out of synchronism and then the motor stops. The speed at which this occurs depends on the motor construction and the type of load, and the motor and the load have inherent damping constants which prevent instability up to a certain point.
Three phase synchronous motors have, of course, been successfully operated in the past, and it is believed that such motors did not have such instability problems because they included either a starting cage or a starting motor, which functioned to damp such oscillations.
U.S. Pat. No. 3,753,063 of C. E. Graf describes a stabilizing system for damping speed oscillations of a three phase a-c reluctance-synchronous motor. According to this patent, the speed oscillations produce an a-c ripple current in the d-c bus supplying the inverter. The Graf patent describes a system for sensing the ripple current and modulating the inverter output voltage to counteract the oscillations. According to the patent, the modulation is such that an increase in rotor speed must result in an increase in the inverter output voltage, and vice versa. The precise construction of the a-c reluctance-synchronous motor is not clear from this patent, but the modulation system described in this patent would destabilize, not stabilize, a permanent magnet synchronous motor of the construction described herein.

Control system for permanent magnet synchronous motor


A ramp-launched read/write device for a data carrier includes an arm, a loading spring having a part fixedly connected to the said arm and a free end part, a platform incorporating at least one read/write transducer, a carrier member to carry the platform, and a guide member for controlling the position of the platform in relation to the data carrier. The guide member is made up of a level surface and at least one ramp, and is arranged to cooperate with the said guide member for bringing the platform to a first, rest position and a second read/write position close to the data carrier to allow the data carrier to be read from or written on. The carrier member includes a suspension spring which has one end fixedly connected to the arm and a free end adapted to contact with the platform. The guide member is fixedly but flexibly connected to the arm and the said free end part of the loading spring contacts the guide member in accordance with the positions of the platform. An anti-vibration member in the form of a spring has one end fixedly connected to the arm and its free end rests against the free end of the suspension spring of said carrier member. The carrier member is shaped to enable the platform to move between the said first and second positions while remaining parallel to itself. To this end the carrier member includes a frame enclosing the platform which is carried by two substantially parallel arms which bend through approximately 180.degree. before connecting up with the central areas of the carrier.

