An optical waveguide laser arrangement includes a solid optical waveguide having a waveguiding portion that extends along an axis between two spaced regions of the optical waveguide and is of a material capable of emitting stimulated light upon excitation by pumping light that is launched into the optical waveguide for axial propagation through the axially spaced regions of the optical waveguide. Two reflectors are provided, each being disposed at one of the axially spaced regions of the optical waveguide to delimit a laser resonator. At least one of the reflectors is constituted by a Bragg grating consisting of a multitude of axially consecutive periodic perturbations in the refractive index of the respective one of the axially spaced regions that cumulatively reflect the stimulated light at a reflectivity that decreases for adjacent longitudinal modes of the stimulated light with increasing deviation from a central wavelength. The axial length of the laser resonator, the reflectivity of the Bragg grating and the gain of the excitable material are so coordinated with one another as to sustain lasing in only a single longitudinal mode.

There are already known various constructions of pumped optical waveguide lasers, among them such utilizing fully or partially reflective coatings on the respective end faces delimiting the laser resonance cavities in solid material optical waveguides, and such using external reflectors to delimit the laser cavities. Even though these solutions have achieved quite a degree of success and/or acceptance in the laser manufacturing and utilization fields, they still suffer of certain drawbacks, one of which is that, because reflecting elements of the above type are reflective over a relatively wide frequency bandwidth, lasing often occurs in more than one mode. This is true even if the optical waveguide, such as an optical fiber, is of the so-called single mode type in which all transverse modes but one are below the cutoff. As a matter of fact, experience has shown that even such a single-mode optical fiber laser typically lases in a great number of longitudinal modes. This, of course, significantly degrades the properties of the laser radiation issued by the optical fiber laser due to mode beating and other optical effects, thus considerably reducing the utility of the issued laser beam. This multiple longitudinal mode operation diminishes if not defeats utility of such lasers for many applications in the telecommunications, sensor and spectroscopic evaluation fields.
Narrow-linewidth single-frequency semiconductor laser diodes are currently the source of choice in low to moderate power coherent systems. In laser diodes, single-frequency narrow-linewidth operation is typically achieved through a distributed feedback or a distributed Bragg reflector structure. Moreover, miniature, diode-pumped, single-frequency, narrow-linewidth solid state lasers are currently being manufactured in a variety of configurations. Both of these laser types, however, suffer of certain drawbacks, an important one of which is that, when they are to be used in optical fiber systems, they require integration into such systems that is alignment insensitive, and hence expensive. Therefore, for these applications, it would be preferable to use optical fiber lasers. However, experience has shown that it is not at all easy to achieve the desired single longitudinal mode operation in linear optical fiber lasers, especially when they are to have substantial lengths. This is so because, even when the reflectors axially delimiting the laser cavity are of the relatively narrow passband type, still the number of longitudinal modes falling within this passband and thus in competition for lasing is substantial when the length of the laser cavity is in excess of a few millimeters or centimeters. Because of this, it was heretofore very difficult if not impossible to provide a linear solid material optical waveguide, especially an optical fiber, laser that would lase exclusively in a single longitudinal mode.
Accordingly, it is a general object of the present invention to avoid the disadvantages of the prior art.
More particularly, it is an object of the present invention to provide pumped optical fiber laser arrangements which do not possess the disadvantages of the known arrangements of this kind.
Still another object of the present invention is so to develop the arrangements of the type here under consideration as to achieve lasing in only a single longitudinal mode.
It is yet another object of the present invention to devise arrangements of the above type which are able to achieve such single mode operation at various cavity lengths and gains of the optically excitable material of the optical waveguide.
A concomitant object of the present invention is to design the optical waveguide lasers of the above type in such a manner as to be relatively simple in construction, inexpensive to manufacture, easy to use and integrate into optical fiber systems, and yet reliable in operation.

Single longitudinal mode pumped optical waveguide laser arrangement


A stepless expandable rod is composed of an outer tube provided therein with an insertion slot and a tube compartment, an insertion strip located in the insertion slot and provided with a plurality of retaining holes, an inner tube expandable received in the tube compartment of said outer tube, a connection rod received in the inner tube and capable of an axial displacement, and a retaining member located at the bottom end of the inner tube and provided with a retaining projection capable of being actuated by the connection rod to extract to engage one of the retaining holes of the insertion strip so as to retain the bottom end of the inner tube at a position in the outer tube at the time when the inner tube is extracted from the top end of the outer tube.

