A hydraulic system for a detachable implement such as draper platform for a combine utilizes a platform-mounted pump supplied with return oil from the existing reel drive motor. The system utilizes the existing combine hydraulic connection for the reel drive to supply oil to the draper belt drive motors. Oil from the combine powers the reel drive motor and then flows into a manifold block (mixing chamber) before entering the inlet of the draper belt drive pump. This pump is sized to provide sufficient oil flow to power the draper belt drive motors, arranged in series. Return oil from the belt drive motors is routed back to the manifold block where it can mix with incoming oil from the reel drive pump before returning to the combine reservoir or being recirculated to the belt drive motors. The hydraulic system avoids the need to equip the platform with a complete hydraulic system and avoids the need to modify the existing hydraulic system of the combine.

1. Field of the Invention
The present invention relates to a hydraulic system for a detachable implement having multiple hydraulic motors and in particular to a hydraulic system for a harvester header, such as a draper platform.
2. Description of Related Art
Draper platforms for harvesting machines, such as a combine, have a flat, wide belt, referred to as a draper or draper belt, to convey crop material. The arrangement and number of draper belts vary among platforms. One style of draper platform has two side belts that convey crop material laterally, to the center of the platform, where a center feed draper belt moves the crop material longitudinally into a combine feederhouse. Each of the draper belts is driven by a hydraulic drive motor.
In addition to the draper belts, a draper platform uses another hydraulic motor to rotate a reel above a cutterbar to hold crop material against the cutterbar and to move the cut crop material onto the draper belts. Hydraulic lift cylinders are used to raise and lower the reel as well as to position the reel fore and aft relative to the cutterbar.
A conventional combine includes a hydraulic system with connections for driving the platform reel and connections for operating the reel lift cylinders and the reel fore and aft adjustment cylinders. In addition to the hydraulic connections to the platform, the combine includes a power take off (PTO) for a mechanical power connection. The PTO is typically used to mechanically drive the platform cutterbar and crop conveying augers if the platform is so equipped.
Combines typically do not have additional hydraulic power connections for operating the draper belt drive motors. Therefore other provisions must be made for providing hydraulic power for this purpose. One option is to provide a complete hydraulic system on the platform including a gear pump that is driven by the combine PTO. This approach requires that the platform hydraulic system be equipped with a reservoir, filter and cooling package. This adds significant cost, weight and complexity to the draper platform. In addition, the PTO shaft speed is typically lower than required for efficient operation of a gear pump.
A second option is to provide additional pump capacity on the combine, thereby utilizing existing combine hydraulics to power the draper belt drive motors. A major disadvantage with this approach is the need for significant combine modifications in retrofit applications, as well as the need for another set of hydraulic hoses and couplers between a combine and the platform.
Accordingly, it is an object of the present invention to provide a hydraulic system for a detachable implement, such as a draper platform, that does not require modification to the existing combine hydraulic system and which does not require the added cost, weight and complexity of a complete hydraulic system onboard the platform.
The hydraulic system of the present invention utilizes a platform-mounted pump, supplied with return oil from the reel drive motor. The system utilizes the existing combine hydraulic connection for the reel drive. Oil from the combine powers the reel drive motor and then flows into a manifold block (mixing chamber) before entering the inlet of the draper belt drive pump. This pump is sized to provide sufficient oil flow to power the draper belt drive motors, arranged in series. Return oil from the belt drive motors is routed back to the manifold block where it can mix with incoming oil from the reel drive pump before returning to the combine reservoir or being recirculated to the belt drive motors.
At the upper end of the reel speed range, oil flow from the reel drive motor is sufficient to supply the needs of the belt drive pump, in which case all returning oil from the belt drive motors is immediately routed back to the combine. At the lower end of the reel speed range, oil from the reel drive motor may not be adequate to supply the entire demand of the belt drive pump, so a portion of the return oil from the belt drive motors will recirculate within the belt drive system, instead of immediately returning to the combine. The ports in the manifold block are configured such that the belt drive pump receives its priority oil from the reel drive motor return, and only draws its own return oil when necessary. The utilization of the oil from the reel drive motor as the priority oil together with the long oil flow path from the pump, through the motors and back to the manifold prevents excessive heat buildup in the belt drive hydraulic oil. The hydraulic system thus uses the belt drive pump to provide the desired oil flow from the reel drive circuit to drive the draper belt motors. No additional hydraulic connection to the combine is needed.
A unique aspect of the hydraulic system is the use of an Eaton T-Series Geroler motor as a pump. This motor was selected as the pump due to its low speed, high torque characteristics. In addition, this motor operates more efficiently at the low shaft speed available on the platform compared to gear pumps. Combine back pressure in the reel motor return will provide positive pump inlet pressure. The T-Series motor is not able to draw oil but combine back pressure provides this service. The T-Series motor was selected since the shaft seal can withstand back pressures up to 1500 psi. The high combine back pressure is not suitable for most gear pumps.
While the present invention has been developed for use with a draper platform for a combine, the hydraulic system of the present invention can be utilized in other applications where an implement is attached to a prime mover and utilizes two or more hydraulic drive motors, with one motor being driven by a connection to a hydraulic system on the prime mover. Other uses may include agricultural tractors and implements as well as construction equipment with detachable implements.

Device for remotely controlling a hydraulic system on a detachable implement


A magneto-resistance effect element comprises a stacked body which comprises a pinned layer having a fixed magnetization direction, a free layer having a magnetization direction that varies according to an external magnetic field, and a nonmagnetic spacer layer which is interposed between the pinned layer and the free layer. The stacked body having a constricted shape in which at least one part of the spacer layer is constricted when viewed from at least one direction perpendicular to a stacked direction of the stacked body.