1. Field of the Invention
The invention relates generally to read/write devices for data carriers and more particularly to a read/write device of the type which is ramp-launched. It is applicable to magnetic read/write devices for magnetic peripherals of data-processing systems, in particular disc memories.
2. Description of the Prior Art
In present-day data processing systems, increasingly frequent use is being made of magnetic disc memories because of their storage capacity and the relatively short time taken by the magnetic read/write transducers to access an item of data contained anywhere on the discs from the time when the transducers receive an order to access this item from the said processing system.
Magnetic discs are known to carry data in concentric circular recording tracks whose radial widths are in the order of a few hundredths of a millimeter or less and which generally cover the major proportion of both faces of the discs. The discs are driven round at constant speed by an electric motor.
To enable data to be read from and written onto disc memories, magnetic transducers are arranged at a distance of a few .mu.m above both faces of the discs. The current practice usually is to associate a single platform provided with one or more transducers with each face of a disc. When it is desired to achieve a substantial reduction in the time taken by a transducer to access any item of data contained on the face in question, the platform is provided with a plurality of transducers. Typical magnetic platforms are illustrated and described in U.S. Pat. Nos. 3,723,665 and 3,846,847 and copending application Ser. No. 882,592 of Lazzari et al, filed Mar. 2, 1978, now U.S. Pat. No. 4,198,667, and assigned to the assignee of the present invention.
The transducers used are generally magnetic transducers which contain a magnetic circuit having an air gap and a winding arranged round it. The air-gap enables data to be read and written. Generally, but not exclusively, platforms incorporating one or more transducers are in the shape of a relatively shallow rectangular parallelepiped of which the major face, termed the lower face, which is adjacent the discs, contains the air gaps of the transducers, and of which the opposite major face, termed the upper face, contains the electrical terminals and wires which enable the windings of the transducers to be connected to the electrical circuits of the disc memory which are associated with them.
When the transducers of a platform are not performing the operation of reading or writing data from or on the corresponding face of the disc, the platform occupies a so-called "rest" position in relation to the disc which is different from the so-called read or write position.
The platforms are provided with a fitting which, as a whole, forms a device which will be referred to herein as a read and/or write head.
There are two main types of read/write heads. One is known as a "ramp-launched head" or "ramp-landed head", and the other is known as an "unstick from contact head".
"Ramp-landed heads" have long been known. They generally comprise: a platform incorporating at least one transducer, a member to carry the platform at one of its ends which takes the form of a substantially rectangular rigid strip, a rigid arm detachably secured to a carriage intended to move the platform above the disc, a loading spring formed by a substantially rectangular flexible strip, one side of which is fixed to the arm and the other side of which is fixed to the member carying the platform at the end of the said member opposite from that carrying the platform, and a means for controlling the position of the platform in relation to the data carrier. The latter means comprises a guide member made up of a level surface and a ramp and a pin which, when it cooperates with the level surface, holds the platform in its rest position and which, when it cooperates with the ramp, brings the platform to its reading/writing position. The level surface forms an extension, generally in the same plane, of the rigid strip carrying the platform. The ramp forms an extension of the level surface in an upwardly inclined plane, that is to say it extends away from the face of the disc.
Given that in this structure the rigid strip which is to carry the platform and to incorporate the position controlling means forms an extension of the loading spring, the platform necessarily carries a heavy loading. A typical value for this loading is in the order of 300 g. It is desirable, however, that the loading on the platform should be light.
Assuming that the disc rotates, typically, at 60 revolutions per second, and that, for reasons inherent in its manufacture, the surface of the disc contains unevenesses which pass in front of the platform at a frequency of 600 Hz, the platform needs to be capable of accepting severe acceleration in order to be able to follow the undulating surface of the disc. Since acceleration is the quotient of force divided by mass, it is possible to achieve high acceleration either by increasing the force or by reducing the mass. However, since the platform flies above the disc at the time of reading or writing as a result of the lifting effect of a cushion of air which exists between the lower face of the platform and the disc, force is a datum which cannot be altered. The problem is therefore to reduce the mass of the head. This being 300 g at the present time for typical structures, it would be desirable to reduce it to 15 g, that is to say to divide it by 20. Unfortunately, it is impossible to produce a landing head having so low a loading while still retaining a conventional structure as described above.
As another drawback of heavy loading, mention should be made of the sensitivity of such heads to the unwanted dust particles that the face of the disc may be carrying. In effect, the head is not sufficiently compliant to react to the presence of large particles which infiltrate between one of its air gaps and the disc. Such particles may act as magnetic shunts and adversely effect the quality of the detected signal and may also cause mechanical damage to the adjoining faces of the disc and the platform.
To overcome the disadvantages of ramp-landed heads, another type of head has been designed termed the "unstick from contact head". Such heads are illustrated and described in copending applications of Michel Plotto, Ser. Nos. 958,839 and 958,840, filed Nov. 8, 1978, now U.S. Pat. Nos. 4,225,891 and 4,212,044, respectively, and assigned to the assignee of the present invention. These new heads are being more and more widely used by reason of their low loading. The platforms for these heads have a lower major face termed the flight surface. The flight surface comprises a first part which is in the form of skids which rest on the disc when the latter is stationary and a second, bevelled part, which is inclined to the skids and which is situated at the front of the platform, the front being that part of the flight surface which, when the face of the magnetic disc associated with the platform is passing in front of the flight surface, is the first in time to have the data on this face of the disc pass before it. The air gaps of the transducers belonging to the platform are situated at the rear of the flight surface.
When it is desired to move the platform from its rest position to its flying position above the face of the disc which is associated with it, it is merely necessary to set the disc in rotation. After a fairly short time, the platform rises due to the lifting effect created by the bevel. When the disc reaches its nominal speed of rotation, the platform is in its flying position with the skids inclined relative to the face of the disc, which provides the platform with sufficient lift for it to fly stably above the disc. The platform is thus enabled to take off by the lift provided by the skids.
Platforms of this kind are carried by a weak leaf-spring, which, in the read or write position, also acts as an arm to guide the platform above the disc and to suspend it.
Despite the advantage which these platforms have by virtue of their being lightly loaded, their use is restricted by the following two principal drawbacks. Firstly, the platform for such a head has an unstick time and, although this time is only of the order of a few milliseconds, it does mean that after a number of take-offs the flight surface of the platform and the corresponding face of the disc deteriorate as a result of the wear on them caused by the mechanical friction between them. Secondly, replacing a disc poses far more problems than it does with ramp-launched heads. In effect, unstick from contact platforms have to be moved away from the disc and then, when the disc has been removed, they have to be held in a position where they cannot be damaged and finally, they have to be moved out of the way again while the new disc is being inserted and adjustments have to be made to ensure that they fly at the correct height.
In contradistinction, ramp-landed heads do not have these advantages inasmuch as the platform is fairly well spaced from the disc in the rest position thereby enabling easy disc replacement. When the disc is in place adjustment is relatively easy.