As shown in FIG. 1, a stepless expandable rod 10 of the prior art is composed of an outer tube frame 11, an outer tube wall piece 13, an inner tube 16, a connection rod 17, and a retaining member 18. The outer tube frame 11 has an inverted U-shaped cross section and an open face which is provided respectively in two sides thereof with a curved insertion edge 12. The outer tube wall piece 13 is provided along the direction of a longitudinal axis thereof with a plurality of round holes 14 and is further provided respectively in two side edges thereof with an insertion slot 15, which is engaged with the insertion edge 12 of the outer tube frame 11. The inner tube 16 is disposed in an outer tube formed of the outer tube frame 11 and the outer tube wall piece 13. The connection rod 17 is received in the inner tube 16. The retaining member 18 is disposed at the bottom end of the inner tube 16 and is connected with the bottom end of the connection rod 17. When the connection rod 17 is exerted on by an external force, the retaining projection 19 is actuated to move outward to engage the round holes 14 so as to retain the inner tube 16 in such a manner that the inner tube 16 is expanded for a predetermined length.
Such a prior art expandable rod 10 as described above is defective in design in that the outer tube frame 11 and the outer tube wall piece 13 must be made separately by extrusion, and that the outer tube wall piece 13 is then provided with the round holes 14 by punching, and further that the outer tube frame 11 and the outer tube wall piece 13 are fastened together by punching. It is therefore readily apparent that the prior art expandable rod 10 is not cost-effective.

103, Ta-Ming 1 Rd., Tung Pao Tsun, Tan Tzu Hsiang


A heat dissipating device includes a base, a heat pipe disposed on the base, and a plurality of first and second heat dissipating fins. Each first heat dissipating fin includes a fin body having a first through hole for extension of the heat pipe therethrough. The first and second heat dissipating fins are mounted on the heat pipe in a stack and in a spaced-apart alternating arrangement. Each second heat dissipating fin includes a fin body having a second through hole for extension of the heat pipe therethrough, two adjacent lateral edges, and a cut edge interconnecting the lateral edges such that each second heat dissipating fin has a smaller area than each first heat dissipating fin. Thus, the flow field resistance of the heat dissipating device can be reduced to increase the amount of airflow through the heat dissipating device for enhancing the heat dissipating efficiency.

1. Field of the Invention
The invention relates to a heat dissipating device and heat dissipating fins thereof, more particularly to a heat dissipating device having heat dissipating fins of different shapes which are stacked in a spaced-apart and alternating arrangement.
2. Description of the Related Art
Since an electronic component (such as a central processing unit or operating chip) in a computer system operates at an increased speed, the heat generated thereby also increases. In order to effectively enhance the heat dissipating efficiency of a heat dissipating device, some methods of improvement are to increase the number and area of heat dissipating fins of the heat dissipating device. However, increasing the number and area of the heat dissipating fins will not only increase the overall weight of the heat dissipating device, the flow field resistance will also rise, so that the amount of airflow supplied by a heat dissipating fan will drop when the air passes through the heat dissipating device, which will undesirably lower the heat dissipating efficiency of the heat dissipating device. Accordingly, the rotational speed of the heat dissipating fan has to be increased to overcome the problem of low airflow. However, raising the rotational speed of the fan will result in increased noise.
As shown in FIGS. 1 and 2, a conventional heat dissipating device 1 has a plurality of heat dissipating fins 11, which are generally stacked in a spaced-apart manner and which are secured on heat pipes 12 mounted on a base 10. Moreover, the heat dissipating fins 11 are of the same shape (such as a rectangular shape). During transfer of heat from the heat pipes 12 to the heat dissipating fins 11, since heat cannot be readily conducted to fin portions 111 (such as upper left and lower right corner portions shown in FIG. 2) of each fin 11 that are distal from the heat pipes 12, and since the fin portions 111 have temperatures lower than those of fin portions 112 that are proximate to the heat pipes 12, the heat conducting effect of the fin portions 111 is unsatisfactory, and the heat dissipating efficiency is poor. Furthermore, the fin portions 111 distal from the heat pipes 12 are also a source of flow field resistance, so that the amount of airflow supplied by a heat dissipating fan (not shown) will drop when the air passes through the heat dissipating fins 11 of the heat dissipating device 1 in a direction indicated by the arrows in FIG. 2, thereby lowering the heat dissipating efficiency of the heat dissipating device 1.
FIG. 3 is a comparison table listing various simulation values obtained by numerical simulation computation with respect to the amounts of the airflow which is supplied by the heat dissipating fan and which passes through the heat dissipating device 1. It is apparent from FIG. 3 that the thermal resistance values and the flow resistance values (i.e., flow field resistance) will decrease with an increase in the amounts of airflow passing through the heat dissipating device 1. The heat dissipating efficiency parameter η of the heat dissipating device 1 is defined as 1/(thermal resistance value×flow resistance value). If the thermal resistance value and the flow resistance value are small, the heat dissipating efficiency parameter η will be large, indicating that the heat dissipating efficiency of the heat dissipating device 1 is high. It can be understood from FIG. 3 that, under different environmental conditions, the heat dissipating efficiency parameter η of the heat dissipating device 1 will vary with the thermal resistance value and the flow resistance value.