1. Field of the Invention
The present invention relates to a magneto-resistance effect element and a thin-film magnetic head which are suitably used for a hard-disk drive, and to a method for manufacturing the magneto-resistance effect element.
2. Description of the Related Art
A hard-disk drive uses a thin-film magnetic head having a magneto-resistance effect element (MR element) to read out a magnetic signal. In recent years, the trend is for hard-disk drives to have higher recording densities. Correspondingly, the magneto-resistance effect element in a thin-film magnetic head is required to have, in particular, higher sensitivity and higher output.
A CIP-GMR (Current in Plane-Giant Magneto-resistance) element which is a giant magneto-resistance effect element having a nonmagnetic layer between ferromagnetic layers and passing a sensing current in parallel to a layer surface, has been conventionally developed as a reproducing element in a thin-film magnetic head. On the other hand, a magnetic head that uses a TMR (Tunnel Magneto-resistance) element which has an insulation layer instead of the nonmagnetic layer as an intermediate layer and which passes a sensing current perpendicular to a layer surface, has also been developed in order to achieve higher densification. Furthermore, a magnetic head that uses a CPP (Current Perpendicular to Plane)-GMR element which is a GMR element having a nonmagnetic layer as the intermediate layer and passing a sensing current perpendicular to the layer surface similar to the TMR element, has also been developed. CPP-GMR element has an advantage of having low resistance in comparison with the TMR element and higher output in a narrower track width than the CIP-GMR element.
FIG. 1 shows a structure of the conventional CPP-GMR element. CPP-GMR element 104 is interposed between lower shield layer 113 and upper shield layer 115, each of which serves as an electrode film as well, and is also referred to as a spin valve film (SV film). CPP-GMR element 104 has a pillar shape having a desired size, and has a structure in which nonmagnetic spacer layer 144 is interposed between pinned layer 143 that is a ferromagnetic layer in which the magnetization direction is fixed and free layer 145 that is a ferromagnetic layer in which the magnetization direction varies according to an external magnetic field. The magnetization direction in the pinned layer 143 is fixed because pinned layer 143 is arranged on antiferromagnetic layer 142 arranged thereon. Recently, pinned layer 143 can be not only made into a single-layered structure of a ferromagnetic material but can also be made into a three-layer structure (synthetic pinned layer) formed of a ferromagnetic layer that is inner layer 143c, a nonmagnetic metal layer that is nonmagnetic intermediate layer 143b, and a ferromagnetic layer that is outer layer 143a. Thus configured, CPP-GMR element 104 provides a strong exchange coupling between two ferromagnetic layers 143a and 143c, and thus effectively increases the power of exchange coupling with antiferromagnetic layer 142. Hard magnetic film (hard bias film) 148 made from CoPt or CoCrPt is arranged around CPP-GMR element 104 through insulation film 147 such as Al.sub.2O.sub.3. Hard bias film 148 is a film for controlling the magnetic domain of free layer 145, and is located on the side of CPP-GMR element 104 in the track width direction. Cap layer 146 and buffer layer 141 are respectively arranged on the top end and the bottom end of CPP-GMR element 104. Cap layer 146, CPP-GMR element 104, and buffer layer 141 are interposed between upper shield layer 115 and lower shield layer 113.
Feature of low resistance of a CPP-GMR element is very advantageous for frequency characteristics, but causes a defect that resistance change is low. This is because when the absolute value of resistance is small, the amount of resistance change is generally small as well. The magneto-resistance effect element having a small amount of the resistance change shows low sensitivity when used as a reproducing element in a thin-film magnetic head.
For this reason, a known CPP-GMR element uses the technology of CCP (Confined Current Path) to increase the resistance value by restricting electric current.
Japanese Patent Application Laid-Open No. 2002-208744 describes a configuration in which a resistance adjustment layer is arranged on at least one of a pinned layer, a spacer layer, and a free layer. For instance, the resistance adjustment layer which is made from a metalloid or a zero-gap semiconductor and which has a pinhole therein, is inserted into each of the layers. In the configuration, an electric current that flows in a direction perpendicular to a layer surface is interrupted by the resistance adjustment layer, and only flows through the pinhole in the resistance adjustment layer. Japanese Patent Application Laid-Open No. 2003-204094 proposes a configuration in which a magnetic metal and an insulative material are distributed on a boundary surface of the spacer layer. The magnetic metal and the insulative material interrupt the electric current flowing in a direction perpendicular to the layer surface. Accordingly, the electric current only passes through gaps which lack magnetic metal and insulative material. As thus described above, in the configurations of Japanese Patent Application Laid-Open No. 2002-208744 and Japanese Patent Application Laid-Open No. 2003-204094, electric current flowing in the direction perpendicular to the layer surface only passes through specific parts (that are pinholes or gaps) inside the spacer layer. In other words, the spacer layer has a function of restricting electric current by confining the path for the electric current to pass, and consequently increases the resistance value.
In addition, Japanese Patent Application Laid-Open No. 2005-136309 proposes a configuration in which a spacer layer is partially irradiated with an Ar ion beam and then the spacer layer is oxidized. As a result, a region which has been previously irradiated with the Ar ion beam, becomes a current control region for passing an electric current in a direction perpendicular to a layer surface. The region which has not been previously irradiated with the Ar ion beam becomes an insulator region for interrupting the electric current in the direction perpendicular to the layer surface. In the configuration described in Japanese Patent Application Laid-Open No. 2002-176211, a stacked body of a pinned layer, a spacer layer, and a free layer are partially oxidized from the side of the stacked body. As a result, there exists an oxidized region for interrupting the electric current in the direction perpendicular to a layer surface, in both sides of each layer; and there remains a non-oxidized region for passing the electric current in the direction perpendicular to the layer surface, in the central part of each layer. Thus, in the configurations of Japanese Patent Application Laid-Open No. 2005-136309 and Japanese Patent Application Laid-Open No. 2002-176211 as well, the electric current in the direction perpendicular to the layer surface only passes through a specific part (that is current control region or non-oxidized region) inside the spacer layer. In other words, the spacer layer has a function of restricting the electric current by confining the path for the electric current to pass, and consequently increases a resistance value.
As described above, in configurations according to the above described four patent documents, a spacer layer increases a resistance value by the function of confining electric current, and thereby increases the amount of resistance change.
In a CCP-CPP-GMR element, an electric current value in a direction perpendicular to a layer surface varies, in other words, a resistance value varies according to the size of a current confining part. The amount of resistance change is dependent on the change of the electric current, and furthermore, the sensitivity of the magneto-resistance effect element is also dependent on the change of the electric current. Accordingly, in order to obtain a magneto-resistance effect element having the desired sensitivity, the current confining part needs to be formed with high accuracy.
In a configuration described in Japanese Application Patent Laid-Open No. 2002-208744 among the above described conventional CCP-CPP-GMR elements, a resistance adjustment layer of an aluminum oxide layer having pinholes is formed, for example, by the steps of forming an aluminum layer and exposing the aluminum layer to an oxygen atmosphere to make self oxidation. The resistance adjustment layer can also be formed by another method comprising the steps of forming one or more copper pillars on a copper layer that makes up the spacer layer; and filling a perimeter of the pillar with an insulation material (oxide, for instance). The resistance adjustment layer can also be formed by still another method comprising the steps of forming an insulative layer that has previously opened pinholes on the copper layer that makes up the spacer layer. However, it is very difficult to form a resistance adjustment layer having pinholes with the appropriate number and size uniformly distributed therein by these methods.
In addition, in Japanese Patent Application Laid-Open No. 2003-204094, the configuration is formed, for instance, by the steps of preparing a copper layer as a spacer layer, forming a magnetic metal film by sputtering, and introducing oxygen gas, so that an insulative material which makes up oxidized parts and a magnetic metal which makes up unoxidized parts are distributed in a mixed state. In this method, it is difficult to precisely and uniformly distribute the oxidized parts of the insulative material, and to precisely and uniformly distribute the unoxidized parts of magnetic metal without being oxidized, in the magnetic metal film at an appropriate ratio.
In a configuration described in Japanese Patent Application Laid-Open No. 2005-136309, it is necessary to irradiate Ar ion beam with high accuracy, and to completely oxidize a part which has not been irradiated with the Ar ion beam. When the Ar ion beam has been irradiated with low accuracy, or when the part which has not been irradiated with the Ar ion beam remains insufficiently oxidized, a current confining part can not be formed with high accuracy, and the obtained magneto-resistance effect element does not show the desired sensitivity.
In the configuration described in Japanese Patent Application Laid-Open No. 2002-176211, when a SV film is oxidized (or nitrided or oxynitrided) up to an inaccurate depth from the side of the SV film, a current confining part can not be formed with high accuracy, and the resulting magneto-resistance effect element does not show the desired sensitivity.
A recent magneto-resistance effect element is so small that the length of one side is about several tens of nanometers. Accordingly, it is difficult to form a highly precise current confining part inside a spacer layer of the magneto-resistance effect element by the methods described in the above four patent documents. In other words, it is very difficult to form extremely fine pinholes with high accuracy based on the method of Japanese Patent Application Laid-Open No. 2002-208744, to oxidize a magnetic metal film at an appropriate ratio based on the method of Japanese Patent Application Laid-Open No. 2003-204094, to precisely irradiate an ion beam and completely oxidize an unirradiated part based on the method of Japanese Patent Application Laid-Open No. 2005-136309, and to precisely oxidize (or nitride or oxynitride) an SV film from the side of the SV film by the desired depth based on the method of Japanese Patent Application Laid-Open No. 2002-176211. Accordingly, it is actually difficult to obtain the desired current confining effect and the desired sensitivity in an extremely fine magneto-resistance effect element by the four methods. Besides, in the configurations described in those patent documents, an unprecedented, special, and complicated step must be done for the purpose of forming the current confining part. As a result, the manufacturing cost increase.

Magneto-resistance effect element with a stacked body having a constricted shape


A flexible interposer for the attachment of a microelectronic package to a microelectronic socket, wherein a first portion of the flexible substrate may be positioned between the microelectronic package and the microelectronic socket, and a second portion of the flexible interposer may extend from between the microelectronic package and the microelectronic socket to electrically contact an external component. In one embodiment, the external component may be a microelectronic substrate and the microelectronic socket may be attached to the microelectronic substrate.

The microelectronic industry is continually striving to produce ever faster and smaller microelectronic structures for use in various mobile electronic products, such as portable computers, electronic tablets, cellular phones, digital cameras, and the like. Microelectronic packages, such packages including a microprocessor, a chipset, a graphics device, a wireless device, a memory device, an application specific integrated circuit, or the like, may be attached to a microelectronic substrate through a microelectronic socket mounted to the microelectronic substrate. However, for a given sized microelectronic socket, there are a limited number of interconnects can be formed through the microelectronic socket to provide conductive routes between the microelectronic package and the microelectronic substrate. This can create significant constraints with regard to mounting high input/output microelectronic packages using microelectronic sockets.


An actuator mechanism for operating the shutter door of a torpedo tube indes two hydraulic cylinders connected in series and a plurality of interconnected links pivotally connected between the inner hull and the shutter door. In operation, the combined movement of the hydraulic cylinders rotates an elongated torque arm and a transfer link about a rotatable shaft. As the transfer link rotates it moves the end of the link inwardly away from the outer hull. As the transfer link further rotates away from the outer hull, it draws the connector link and the shutter door inwardly. The added throw of the two cylinders cooperate with the longer torque arm to provide an increased moment, and hence greater opening force on the shutter door.