Lightly loaded ramp-launched read/write device for a data carrier

Compagnie Internationale pour l'Informatique CII-Honeywell Bull (Societe Anonyme)


A low pressure fluorescent tanning lamp (10) includes an elongated, tubular glass envelope (12) including an arc generating and sustaining medium (14) and electrodes (16) therewithin and having a first section (18) and a second section (20). A phosphor coating (22) is provided on the interior of the first section (18) and only a portion (24) of the second section (20). The phosphor coating comprises materials emitting in the UVA and UVB areas of the electromagnetic spectrum and additionally in the visible area of the electromagnetic spectrum in the range above 600 nm. The second section (20) includes a clear window (26) and the phosphor comprises a mixture comprising about 91% BaSi2O5:Pb; about 6% MgSrAl10O17:Ce; and about 3% Y2O3:Eu.

Tanning lamps are known commodities and have been employed for some time in tanning booths and tanning beds. It has been a problem to provide even tanning where the facial features are concerned because of the higher levels of melanin pigments in the face, resulting from more frequent exposure to the sun than the rest of the body. Prior attempts at correcting this problem have used additional lamps in the face area; high pressure UV lamps; lamps with multiple areas of differing phosphors to provided differing radiation zones; and lamps with specialized grooves formed in the head-end of the lamp.
These processes have been complicated and expensive. Thus, there is a continuing need for discharge lamps for use in tanning facilities that provide enhanced performance.


An eyeglass lens processing apparatus for processing an eyeglass lens includes: a processing chamber inside which a lens grinding tool is disposed; a tank which stores grinding water; a drain hose connecting the processing chamber with the tank; a filter for eliminating bubbles attached to an outlet of the drain hose, which includes a large number of pores having a size such that permits passing of processing debris stemming from rough processing and inhibits passing of bubbles larger than the processing debris.

1. Field of the Invention
The present invention relates to an eyeglass lens processing apparatus for processing an eyeglass lens, and to a grinding water tank unit for storing and circulating grinding water used at the time of lens processing.
2. Description of Related Art
In an eyeglass lens processing apparatus, grinding water is supplied during processing so as to cool the ground portion of a lens and eliminate grinding debris from the lens. As this water supplying system, there is a system in which grinding water is circulated between a grinding water tank and the main body of the processing apparatus. In this system, the grinding water stored in the tank is pumped up by a pump and supplied to the main body of the processing apparatus, the grinding water after use is discharged (drained) into the tank and is reused by being circulated.
If a plastic lens is ground by a grinding wheel, the grinding water, particulates of grinding debris and air cause bubbles to be generated in the discharged grinding water. If the grinding is continued, there are cases where the bubbles and the grinding water overflow the tank, or the bubbles and the grinding water flow into the grinding chamber of the main body of the processing apparatus. For this reason, generally, anti-foaming agent (surface active agent) is mixed with the grinding water and the mixture is used in order to restrain a generation of the bubbles.
However, if using the anti-foaming agent, the grinding water tends to be turbid. If the turbid grinding water continues to be circulated and used, processing quality may deteriorate and troubles of the processing apparatus are liable to occur. Further, recently, in term of the environment issue, it becomes necessary to restrain use of surface-active agent inclusive of the anti-foaming agent. In case of no use of anti-foaming agent, since the tank is filled with the bubbles by processing a small number of lenses, replacement of grinding water in the tank should be frequently conducted.

Grinding water tank unit for eyeglass lens processing and eyeglass lens processing apparatus having the same