Heat dissipating device and heat dissipating fin


The invention relates generally to compositions that contain multiple antibodies, e.g., multiple neutralizing antibodies, that immunospecifically bind to one or more toll-like receptors, e.g., two or more toll-like receptors, and methods of using these compositions in the treatment of inflammatory disorders.

Toll receptors, which were first discovered in Drosophila, are type I transmembrane protein having leucine-rich repeats (LRRs) in the extracellular portion of the protein, and one or two cysteine-rich domains. The mammalian homologs of the Drosophila Toll receptors are known as "Toll-like receptors" (TLRs). TLRs have been have been shown to play a role in innate immunity by recognizing microbial particles and activating immune cells against the source of these microbial particles.
Currently, ten types of Toll-like receptors have been identified, TLRs 1-10. These TLRs are characterized by the homology of their intracellular domains to that of the IL-1 receptor, and by the presence of extracellular leucine-rich repeats.
TLRs are activated by different types of microbial particles known as pathogen-associated molecular patterns (PAMPs). For example, TLR4 is primarily activated by lipopolysaccharide (LPS), while TLR2 is activated by lipoteichoic acid (LTA), lipoarabinomannan (LAM), lipoprotein (BLP), and peptideglycans (PGN). It is therefore possible that any given microbe can stimulate several different TLRs in parallel at any given time during an infection.
In addition, certain TLRs have been shown to require the presence of accessory proteins in order to function. For example, TLR4 forms a complex with myeloid differentiation protein-2 (MD-2) on the cell surface. The MD-2 protein has been found to interact directly with TLR4, and MD-2 has the ability to enable post-translational modifications of TLR4, as well as facilitate its transport to the cell surface. CD14 is another protein that has been linked to TLR4 function, and in addition, CD14 has also been implicated in TLR2 recognition of microbes.

Combining therapies targeting multiple toll-like receptors


A shock absorber including a pressure tube, a piston assembly slidably disposed within the pressure tube, and a fluid transfer tube that extends about the pressure tube is provided. The piston assembly divides an inner volume of the pressure tube into first and second working chambers. An intermediate chamber between the pressure tube and the fluid transfer tube is arranged in fluid communication with the first working chamber. A valve assembly is disposed in fluid communication with the intermediate chamber and the second working chamber. The valve assembly controls fluid flow between the intermediate chamber and the second working chamber. At least part of the intermediate chamber is formed by a fluid transfer channel that extends longitudinally within the fluid transfer tube to provide a fluid flow path extending between the first working chamber and the valve assembly.

This section provides background information related to the present disclosure and is not necessarily prior art.
Shock absorbers are used in connection with automobile suspension systems and other vehicle suspension systems to absorb unwanted vibrations, which occur during locomotion. To absorb unwanted vibration, shock absorbers are generally connected between the body and the suspension of the automobile. A piston is located within the shock absorber and is connected to the vehicle body through a piston rod. The piston creates two working chambers inside the shock absorber that are filled with a damping fluid. The piston has passageways and valve disk stacks that limit the flow of damping fluid between the two working chambers of the shock absorber when the shock absorber undergoes compression and extension. As a result, the shock absorber is able to produce a damping force that counteracts suspension movements and vibration which could otherwise be transmitted from the suspension of the automobile to the body.
In a semi-active shock absorber, the amount of damping force generated during compression and extension movements of the shock absorber is controlled by using an electromechanical valve that selectively modifies a secondary passageway between the two working chambers of the shock absorber. During use, high frequency piston accelerations can cause pressure resonances. Pressure waves created in the secondary passageway by high frequency piston accelerations can cause clatter noises that are objectionable to drivers and occupants of the vehicle. As a result, there remains a need for shock absorbers that produce less clatter noise during high frequency suspension movements.