(1) Field of the Invention
The instant invention relates to submersible vessels and more particularly to an actuator mechanism for operating a torpedo tube shutter door.
(2) Description of the Prior Art
Referring to the drawing FIGS. 1 and 2, the prior art actuator mechanism for operating a hinged torpedo tube shutter door 10 is illustrated and it is generally indicated at 12. It is noted that FIG. 1 shows the mechanism 12 in the closed position and that FIG. 2 shows the mechanism 12 in the open position. The torpedo tube shutter door 10 is a long rectangular shaped fairing plate which streamlines the outer hull 14 of a submarine when the submarine's torpedo tube outer door is closed. The shutter door 10 is necessary to prevent flow turbulence in the flow field of the submarine as it propels itself through the water. Prior to firing a torpedo, the shutter door 10 is opened to provide a clear path for the torpedo to be ejected from within the ship. It is noted that the shutter door 10 is not a pressure containing door as this function is accomplished by a much stronger pressure sealed torpedo tube muzzle door. In addition, there is no pressure seal between the shutter door 10 and the outer hull 14. Therefore, there are no forces on the shutter door 10 which are attributable to sea pressure. However, the shutter door 10 is subjected to hydrodynamic flow over its surface. Since the firing line 16 of an ejected torpedo typically intersects the outer hull 14 at an angle anywhere from 12.degree. to 14.5.degree., the shutter door 10 may be quite long, and therefore the hydrodynamic forces exerted thereon can be quite significant. For example, if the flow velocities across a shutter door produce a 10 psi pressure differential, then a 30 sq. ft. shutter door (4320 sq. in.) would have to overcome a 43,200 pound force plus the shutter's own weight and any system binding forces before it could be operated. While the shutter door is not a pressure containing member, it is designed to be relatively stiff via the use of stiffening members to prevent shutter vibration and deflection and therefore a shutter door may weigh between 1500 and 1800 pounds.
In the existing prior art assembly as illustrated in FIGS. 1 and 2, the power to operate the mechanism 12 comes from a hydraulic cylinder 17 through a power transmission link 18 which provides force to overcome the system moments and weights, forces due to misalignment and binding parts, and the hydrodynamic loads on the shutter door 10 due to the ship's forward motion through the water. Although the system moments and weights can be accurately calculated prior to the actual manufacture of the hardware, the forces due to misalignment and binding of the parts are difficult to calculate due to the varying deflection of parts with varying ship's depths and manufacturing tolerances. The quantification of hydrodynamic loads is equally as difficult to calculate because the hydrodynamic flow, pressure points, and flow vortices vary with different ship's speeds and maneuvers, and varying positions of the shutter door 10 between the fully open and fully closed positions. Unfortunately, the only accurate method to determine these forces is to conduct a full scale ship's test. However, not even a ship's test is 100% accurate due to the variations in construction between like ships in a class. Even if these variation were ignored, such a test would be extremely expensive and could only be conducted after it was too late to incorporate the results into the ship's basic design.
The prior art shutter mechanism 12 is pivotably connected between the inner hull 20 and the shutter door 10 via a series of interconnected links which draw the shutter door inwardly when force is applied through the hydraulic cylinder link 18. In operation of the mechanism 12, the hydraulic cylinder link 18 exerts force to the right as viewed in the drawings figures. The hydraulic cylinder link 18 is pivotably connected to links 22 and 24, and link 22 is pivotally connected to the inner hull 20 at pivot point 26. Movement of hydraulic cylinder link 18 to the right pivots link 22 counterclockwise about point 26 and forces link 24 to the right. Link 24 is pivotably connected to a torque arm 28. The torque arm 28 and a transfer link 30 are keyed to a common shaft 32 which rotates about pivot point 34. Therefore, when link 24 moves to the right, it pivots both links 28 and 30 counterclockwise about pivot point 34. Link 30 is pivotably connected to a connector link 36 at pivot point 38, and link 36 is in turn pivotably connected to the shutter door 10 at pivot point 40. As link 30 rotates in a counterclockwise direction, it moves the end of the link, i.e. pivot point 38, inwardly away from the outer hull 14. As link 30 further rotates away from the outer hull 14, it draws link 36 and the shutter door 10 inwardly. The shutter door 10 is pivotably connected to the outer hull 14 at pivot point 42, and is thus free to move inward as it rotates about pivot point 42. It is necessary to utilize this complex linkage system to prevent the shutter door 10 from inadvertently opening inward due to wave slap. It is pointed out that in the fully closed position, pivot point 38 is located slightly to the left of a straight line drawn between pivot point 34 and pivot point 40. This arrangement permits force from wave slap to be transmitted via the linkage to hydraulic cylinder link 18 which has a positive stop, thus preventing it from moving in the direction of the force. Therefore, it can be seen that the shutter door 10 will not open due to wave slap.
Because of the difficulty in accurately calculating all the potential forces which are exerted on the shutter door, it has been found that the power generated by the prior art mechanism is often insufficient to operate the shutter door under all operating conditions. This flaw in the prior art mechanism can cause significant problems because the inability to operate the shutter door prevents a submarine from being able to fire its torpedoes.
Several solutions to the problem have previously been suggested. The most obvious method to eliminate the torque problems of operating a shutter door would be to replace the hinged shutter doors with rotating shutters. However, this solution is plagued by several problems which relate to the large physical size of rotating shutters. The larger size of a rotating shutter would require extensive modifications of the forward portions of the ship in order to fit the rotary shutter in place. Such extensive ship modifications, whether in a new ship or an existing ship, are cost prohibitive. In addition, there are also problems associated with misalignment of the shutter and deflection of parts.
Another possible solution is to utilize a larger and more powerful hydraulic cylinder 17 to operate link 18. If a larger, more powerful hydraulic cylinder 17 was backfit into an existing design, the larger cylinder 17 would most likely have a larger shaft size. The added power and increased shaft size would require that all the components interconnected with the hydraulic cylinder 17 be strengthened in a like manner. Such a design would also most likely require new support bearings, a new hull stuffing box, and replacement of all the interlock mechanisms, pins, and hinges which transmit or have force applied to them. As a result such a design would be very costly to implement. If the larger hydraulic cylinder 17 were integrated into a new ship construction, it is quite likely that the larger stronger components would not fit in the same space available and thus the forward portions of the ship would also have to be redesigned.
Still another possible solution is to lengthen the travel of the hydraulic power cylinder 17 to facilitate a better mechanical advantage to the shutter door linkage. This type of design is also plagued by a multitude of problems. If the longer hydraulic cylinder were backfit into an existing ship, the increased travel distance would require the shaft bearing supports to be spaced further apart. In addition, the interlock system, support brackets, links, and hinge pivot points would have to be relocated to be compatible with the modified cylinder travel. If it were possible to fit these modified parts into the existing space available, then cost, shock, and timing requirements would have to be addressed. This design would also likely require the use of a larger hydraulic cylinder to withstand shock loads. In addition, the increased travel distance would also cause a longer actuation time due to increased travel length. This could be a critical factor in situations where it is desired to quickly fire weapons in an emergency.
Yet another potential solution for correcting the problem in an existing ship would be to redesign some components to minimize assembly binding and to control pressure differentials caused by hydrodynamic flow. The problem with this solution is that it is impossible to ensure complete system alignment at all depths of operation and to ensure maintenance of system alignment as components wear. In addition, once a ship system is designed, it is difficult to significantly alter the forces resulting from hydrodynamic flow.
In spite of the previously noted alternatives, it is still possible that the shutter doors would not operate under all conditions. Such a failure could result because it is impossible to determine with 100% accuracy all the forces which will be exerted on an operational shutter door.

Actuator mechanism for operating a torpedo tube shutter door

The United States of America as represented by the Secretary of the Navy

92
FSC 91
FSC 114
FSC 440
FSC 49
FSC 105


A semiconductor device includes a first pad region including a plurality of first storage nodes, a second pad region neighboring the first pad region and including a plurality of second storage nodes, a coupling portion disposed between the first pad region and the second pad region, and a plate electrode disposed over the plurality of first storage nodes of the first pad region and the plurality of second storage nodes of the second pad region, and disposed in the coupling portion to interconnect the first pad region and the second pad region.

Generally, highly-integrated semiconductor devices have been formed by stacking conductive layers (for example, a conductive layer including a metal film and an insulation layer), and by interconnecting stacked conductive layers. The number of stacked conductive layers increases as these semiconductor devices become more precise and complicated. After the desired number of conductive layers are stacked, a bonding pad having a multi-layer structure that includes a plurality of conductive films is formed.
The bonding pad has a line structure disposed over a surface of the integrated circuit and is configured to provide a contact surface between an external pin lead and an internal circuit of the semiconductor device. A bonding wire provides an electrical contact between the pin lead and the bonding pad. During attachment of the bonding wire to the bonding pad, an end portion of the bonding wire is positioned to contact the bonding pad using a precise position adjustment machine. The machine exerts force on the bonding pad and causes deformation of an internal portion of the semiconductor device. For example, a lower portion of a pad region including a metal-oxide-semiconductor (MOS) capacitor and a specific circuit, which are used to reduce noise of the semiconductor device, may deform until a defect such as a crack or a void occurs in the semiconductor device. As a result, a micro bridge may form in the pad region and the peripheral region. In addition, as the degree of integration increases, the size of a region between two neighboring pad regions is reduced, and it becomes more difficult to form one or more conductive lines between the pad regions.

Semiconductor device and method for forming the same


An evapotranspiration mitigation method, system, and computer program product include checking a condition via a first sensor connected to an outside of a device to compute an evapotranspiration level and activating a roof opening of the device to deploy a roof from the device if the evapotranspiration level is greater than a pre-determined threshold.

The present invention relates generally to an evapotranspiration mitigation method, and more particularly, hut not by way of limitation, to a system, method, and computer program product for controlling an enclosure containing sensors for evapotranspiration computation (such as air temperature, relative humidity, wind speed, soil moisture, etc.) and a retractable mechanical surface (e.g., side or roof).
In agriculture operations, water and sunlight are the most essential input. On a daily basis, a significant amount of water is lost due to evapotranspiration from soil and plants. Evapotranspiration can be measured and modelled, given its dependency to atmospheric variables such as solar radiation, temperature, wind, etc. However, conventional techniques only consider water saving techniques without taking into account evapotranspiration.

INTERNATIONAL BUSINESS MACHINES CORPORATION


A method of enabling a knowledge management community. A community is originated based on a vision of values and benefits that can be realized from the organized sharing of knowledge within a common group of people. The group is defined based on subject matter, interest, geography, or any other category. Based on the vision of a community, an initial definition of the community is created, including a community charter. Based on the community charter, the community is designed. The design of the community includes creating a matrix showing processes performed by members of the community and the outcomes of these processes, developing knowledge maps that show the knowledge used and created in performing processes, and defining metrics to measure the benefit derived from the sharing of knowledge within the community.

Knowledge is one of the most important assets of any organization. In the information age, it can hardly be disputed that knowledge is value. It has been speculated that the ability of an enterprise to capture and share knowledge, and its ability to reuse, reinvent and innovate using that knowledge, will become a key determinant and predictor of the enterprise's value in the near future.
Knowledge management (KM) refers to a system for the codification, creation, storage, structuring, dissemination, application and sharing of an organization's knowledge assets. Knowledge management is, in some sense, a system for formally accounting for an organization's intellectual capital. Despite the clear importance of knowledge to any organization, such knowledge management systems have not gained widespread acceptance.
A principal reason why knowledge management is not widely used is that existing knowledge management techniques are not tightly bound with the business processes to which they relate, and thus are often perceived by those who must use them as unwieldy appendages. For example, an attempt to introduce knowledge management into an organization may fail because the knowledge management process is viewed by the people who must carry it out as a non-integrated separate project rather than a systemic change in the way work is performed. Within a business, there may be employee resistance to corporate initiatives. The management commitment for knowledge management may wane—particularly if the champion of knowledge management has left the organization, or if the benefits of knowledge management are not quickly and visibly realized. Similarly, since knowledge management must be carried out by the employees who participate in knowledge-using and knowledge-generating processes, employees may resist the knowledge management activities if the employees are not involved in the planning of the knowledge management system.
In view of the foregoing, there is a need for a technique for creating a sustainable knowledge management system that overcomes the drawbacks of the prior art.


A quick-to-the-ground integrated vehicle leveling and stabilizing apparatus which may be easily and accurately connected to the underside of a vehicle and which may be extended to an operative position and retracted to a storage position with a minimum of operator time and effort. The components of the present invention are self-aligning so that upon being extended to the operative position, the components are automatically properly positioned for the subsequent leveling and stabilizing operations. The apparatus has integral components that need not be separated from the leveling and stabilizing apparatus itself when the apparatus is retracted to a storage position. Furthermore, the apparatus has increased strength and durability relative to known devices.

Vehicle leveling and stabilizing devices of the type that are attached to the underside of a vehicle for use when the vehicle is at rest are generally well known. These devices include a horizontal cross member for attachment to the underside of a vehicle with a support leg pivotally connected to the cross member. When deployed to support or partially support the weight of a vehicle, a screw jack assembly including a support strut and screw member extends between the support leg and the cross member to brace the support leg away from the cross member to support the vehicle weight. The screw jack assembly is operated to extend/retract the support leg and associated strut relative to the undercarriage of the vehicle to which the apparatus is connected. Recreational vehicles such as trailers and motor homes commonly include one or more of these devices for stabilizing the vehicle when it is at rest. The leveling and stabilizing apparatus is deployed to support or partially support the vehicle weight such that the movement of the vehicle over its resilient suspension in response to the movement of the occupants within the vehicle, for example, is minimized when the vehicle is at rest. Furthermore these devices are utilized to level the vehicle relative to the surface of a parking lot or camp site to improve the comfort of the occupants.
While known leveling and stabilizing devices are generally effective, there has been found a need to provide an integrated vehicle leveling and stabilizing apparatus that may be extended to an operative position and retracted to a storage position with a minimum of operator time and effort without sacrificing strength and durability. Known devices require the operator thereof to slowly extend and retract the support legs of the stabilizing devices with time consuming operation of the screw jack assembly. Another known device includes a support strut and screw jack assembly that must be separated from the stabilizing device when the device is not in use resulting in inconvenience and the potential for misplaced screw jack components. There has also been found a need to provide a leveling and stabilizing apparatus which has superior strength and durability over known devices.
Known leveling and stabilizing devices as described above also lack an effective mechanism for easily and accurately mounting the devices to the underside of a vehicle. Thus, there has also been found a need to provide a vehicle leveling and stabilizing apparatus that is adjustable to fit on vehicles having different widths. Likewise, there has also been found a need to provide a vehicle leveling and stabilizing apparatus, the lateral position of which relative to the underside of the vehicle may be adjusted to compensate for vehicle manufacturing intolerances.

Vehicle leveling and stabilizing apparatus


This polishing apparatus includes a head that holds a semiconductor wafer, a polishing pad that polishes a surface to be polished of the semiconductor wafer held by the head, and a dresser that reconditions the polishing pad by cutting the polishing pad. The polishing apparatus polishes a surface to be polished of the semiconductor wafer while causing the head and the polishing pad to rotate and reconditions the polishing pad by use of the dresser before and after polishing the surface to be polished. The polishing apparatus of the present invention supports at least two dressers so that the dressers can rotate on their own axes and further includes a dresser oscillator that causes the dressers to oscillate simultaneously on the polishing pad.

1. Field of the Invention
The present invention relates to a CMP (chemical mechanical polishing) apparatus that polishes wafers in the manufacturing process of semiconductor devices, and a dresser that reconditions a polishing pad provided in a CMP apparatus.
2. Description of the Related Art
The surface of a polishing pad is worn down during wafer polishing in the CMP process and, therefore, it is inevitable to perform reconditioning by the use of a dresser. Under the present circumstances, one dresser is arranged for one polishing pad and reconditioning is performed by causing the polishing pad and the dresser to rotate on their own axes.
FIG. 1 is a sectional view of a CMP apparatus of a related art in which one dresser is arranged, and FIG. 2 is a plan view of FIG. 1. As shown in these figures, the CMP apparatus has polishing head 1 that produces a polishing action by pushing the surface of wafer 2 against polishing pad 5. Polishing head 1 is provided with retainer ring 3 that holds wafer 2 that is being polished and is provided with membrane 4 that applies pressure to a rear surface of wafer 2 that is being polished. In order to ensure that the whole surface of semiconductor wafer 2 is evenly depressed onto the surface of polishing pad 5, polishing head 1 is also provided with periphery pressurizing portion 6 that pressurizes the periphery of wafer 2. During polishing, a rotational motion is given to polishing head 1, and also polishing pad 5 is rotatably driven around a center portion of the polishing pad.
A slurry supply port 7 that supplies slurry (an abrasive) is present on the polishing pad 5 and a dresser 8 that reconditions the polishing pad 5 is also arranged thereon.
To recondition polishing pad 5, this dresser 8 oscillates on polishing pad 5 in the range of the radius of polishing pad 5 while rotating on its own axis as shown in FIG. 2, thereby performing the cutting of polishing pad 5. For this reason, the reconditioning time becomes long in proportion to the size of polishing pad 5 and the dresser life relative to the number of treated wafers decreases.
To extend the life of a polishing pad and stabilize the polishing rate, Japanese laid-open patent publication No. 11-48122 proposes a technique for using two kinds of dressers for one polishing pad as a related art.
However, conventional CMP apparatus have had the following problems.
The dresser reconditions the polishing pad by cutting the polishing pad while oscillating within the radius of the polishing pad in the spare time when the wafer is being conveyed before and after polishing. For this reason, the larger the diameter of the polishing pad, the longer the required reconditioning time will be, and the throughput of the CMP apparatus will decrease by just that much.
Also, when a dresser is used, the edge of diamond abrasive grains fixed to a bottom surface of the dresser becomes dull and the cutting capacity of the polishing pad decreases. When the polishing pad diameter increases, the cutting time becomes long and, therefore, the cumulative number of treated wafers per dresser decreases. Furthermore, it is necessary that dresser replacement be performed in accordance with the procedure of replacement work, simulation polishing and checking the polishing rate/uniformity of polishing/dust/scratches and the like, and the apparatus comes to a stop for about 4 hours once the replacement is made. Therefore, it follows that the apparatus stop time (downtime) also increases with increasing frequency of dresser replacement.