Tenneco Automotive Operating Company Inc.


A device for braking traveling threads, wires or the like, in particular for use for the entry of the filling thread in looms (8), having a plurality of brake parts (B, B') which are under spring action with respect to each other and between which the thread (5) travels; in order to obtain optimal use, a cyclic change in the brake force is derived from the rotation by motor drive of one of the brake parts (B, B', C, C').

The present invention relates to a device for the differential braking of traveling threads, wires or the like, particularly for use in connection with the filling thread insertion on looms, having two or more braking parts under spring action with respect to each other between which the thread passes.
Devices are known on the market in which the brake parts, which are under spring action with respect to each other, have two or more plates consisting of spring material between which the thread travels. The spring force with which the two plates come against each other must, on the one hand, be sufficiently great to produce sufficient braking of the thread. On the other hand, they must not impair the insertion of the filling. It must also be taken into account that knots must be able to pass through the plates which are under spring action with respect to each other without the thread being broken. In present-day looms, which operate with high weft speed with cyclic insertion of the filling taking place at short time intervals, only a few milliseconds are present due to the start and stop principle for the braking and release of the thread, with the problem that the plates, which are under spring action with respect to each other, do not react sufficiently rapidly and lead to disturbances in the transport of the thread.

Device for the differential braking of traveling threads, wires or the like

Sobrevin Societe de brevets industriels-Etablissement


Valve drive for an internal combustion engine having a valve which is axially displaceable between an open position and a closed position and is prestressed by a locking spring in the direction of its closed position, in which a control shaft driven by an electric motor to pivot about a longitudinal axis, has a cam, provided for operating the valve a pressure element that can be pivoted about a pivot axis, and a spring element which prestresses the pressure element and exerts a torque on the control shaft via the pressure element. The mass moment of inertia of the pressure element relative to its pivot axis is greater than the mass moment of inertia of the control shaft and the cam relative to the longitudinal axis of the control shaft. The valve drive so configured provides greater electrical operating efficiency and permits valve actuation to be performed at lower electric motor rotation speeds.

The present invention relates to a valve drive of an internal combustion engine that operates according to the "rotating actuator principle."
Such a valve drive is known from German Patent DE 101 40 461 A1. With traditional internal combustion engines, the camshaft is driven mechanically by the crankshaft via a control chain or a control belt. To increase the engine power and to reduce fuel consumption, a considerable advantage would be achieved by individually triggering the valves of the individual cylinders or at least the intake valves and outlet valves of the individual cylinders. This is possible by means of an electromagnetic valve drive. In an electromagnetic valve drive, an "actuator unit" is assigned to each valve and/or each "valve group" of a cylinder. Different basic types of actuator units are currently being researched. In one basic type, an opening magnet and a closing magnet are assigned to one valve or one valve group. The valves can be displaced axially, i.e., opened and/or closed, by applying electric current to the magnets. However, such valve drives are difficult to control from the standpoint of control technology. With the other basic type, a control shaft with a cam is provided, whereby the control shaft can be pivoted back and forth by an electric motor. This is also referred to as the so-called "rotating actuator principle." In German Patent DE 101 40 461 A1 cited above, the cam acts on a rocker arm. Then the opening force generated by the cam is applied by the rocker arm to the valve. At the end of the control shaft, a lever-like element is also provided in the form of a "hand crank." Furthermore, a spring clip is also provided, having a protruding spring arm that presses against the lever-like element. The spring arm of the pivoting lever exerts a torque on the control shaft and/or on the cam. The torque depends on the position of the lever-like element, i.e., the pivot position of the control shaft.
As mentioned above, the control shaft together with the cam in the case of a valve drive like that described in German Patent DE 101 40 461 A1 pivots cyclically back and forth. A reversal of direction of rotation is thus occurring constantly. The electric motor here must accelerate the control shaft and the cam and the lever-like element attached thereto out of the resting state to a relatively high rotational speed. Although the electric motor is supported by the spring clip in opening the valve, it must work against the force of the locking spring, which requires a relatively high electric power. One essential problem here is that the electric motor "starts" from the resting state each time in acceleration of the control shaft, the cam and the lever-like element of the electric motor connected to the control shaft. It takes a certain amount of time with each cycle until the electric motor reaches a rotational speed at which the electric motor operates with a favorable electric efficiency. At low rotational speeds in particular, the efficiency of the electric motor is relatively unfavorable, resulting in a high power consumption.
The object of the present invention is to create an electric valve drive that operates according to the "rotating actuator principle" which is improved with regard to the electric power consumption.
The starting point for the present invention is a valve drive for an internal combustion engine with a valve that is arranged so that it is axially displaceable between an open position and a closed position. Due to a locking spring, the valve is prestressed in the direction of its closed position. Furthermore, a control shaft is provided with a cam which operates the valve. The control shaft is coupled to an electric motor that pivots the control shaft back and forth about a longitudinal axis. Furthermore, a pivotably mounted "pressure element" prestressed by a spring is provided. The pressure element prestressed by the spring exerts a torque on the control shaft. The torque exerted instantaneously on the control shaft depends on the pivot position of the cam. In the back and forth movement of the control shaft, the pressure element is also pivoted back and forth about its pivot axis.
The present invention is based on the finding that the power required for operation of the valve and/or the electric power required for valve operation depends to a significant extent on the ratio of the moments of mass inertia of the "pivotable valve drive components." The greater the mass moment of inertia of the control shaft and of the cam, the more power must be supplied by the electric motor for acceleration of the control shaft and the cam. In opening the valve, the acceleration of the control shaft and the cam is supported by the pressure element prestressed by the spring. When the valve is closed, then the spring is maximally stressed. It can be demonstrated in an experiment that the mass moment of inertia of the pressure element in particular and/or the mass moment of inertia formed by the spring and the pressure element have a decisive effect on the electric power required for operation of the electric motor. A good "electric efficiency" is achieved when the mass moment of inertia of the pressure element in relation to its pivot axis is greater than the mass moment of inertia formed by the control shaft and the cam in relation to the longitudinal axis of the control shaft.
Thus, the pressure element is designed to be "more solid" than would actually be necessary for transmission of the prestressing force generated by the spring.
In designing the electric motor, it is advantageous not to set the maximum rotational speed of the electric motor too high. In fact, the maximum rotational speed of the electric motor could be reduced with an increase in the mass moment of inertia of the control shaft and the cam. As already mentioned, however, the dynamics of the valve drive decreases with an increase in the mass moment of inertia of the control shaft and the cam because the mass moment of inertia of the control shaft and the cam must first be accelerated electrically by the electric motor and then must additionally be accelerated mechanically by the springs because the mass moment of inertia of the control shaft and of the cam must also be accelerated even in the "stable end positions," i.e., from the resting positions of the control shaft. Likewise, this mass moment of inertia must be accelerated electrically in the case of a "mini stroke operation."
However, an increase in the mass moment of inertia of the pressure element has the advantage that the pressure element need not be accelerated out of the resting position by the electric motor alone when opening the valve but instead is also moved by the spring element.
During an initial phase of the opening procedure of the valve, first the control shaft and the cams are accelerated by the electric motor to a certain speed without the valve already being opened. During this initial phase, the pressure element is also accelerated and thus stores a certain amount of rotational energy. The actual opening movement of the valve, when the valve is opened against the locking spring force of the valve, begins during the second phase. The energy required for opening the valve is applied primarily by the spring element and the "kinetic energy" stored in the pressure element.
By increasing the mass moment of inertia of the pressure element, more kinetic energy is stored in the pressure element accordingly. This part of the energy need no longer be stored in the camshaft. In other words, according to this invention, a portion of the energy required for opening the valve is "shifted" from the camshaft to the pressure element. This permits a reduction in the maximum control shaft rotational speed required for valve opening. The increase in the mass moment of inertia of the pressure element acts like an increase in the mass moment of inertia of the control shaft in this operating state. Since the "rotational actuator" must be accelerated electrically out of the two end positions, a low mass moment of inertia is favorable with regard to actuator dynamics as well as with regard to electric power consumption, in particular at the start of the acceleration movement.
Another advantage achieved with the present invention lies in the fact that the average rotational speed of the electric motor with this invention is shifted into a higher rotational speed range. Therefore, the ohmic losses are reduced, especially in acceleration of the electric motor from low rotational speeds, thus resulting in an improvement in overall electric efficiency. The total power consumption declines and the amount of lost heat to be dissipated is thus also reduced.
According to one embodiment of the present invention, the spring element is a torsion spring. This may be a torsion spring rod whose first end is fixedly clamped, e.g., being attached to an actuator housing with the pressure element attached to its other end and protruding essentially perpendicularly away from the torsion spring rod. The torsion spring rod may be arranged in parallel with respect to the control cam which is thus a very space-saving arrangement.
The "elevated" mass moment of inertia of the pressure element is preferably achieved by a mass concentration at the end distal from the torsion spring. This yields a relatively high mass moment of inertia with a comparatively low total mass of the pressure element. The pressure element may be manufactured from a plate-shaped component, for example, and may have a closed contour with a recess in the central area. The pressure element may be a punched part. The recess may be punched out of the central area in particular.
As already mentioned, according to the present invention, the mass moment of inertia of the pressure element in relation to its pivot axis is greater than the mass moment of inertia formed by the control shaft and the cam and in relation to the longitudinal axis of the control shaft. An especially favorable mass moment of inertia ratio is obtained when the mass moment of inertia of the pressure element in relation to its pivot axis is greater by a factor in the range between 1.7 and 2.3 than the mass moment of inertia formed by the control shaft and the cam and in relation to the longitudinal axis of the control shaft.
Other objects will become apparent for one skilled in the art on seeing the description and claims.