Polishing apparatus and method of reconditioning polishing pad


A rip guide for a circular saw. The circular saw includes a housing including a shoe plate for supporting the circular saw on a workpiece. The circular saw also includes a motor supported by the housing and a saw blade rotatably driven by the motor about an axis. The saw blade is operable to cut the workpiece in a cutting direction. The guide comprises a support member supported on the housing; an arm supported by the support member and extending from the housing in the cutting direction; and a guide member supported by the arm so that the guide member is pivotally supported by the support member. The guide member extends from the housing in the cutting direction. The guide member includes first and second guide surfaces for selectively guiding the circular saw relative to first and second edges, respectively, of the workpiece. The guide member is pivotable between a working position and a stored position. As the saw blade cuts the workpiece with the guide member in the working position, the guide member does not cause the saw blade to bind on the workpiece and does not obscure the operator's vision of the saw blade.

This invention relates to circular saws and, more particularly, to a rip guide for a circular saw.
A typical rip guide for a circular saw is disclosed in U.S. Pat. No. 2,800,933. The rip guide includes an elongated, straight guide plate connected to a support member shaft. The shaft is supported on the base plate of the circular saw and extends over the lateral edge of the base plate so that the guide plate extends parallel to the lateral edge of the base plate and along a portion of the saw blade. The guide plate is rotatable between a working position in which it is disposed below the plane of the base plate of the circular saw so as to be located for functioning as a rip guide, and a non-working position, in which the guide plate is disposed wholly above the plane of the base plate so that the guide plate does not interfere with the travel of the circular saw across a workpiece.


A relatively inexpensive and reliable latching mechanism for locking or otherwise securing a tailgate to the cargo area of a vehicle or trailer is provided comprised of a latch plate of unitary construction and a locking pin. The latch plate is further comprised of a mounting base having means for attachment to the vehicle or trailer sidewall and an offset projecting lug having a lanced tab for receiving the locking pin. In a preferred embodiment, the mounting base is attached to the vehicle side wall and the lanced tab projects through a complimentary closed slot in the tailgate and receives the locking pin thereby securing the tailgate between the offset, the projecting lug and the lanced tab. The offset projecting lug creates a space between the vehicle side wall and the projecting lug which traps a portion of the tailgate which forms the closed slot therebetween to add additional strength and stability to the attachment.

Latching mechanisms for attaching a tailgate to a utility trailer or to the cargo bed of a pickup truck are known in the art. Many elaborate and expensive systems which include a hinged attachment along one border of the tailgate and a separate locking mechanism are prevalent in the industry as seen with the standard tailgate of a pickup truck, e.g, a Ford or General Motors product.
Often times when removal of the tailgate is desired the hinged portion must be manually disconnected leaving exposed hardware attached to the cargo body which interferes with substantially unobstructed access to the cargo area. Likewise, there may be hardware associated with the hinges or the latching mechanism which remains attached to the tailgate which interferes with convenient storage. This is especially true with the tailgate assembly of many commercially available utility trailers
Accordingly, there exists a need in the art for a reliable, inexpensive latching mechanism which allows for quick attachment and removal of the tailgate that does not require the removal of hardware which otherwise protrudes into or obstructs access to the cargo area.


The present invention provides an improvement to the two, inaccurate, traditional approaches relating concentration to density. The first of these assumes that the solute is completely insoluble in the solvent; the second is based on a soluble solute. The present improved relationship is referred to as the CONCENTRATION-DENSITY MODEL. This model allows for a theoretical determination of the concentration-density relationship for a multi-component solid/liquid or liquid/liquid mixture. Included in the Concentration-Density Model is a new concept referred to as ADDITIVE VOLUME COEFFICIENT (AVC). This concept compensates for the fact that the net volume of a mixture does not always equal the sum of the volumes of each component. This improved Concentration-Density Model provides fluid-handling manufacturers with a method for accurately determining a mixture""s concentration on-line with the aid of current density measurement instrumentation. By allowing for accurate concentration determination in manufacturing scenarios where such measures were previously impractical, the present invention enables improved control of the manufacturing process.

This invention relates to the determination of the concentration of a multi-component solid/liquid or liquid/liquid mixture. It can be applied to any situation where the density of such a mixture is known or can be determined. This invention provides a means for improving the control of a continuous process which handles such a mixture and is dependent on the mixture""s concentration, and can thus assist manufacturers in effectively monitoring and operating their processes. Data generated by this invention can be used to: control a known process fluid to a targeted concentration, for instance in a paper coating process; verify on-line the accuracy of batchwise or continuous ratio blends in the manufacture of such products as food products (ketchup, mayonnaise, syrup), personal care products (skin cream, shampoo), pharmaceutical products, paints, petroleum blends, and the like; and eliminate the excessive empirical work necessary with density monitoring process control systems.
The solute content of a solid/liquid or liquid/liquid mixturexe2x80x94commonly expressed as the mixture""s concentrationxe2x80x94can be determined from the mixture""s true density utilizing a relationship that exists between the mixture""s concentration and density. This relationship consists of a linear correlation between a mixture""s concentration and density, which is unique to each mixture. Stated generally, a unique, linear relationship exists for any solute/solvent mixture (solution or slurry).
Defined hereinbelow is an improvement to the two inaccurate, traditional approaches relating concentration to density. The first, the Non-linear Model, assumes that the solute is completely insoluble in the solvent. The second, the Linear Model, is based on a soluble solute. The present improved relationship is referred to as the CONCENTRATION-DENSITY MODEL. This model allows for a theoretical determination of the concentration-density relationship for a multi-component solid/liquid or liquid/liquid mixture. Included in the Concentration-Density Model is a new concept referred to as ADDITIVE VOLUME COEFFICIENT (AVC). This concept compensates the Non-linear Model for the fact that the net volume of a mixture does not always equal the sum of the volumes of each component.
As described in detail herein, this improved Concentration-Density Model provides fluid-handling manufacturers with a method for accurately determining a mixture""s concentration on-line with the aid of current density measurement instrumentation. The Concentration-Density Model of the present invention allows for accurate concentration determination in manufacturing scenarios where such measures were previously impractical. These concentration measurements can then be used to control the manufacturing process.
It is common for a solid/liquid mixture""s concentration to be determined in a laboratory by measuring the weight of a sample both before and after evaporating the liquid phase of the mixture. This approach can be very accurate, but must occur off-line which results in a significant time delay between the time of sampling and the time of measurement. This time delay decreases the number of manufacturing applications where this measurement is useful.
Other methods, either off-line or on-line, determine concentration indirectly. A property of a solid/liquid or liquid/liquid mixture (e.g., density, gamma radiation absorption, and so on) is empirically correlated to a mixture""s concentration. The mixture""s concentration can then be calculated from a measurement of that property (on-line or off-line).
All of these methods, however, face certain challenges. For the sake of accuracy, each mixture to be measured requires the empirical determination of the relationship between the mixture""s concentration and density. When many mixtures are involved, this can result in a great deal of upfront effort. To minimize this upfront effort, one of two models relating a mixture""s concentration to its density is commonly used.
NON-LINEAR MODEL (Insoluble, Two-component System):
Modeling the case of a mixture (M) where the solute (S) is completely insoluble in the solvent (L), the volumes (V) are additive:
VM=VS+VLxe2x80x83xe2x80x83Eq.1
Therefore:                                           m            M                                ρ            M                          =                                                            m                M                            ·                              x                S                                                    ρ              S                                +                                                    m                M                            ·                              (                                  1                  -                                      x                    S                                                  )                                                    ρ              L                                                          Eq.  2-1
where: m=mass, and, xcfx81= density;
or,                               1                      ρ            M                          =                                            x              S                                      ρ              S                                +                                    1              -                              x                S                                                    ρ              L                                                          Eq.  2-2
Solving Eq. 2-2 for the mixture""s solute content, xs:                               x          S                =                                            ρ              S                                                  (                                                ρ                  M                                -                                  ρ                  L                                            )                                                          ρ              M                                                  (                                                ρ                  S                                -                                  ρ                  L                                            )                                                          Eq.  3
Eq.3 can be rewritten as:                               x          S                =                                            ρ              S                                      (                                                ρ                  S                                -                                  ρ                  L                                            )                                -                                                                      ρ                  S                                ·                                  ρ                  L                                                            (                                                      ρ                    S                                    -                                      ρ                    L                                                  )                                                                xe2x80x83                                                  (                              1                                  ρ                  M                                            )                                                          Eq.  4
Therefore, on a plot comparing the mixture""s concentration to the inverse of it""s density:       Slope    =                            ρ          S                ·                  ρ          L                            (                              ρ            S                    -                      ρ            L                          )              ;      xe2x80x83                y                    -                  Intercept        =                  ρ        S                    (                              ρ            S                    -                      ρ            L                          )
LINEAR MODEL (Soluble, Two-component System):
Modeling the case of a mixture (M) where the solute is considered soluble in the solvent, it is assumed that the density of the mixture varies linearly from the density of the pure solvent (L) to the density of the pure solute (S), based on the mass ratio of the two components.
This model is expressed as:                               x          S                =                                            ρ              M                        -                          ρ              L                                                          ρ              S                        -                          ρ              L                                                          Eq.  5-1
which can be re-written as:                                           x            S                    =                                    -                                                ρ                  S                                                                      ρ                    S                                    -                                      ρ                    L                                                                        +                                          ρ                M                                                              ρ                  S                                -                                  ρ                  L                                                                                xe2x80x83                                    Eq.  5-2
Therefore, on a plot comparing the mixture""s solids content to the it""s density:       Slope    =          1                        ρ          S                -                  ρ          L                      ;      xe2x80x83                y                    -                  Intercept        =          -                        ρ          L                                      ρ            S                    -                      ρ            L
In both of the above, the formula components are defined as follows:
VM=Total System Volume (Volume of Mixture)
VS=Volume of the Solute
VL=Volume of the Solvent
mM=Total System Mass (Mass of Mixture)
xS=Mass Fraction of the Solute
xL=Mass Fraction of the Solvent
xcfx81M=Density of Mixture
xcfx81S=Absolute Density (not Bulk Density) of Solute
xcfx81L=Density of Solvent
However, both of these common models used make erroneous assumptions. In the Non-Linear Model, it is assumed that the volumes of the components are completely additive, meaning that the components are completely insoluble in each other. This is very rarely the case. Most real world cases employ a solution of soluble or partially soluble solutes. In these cases, this model tends to overestimate the solution""s concentration. In the Linear Model, the assumption fails because it does not compensate for the molecular interactions between the solute and the solvent. In either case, the assumptions often introduce enough error to render the results useless, as shown in Table 1.
The present invention provides a new method for predicting the concentration of a solid/liquid or liquid/liquid mixture by use of the mixture""s true density. This method makes use of a model, referred to herein as the Concentration-Density Model, which is an improvement over current methods of relating a mixture""s concentration and density. This model introduces a novel concept referred to as the Additive Volume Coefficient (AVC), which reflects the change in volume that occurs after dissolving or mixing a solute into a solvent. The AVC is an important concept and provides this method with advantages over current technology.
The present invention provides a more accurate measurement of concentration than current technologies, and applies to a wider range of applications. As a result, the present invention, when coupled with an on-line measurement of solution density, provides accurate, continuous, real time feedback of a process fluid""s concentration. This measurement is valuable to various industries in that it can assist manufacturers in effectively monitoring and operating their processes. Specifically, this data can be used, based on the manufacturing process, to do such things as:
1) control a known process fluid to a targeted concentration, e.g. in a paper coating process,
2) verify on-line the accuracy of batchwise or continuous ratio blends such as food products (ketchup, mayonnaise, syrup), personal care products (skin cream, shampoo), paints, petroleum blends, etc., and
3) eliminate excessive empirical work necessary with density monitoring process control systems.
The present invention is an improvement in that it more accurately converts a measured mixture density (xcfx81M) to concentration (m) through the formula:   m  =            1              (                  1          -                                    ρ              L                                                                  ∑                                  i                  =                  1                                n                                                          xe2x80x83                                                                                k                    i                                                                          x                    i                                                                                (                                          ρ                      S                                        )                                    i                                                                    )              -                            ρ          L                          (                      1            -                                          ρ                L                                                                            ∑                                      i                    =                    1                                    n                                                                  xe2x80x83                                                                                k                      i                                                                                x                      i                                                                                (                                              ρ                        S                                            )                                        i                                                                                )                                  (                  1                      ρ            M                          )
wherein xcfx81L is the (temperature-dependent) density of the solvent, ki is the Additive Volume Coefficient for each solute, xi is the weight-% dry for each solute, (xcfx81S)i is the (temperature-dependent) density of each solute, and xcfx81M is the (temperature-dependent) density of the mixture.

Mixture concentration control in manufacturing processes


A method for carrying out gearshifting of a bicycle derailleur through an actuation device is described that utilizes a mobile mechanical member to control the derailler. Every gearshifting operation corresponds to a movement of predetermined amount of the mobile member. The method is carried out by the steps of an active initial movement of the mobile member for a first amount equal to only a portion of the amount of the movement corresponding to gearshifting; and an automatic final movement of the mobile member for a second amount equal to the remaining portion of the amount of the movement corresponding to gearshifting. Devices capable of implementing such a method are also described.

A bicycle is normally provided with a rear derailleur associated with the pinion group, which consists of a series of coaxial toothed wheels (crowns), having different diameters and numbers of teeth, integral with the hub of the rear wheel.
A bicycle is typically also provided with a front derailleur associated with the chainset, which consists of a series of toothed wheels (crowns) having different diameters and numbers of teeth, associated with a shaft of the crank axle rotated by a pair of pedals.
In both cases, the derailleur engages a transmission chain extending in a closed ring between the pinion group and the chainset, moving it on to sprockets having different diameters and number of teeth, so as to obtain different transmission ratios.
In particular, downward gearshifting or downshifting refers to when the chain passes from a sprocket having a larger diameter to a sprocket having a smaller diameter, and upward gearshifting or upshifting refers to when the chain moves from a sprocket having a smaller diameter to a sprocket having a greater diameter. In this respect, it should be noted that with reference to the front derailleur, downward gearshifting corresponds to the passage to a lower transmission ratio and upward gearshifting corresponds to the passage to a higher transmission ratio, vice-versa with reference to the rear derailleur, downward gearshifting corresponds to the passage to a higher transmission ratio and upward gearshifting corresponds to the passage to a lower transmission ratio.
The movement in the two directions of a derailleur is obtained through an actuation device mounted to allow easy operation for the cyclist, i.e. normally on the handlebars, close to the handlebar grip where the brake lever for commanding the braking of the front or rear wheel is also located. Control devices that allow both a derailleur to be driven in the two directions and a brake to be controlled are, as mentioned above, commonly known as integrated controls.
Customarily, the actuation device of the front derailleur and the brake lever of the front wheel are located by the left-hand grip of the handlebars, and vice-versa the actuation device of the rear derailleur and the brake lever of the rear wheel are located by the right-hand grip.
More specifically, in a mechanical gearshift, each derailleur is moved between the sprockets, in a first direction by a traction action exerted by a normally sheathed inextensible cable (commonly known as Bowden cable), in an opposite second direction by the release of the traction of the cable and/or by the elastic return action of a spring provided in the derailleur itself.
Normally, the direction in which the movement is determined by the release of the traction of the cable and/or by the return spring is that of downward gearshifting; vice-versa, the traction action of the control cable takes place in the direction of upward gearshifting, in which the chain moves from a sprocket having a smaller diameter to a sprocket having a larger diameter.
In the actuation device, the control cable is actuated in traction or in release through winding and unwinding on a rotor element, commonly known as cable-winding drum, the rotation of which is controlled by the cyclist by a pair of suitable control levers.
In any case, the actuation device must provide that the drum be held still in rotation in a number of predetermined angular positions, corresponding to the different positions of the derailleur required by the different ratios, i.e. on the different sprockets of the transmission. Therefore, the actuation device of a front derailleur has a relatively low number of predetermined angular positions (typically three), corresponding to the positions of the front derailleur on the different crowns of the chainset; a rear gearshift, on the other hand, has a relatively high number of predetermined angular positions (typically from seven to ten), corresponding to the positions of the rear derailleur on the different pinions.
So called "release-type" actuation systems are known in which the rotation of the cable-winding drum, where the cable is wound up, takes place as a result of the physical effort exerted by the cyclist on the appropriate upshift lever, whereas the rotation in the opposite direction is obtained by actuating the downshift lever, substantially freeing the cable-winding drum and allowing a return spring, which can be that of the derailleur as well as a return spring connected to the cable-winding drum inside the mechanism itself, to act in the direction to unwind the cable from the drum, clearly in a controlled manner.
A first release-type device is one in which the downshift lever is in the form of a button. The drum is kept in fixed position by a pawl that engages the teeth present on the outer surface of the cable-winding drum. The pressing of the button keeps the cable-winding drum locked in position while it allows the disengagement of the pawl from the teeth of the drum. The subsequent release towards the neutral rest position of the button allows the free rotation of the drum under the thrust of a coil spring mounted coaxial to the drum, while simultaneously the pawl engages the subsequent tooth of the cable-winding drum, locking it in the new position after the desired angular rotation.
A first drawback of such a device is that downward gearshifting is not sufficiently quick upon actuation by the cyclist, since it does not take place when the button is pressed but rather essentially in the step of releasing the button.
Another drawback is that to effect multiple downshifts, it is necessary to carry out multiple individual consecutive downward gearshifting operations.
A second release-type device is one in which the cable-winding drum is kept in position by a lever that engages at its first end the teeth present on the outer surface of the cable-winding drum. The thrusting actuation of the downshift lever allows the disengagement of the first end of the lever from the teeth of the cable-winding drum, the free rotation of the cable-winding drum for an amount of rotation equal to about half the desired rotation and the engagement of the second end of the lever on the teeth of the outer surface of the drum. The subsequent release of the downshift lever towards the neutral rest position determines the free rotation of the cable-winding drum for the second amount of rotation, which completes gearshifting, and the reengagement of the first end of the lever on the outer teeth of the drum.
In such a device downward gearshifting is also not sufficiently quick upon actuation by the cyclist, since it takes place substantially in two steps corresponding to the pushing and to the release of the lever and gearshifting is complete only after release of the downshift lever and its return to the neutral rest position.
As in the previous example, another drawback is that to effect multiple downshifts, it is necessary to carry out multiple individual consecutive downward gearshifting operations.
So called "active-type" actuation devices are also known in which the rotation of the cable-winding drum both in the sense of winding of the cable and in the sense of unwinding of the cable takes place by the physical force exerted by the cyclist on the appropriate upshift and downshift levers or by a servomechanism activated by the cyclist.
A known active-type device is one in which upshift and downshift levers act by actively thrusting on the cable-winding drum to place it in rotation for the entire angular extension defined between two adjacent gearshift positions. In particular, to carry out downward gearshifting, the lever must be rotated until the cable-winding drum reaches its desired final position, where it is locked in position by an indexing means.
A first drawback of such a device is that downward gearshifting is not sufficiently quick upon actuation by the cyclist, since it is only completed when the downshift lever has carried out a sufficient rotation to take the cable-winding drum into the final position.
Another drawback is that if the downshift lever is not pushed by a sufficiently large angle to take the cable-winding drum in rotation into the new gearshifting position, gearshifting is not completed and the derailleur remains in a disadvantageous intermediate position between two sprockets.
The problem at the basis of the invention is that of allowing quicker and more precise gearshifting operations to be carried out compared to known actuation devices.

Actuation method and device for a control cable for a bicycle gearshift


A power semiconductor component (2) has a chip stack, which contains a first chip (10), a second chip (6) and a third chip (8), where at least the second chip (6) and the third chip (8) are the same height. The power semiconductor component (2) also has a package in which the first chip (10), the second chip (6) and the third chip (8) are placed. The second chip (6) and the third chip (8) are mounted side by side on a lead (4), and the first chip (10) rests both on the second chip (6) and on the third chip (8).

In some applications of power semiconductors, such as in bridge circuits for motors, a plurality of chips are placed together as a chip stack in a package. This both saves space for the complete system and also reduces the length of interconnects between the chips.
German patent DE 196 35 582 shows such a bridge circuit containing high-side and low-side switches, for which a second chip is mounted on a first chip such that the load paths of the first and second chip are connected in series. The second chip, which lies on top and contains the low-side switch is here designed to be smaller than the first chip, which lies below and contains the high-side switch. This ratio should be inverted, however, in many bridge circuits, for example, because the low-side switch is subject to a far greater load. The current-carrying capability of the power semiconductor component is hence restricted by the size of the low-side switch.

Power semiconductor component having chip stack


System for ironing a cylindrical portion of a workpiece, and trimming one axial end of the cylindrical portion remote from a radial bottom portion. The system uses a stepped punch having a small-diameter portion and a large-diameter portion, and a die having a die hole whose inner surface includes a tapered portion and a land portion adjacent to the small-diameter end of the tapered portion. With the small-diameter portion of the punch in abutting contact with the radial bottom portion of the workpiece, the punch and die are moved relative to each other axially of the workpiece, from an initial position in which the radial bottom portion is ahead of the land portion of the die in the moving direction, to a final position in which at least the leading end of the large-diameter portion of the punch is located within the land portion. This relative movement causes removal of a waste material at the trailing end of the workpiece.

1. Field of the Invention
The present invention relates to a method and an apparatus for ironing and trimming a workpiece or blank which has a cylindrical portion and a radial bottom portion formed at one axial end of the cylindrical portion. More particularly, the invention is concerned with improved method and apparatus for ironing the cylindrical portion of such workpiece, and trimming the axial end of the cylindrical portion remote from the radial bottom portion.
2. Discussion of the Prior Art
An article or product in the form of a cup or container is obtained by subjecting a deep-drawn cup-like workpiece to a trimming operation, in which the axial open end of the cylindrical portion of the workpiece is trimmed. For trimming the axial open end of the cylindrical portion, the following three methods are known in the art.
The first trimming method is illustrated in FIGS. 24 and 25. Initially, a deep-drawn cup-like workpiece 500 having an outward flange at the open end is set in a die, and the outward flange is cut at a selected radial position by a punch, as shown in FIG. 24. The radial position at which the outward flange is cut determines the final depth or height of the article to be obtained as an end product 500 as shown in FIG. 25. Then, the workpiece 500 whose outward flange has been trimmed is subjected to a kind of drawing operation for straightening the trimmed outward flange while ironing the workpiece to reduce the wall thickness of the cylindrical portion, as shown in FIG. 25, whereby the end product 502 is produced.
The second trimming method includes the steps of: preparing a non-flanged workpiece 504 by either straightening the deep-drawn flanged cup-like workpiece 500 or punching off the entire portion of the outward flange of the cup-like workpiece 500; and trimming the axial open end of the thus prepared non-flanged workpiece 504, by using a shearing punch 506 which is moved in different radial directions of the workpiece 504, so that successive circumferential parts of the open end portion of the workpiece 504 are sequentially removed by shearing cuts effected by respective radial movements of the punch 506 relative to the workpiece 504, as indicated in FIG. 26.
In the third trimming method, the non-flanged workpiece 504 is first prepared as described above with respect to the second trimming method. Then, the open end portion of the workpiece 504 is continuously cut along the circumference of the cylindrical wall, by using a shearing roller 508. As shown in FIG. 27, the roller 508 which has a shearing blade on its outer circumference is rotatable about an axis parallel to the center line of the workpiece 504, and is moved along a circle coaxial with the workpiece so that the open end of the cylindrical wall of the workpiece 504 is continuously cut off by a continuous shearing cut effected by a circular movement of the roller 508.
However, all of the three trimming methods described above suffer from a considerable amount of shear droop at the trimmed open end of the end product, which is caused by cracking of the workpiece material due to penetration of the shearing punch or roller into the material.
The shear droop means a deviation of the actual shape or configuration of the open end face of the product from the nominal shape. For example, the open end face of the product may have curved or rounded edges, instead of the nominal right-angled or chamfered edges, or the actual radius of curvature of the edges may deviate from the nominal or specified radius, for instance, may be larger than the specified radius.
In particular, the first trimming method suffers from difficulty in assuring a high degree of accuracy of the height (depth) of the end product, even if the trimming of the outward flange is effected with high dimensional precision with the desired final height of the end product taken into account. Namely, the height of the end product is also determined by the wall thickness of the workpiece which is reduced by the ironing while the outward flange is straightened by the punch. However, the wall thickness of the workpiece usually has a certain amount of error, which inevitably results in an error in the height dimension of the end product.
The second and third trimming methods have another drawback. In these methods, the trimming is effected by the radial shearing cut or cuts at a selected axial position of the workpiece, whereby the height dimension of the end product can be controlled with high precision. However, the trimming is not effected at one time in these trimming methods, that is, effected by a continuous shearing cut or successive shearing cuts along the circumference of the cylindrical wall of the workpiece. Accordingly, the open end portion of the cylindrical wall of the workpiece is subjected to different shearing forces at different circumferential positions thereof, whereby the end product obtained tends to have some deformation in the cross sectional shape. The second trimming method which requires successive radial shearing cuts to trim the open end of the workpiece also suffers from a problem that the trimmed end face of the product obtained has low flatness or straightness, namely, more or less has raised and recessed portions because the successive radial shearing cuts are not performed under the same condition.
The third trimming method has a further problem that a device for moving the shearing roll 508 along the predetermined circular path is expensive.
Although the shear droop experienced in the prior art discussed above may be reduced by minimizing the n-value (work hardening exponent) of the workpiece, the reduction of the n-value results in another problem, namely, considerable deterioration of the formability of the workpiece, for example, reduction in the ease of bending or drawing of the workpiece. Therefore, the reduction in the n-value of the workpiece is not a practical solution to this problem.

Method and apparatus for ironing and trimming cylindrical portion of workpiece, using stepped punch and die having tapered die hole


A method of servicing a nuclear reactor during a reactor outage is provided. The reactor includes a primary containment vessel and a reactor pressure vessel positioned in the primary containment vessel. The method includes positioning a servicing platform above the reactor pressure vessel and performing predetermined servicing operations on the reactor. The servicing platform includes a frame having a plurality of interconnected beams, a support structure attached to the frame, and a floor attached to a top of the frame. The floor includes a reactor access opening sized to permit access to the reactor pressure vessel. The servicing platform also includes at least one auxiliary platform movably coupled to the frame and extending into the access opening. The at least one auxiliary platform is movable along a perimeter of the access opening of the floor.

This invention relates generally to nuclear reactor, and more particularly to a service platform for use in a nuclear reactor.
A reactor pressure vessel (RPV) of a boiling water reactor (BWR) typically has a generally cylindrical shape and is closed at both ends, e.g., by a bottom head and a removable top head. A top guide, sometimes referred to as a grid is spaced above a core plate within the RPV. A core shroud, or shroud, surrounds the core plate and is supported by a shroud support structure. The core shroud is a reactor coolant flow partition and structural support for the core components. Particularly, the shroud has a generally cylindrical shape and surrounds both the core plate and the top guide. A removable shroud head is coupled to a shroud head flange at the top of the shroud.
During refueling of a nuclear reactor, the majority of the servicing operations are performed from a bridge system that spans the refueling floor and the reactor and fuel storage pool cavities. These bridges typically have a straight four to eight foot wide walkway along their length and can be positioned above the reactor or refueling pool cavity. To clear the hand rails and other structures at the edge of the reactor cavity or service pools, the refuel bridge must be elevated about five feet above the floor surface.
In use, the bridge is moved to the desired position above the reactor and personnel work along the walkway of the bridge. When working over a round reactor vessel such as a boiling water reactor, access to a specific azimuth zone of the round reactor vessel is restricted for any given placement of the bridge because of shape of the bridge. With existing bridge access, the number of work activities, and number of personnel that can perform work at the same time is limited. The use of refuel bridges and auxiliary bridges is the most efficient known method of work access for achieving productivity for plant outage schedules.
The type of work required to service a nuclear plant would be enhanced by access to the reactor along the radial and tangential directions of the vessel or component. A normal bridge system can only accomplish radial or tangential alignment at the specific azimuth positions of 0, 90, 180, or 270 degrees. Radial and tangential alignment can never be accomplished simultaneously. Therefore, personnel and equipment may not have the optimal angle of access for visual observation or equipment manipulation.


A small footprint vertical lift and rotary positioning stage comprises a bottom wedge and a top wedge, a linear bearing between the bottom wedge and the top wedge, cam grooves and cam surfaces for constraining the motion of the top wedge in a vertical direction, a brushless linear motor for moving the bottom wedge back and forth along a horizontal path raising and lowering the top wedge, a circular table rotatably mounted on the top wedge and having a first cylindrical flange extending downward from a segment of the circumference of the circular table, a bracket mounted on the side of the top wedge, the bracket supporting an upwardly extending second cylindrical flange coaxial with the circular table and the first cylindrical flange, and a brushless curvilinear motor between the first and second cylindrical flanges.

This invention relates to the field of direct drive vertical lift and rotation stages for precision motion control. More specifically, it relates to small footprint linear and curvilinear motor driven positioning stages useful in the alignment of optic fibers.
Optic fibers are being used more and more for the transfer of information due to the large bandwidth and insensitivity to certain types of electromagnetic interference. Optic fibers are transparent glass fibers through which light waves encoded with information are passed. The fibers themselves are often less than 100 nm in diameter. Typically, they are enclosed in a protective coating. The fibers are not infinitely long and, therefore, it is necessary to align and bond fibers together. The alignment must be very precise, that is, the centers of the fibers must be aligned in order to minimize power loss across a bonded joint. Not only must the fibers be joined end to end, fibers must be connected to tiny components, such as transmitters, amplifiers and receivers. This process is referred to in the industry as pig-tailing.
In order to position fibers for fiber-to-fiber bonding or pig-tailing automatically, mechanical positioning stages with extremely high resolution and repeatability are required. Very often the bonding and pig-tailing take place in clean rooms. The expense of building and maintaining clean rooms is directly related to the volume of the room. Hence, miniaturization of the mechanical positioning stages for use in optic fiber alignment is extremely critical.
While linear motor driven vertical lift stages have been successfully implemented as disclosed in U.S. Pat. No. 5,731,641, the small footprint requirement for fiber alignment applications and the need to associate a rotation stage over the vertical lift stage has created the need for the advances disclosed herein.
It is an advantage, according to the present invention, to provide a small footprint vertical lift and rotation stage driven by linear and curvilinear motors that have high speed, high accuracy, high repeatability and high position stability making them a superior choice for fiber alignment applications.
Briefly, according to the present invention, there is provided a small footprint vertical lift and rotary positioning stage comprising a base plate, first and second side plates perpendicular to the base plate and fixed near opposite edges of the base plate, a bottom wedge, and a top wedge. The bottom (or drive) wedge has a bottom face parallel with the base plate and an upper face forming an angle alpha with the bottom face. The top (or carriage) wedge has a top face parallel with the base plate and a lower face forming an angle alpha with the top face.
A first linear bearing is positioned between the base plate and the bottom face of the first wedge. A second linear bearing is positioned between the upper face of the bottom wedge and the lower face of the top wedge. Cam grooves are provided in the first plate having cam surfaces for receiving cam follower rollers journaled to the top wedge. The cam surfaces and cam follower rollers constrain the motion of the top wedge in a direction perpendicular to the base. A brushless linear motor comprising an armature winding is fixed to the second side plate. A rare earth magnet track is fixed to the bottom wedge for moving the bottom wedge back and forth along a path constrained by the first linear bearing. As the bottom wedge moves back and forth due to the geometry of the wedges and the cam surfaces and cam rollers, the top wedge is raised and lowered. A linear encoder comprises an encoder reader fixed relative to the base plate and an encoder scale fixed to the bottom wedge extending parallel to the base plate in the direction of travel of the bottom wedge. A rotating stage has a circular plate fixed to the top surface of the top wedge and a circular table rotatably mounted to the circular plate. The table has a first cylindrical flange extending downward from a segment of the circumference of the table outside of one of the side plates. A bracket is mounted on the side of the top wedge extending outwardly of one of the side plates. The bracket supports an upwardly extending second cylindrical flange coaxial with the circular table and the first circular flange. A brushless curvilinear motor comprises an armature winding fixed in the second cylindrical flange and a rare earth magnet track fixed in the first cylindrical flange. An encoder comprising an encoder reader is mounted on the top of the top wedge adjacent the circumference of the table and an encoder scale is mounted on the circumferential edge of the table.

Small footprint vertical lift and rotation stage


A sub-combat unit to be separated from a flying body, comprises a warhead, a target detector and two diametrically disposed carrier surfaces designed and arranged to impart to the sub-combat unit a rotation for scanning of the target area in a helical pattern during the fall of the sub-combat unit down towards the target area. The two carrier surfaces are pivotable between a closed position and an opened position in which the two carrier surfaces form a retarding area for controlling the fall velocity of the sub-combat unit and a flow influencing means is provided at at least one of the two carrier surfaces for creating a turbulent area immediately above the carrier surface for completely relieving the carrier surfaces even for large differences in the direction of the impinging wind.

The characterizing features of the sub-combat unit described in the above-mentioned patent are that the target detector is pivotally disposed on a journal shaft which is parallel to the line of symmetry of the warhead so as to permit outward pivoting of the target detector from a closed position where the optical axis of the target detector coincides with the line of symmetry of the warhead, to an opened position where the optical axis of the target detector is parallel to the line of symmetry of the warhead to permit a free view of the target detector beside the warhead. In addition, a carrier surface is pivotally disposed on a journal shaft which is also parallel to the line of symmetry of the warhead so as to permit outward pivoting of the carrier surface from a closed position to an opened position beside the warhead.
By a suitable aerodynamic design of the sub-combat unit and the retarding area of the detector and carrier surface, there will be obtained a suitable fall velocity of the sub-combat unit and further an impelling moment about the spinning axis which gives the sub-combat unit its rotation. This is achieved without the aid of a parachute, which is an advantage since the parachute is bulky and requires space. Therefore, more space in a carrier shell can instead be made available for the warhead proper.
Even thought the above-described sub-combat unit has proved to possess superior properties with respect to fall velocity and scanning rotation, it has been desired in the art to increase the retarding area even further. This may, for instance, be the case when it is desired to employ heavier warheads. The retarding area of the target detector and carrier surface is restricted to the cross-sectional area of the cylindrical sub-combat unit body, which may entail that the fall velocity will become too high with the existing size of the retarding area if, at the same time, the weight of the warhead is increased.
Swedish patent application number 8903474-8 corresponding to U.S. Pat. No. 5,088,414 describes a sub-combat unit in which the retarding area has been made considerably larger. The characterizing feature of the sub-combat unit is that two diametrically located carrier surfaces are pivotally disposed each on its own shaft located in a plane which is at right angles to the axis of symmetry of the warhead, and pivotable from a closed position where the carrier surfaces follow the casing surface of the sub-combat unit, to a 90.degree. opened position where both of the carrier surfaces form a retarding area for the fall velocity of the sub-combat unit.
In this case, the carrier surfaces are made of an elastically flexible material, so that, when they pivot out from their closed position, they are at the same time bent to a substantially straight or gently curved surface.
The advantage inherent in the above-described design, in addition to the larger retarding area, is that both of the carrier surfaces may be made comparatively thin, which is favorable from the point of view of weight and payload. For example, the carrier surfaces may be made of titanium and bent so that, in their opened position, they have a certain radius. The bending may be varied and the carrier surfaces may be of different lengths, in which event further parameters for varying the aeronautical properties of the unit will be obtained.
Even if the two carrier surfaces are designed with an accurately specified geometry in accordance with known ballistical laws, it may occur at certain angles of wind impingement in relation to the carrier surface that the momentaneous is disturbed, so that a disturbance (unwanted pendulum motion, instability) occurs in the sub-combat unit to the detriment of the scanning movement.