Electric valve drive with a rotating actuator

Bayerische Motoren Werke Aktiengesellschaft


A Wireless Local Area Network (WLAN) infrastructure includes a wired backbone network, an air controller, and a plurality of wireless access points (WAPs). Each WAP includes a processor, a wired backbone interface, a first radio, a directional antenna, a second radio, and an antenna. The first radio and directional antenna service wireless terminals. The second radio and the antenna collect non-participatory WAP data. The first radio and directional antenna optionally collect participatory WAP data. Based upon the non-participatory WAP data (and optionally the participatory WAP data), the processor creates WAP operational reports and provides the WAPs operational reports to the air controller. The air controller creates directions based thereon and directs one or more of the WAPs to alter the gain pattern(s) of the directional antenna(s), alter the transmit power(s) of the first radio(s), and/or to alter the channel usage of the first radio(s). In another embodiment, the first radio collects non-participatory WAP data when not servicing communications with wireless units.

Communication technologies that link electronic devices in a networked fashion are well known. Examples of communication networks include wired packet data networks, wireless packet data networks, wired telephone networks, wireless telephone networks, and satellite communication networks, among other networks. These communication networks typically include a network infrastructure that services a plurality of client devices. The Public Switched Telephone Network (PSTN) is probably the best-known communication network that has been in existence for many years. The Internet is another well-known example of a communication network that has also been in existence for a number of years. These communication networks enable client devices to communicate with each other on a global basis. Wired Local Area Networks (LANs), e.g., Ethernets, are also quite common and support communications between networked computers and other devices within a serviced area. LANs also often link serviced devices to Wide Area Networks and the Internet. Each of these networks is generally considered a "wired" network, even though some of these networks, e.g., the PSTN, may include some transmission paths that are serviced by wireless links.
Wireless networks have been in existence for a relatively shorter period. Cellular telephone networks, wireless LANs (WLANs), and satellite communication networks, among others, are examples of wireless networks. Relatively common forms of WLANs are IEEE 802.11(a) networks, IEEE 802.11(b) networks, and IEEE 802.11(g) networks, referred to jointly as "IEEE 802.11 networks." In a typical IEEE 802.11 network, a wired backbone network couples to a plurality of Wireless Access Points (WAPs), each of which supports wireless communications with computers and other wireless terminals that include compatible wireless interfaces within a serviced area. The wired backbone network couples the WAPs of the IEEE 802.11 network to other networks, both wired and wireless, and allows serviced wireless terminals to communicate with devices external to the IEEE 802.11 network.
WLANs provide significant advantages when servicing portable devices such as portable computers, portable data terminals, and other devices that are not typically stationary and able to access a wired LAN connection. However, WLANs provide relatively low data rate service as compared to wired LANs, e.g., IEEE 802.3 networks. Currently deployed wired networks provide up to one Gigabit/second bandwidth and relatively soon, wired networks will provide up to 10 Gigabit/second bandwidths. However, because of their advantages in servicing portable devices, WLANs are often deployed so that they support wireless communications in a service area that overlays with the service area of a wired network. In such installations, devices that are primarily stationary, e.g., desktop computers, couple to the wired LAN while devices that are primarily mobile, e.g., laptop computers, couple to the WLAN. The laptop computer, however, may also have a wired LAN connection that it uses when docked to obtain relatively higher bandwidth service.
When a decision is initially made to install a WLAN in a premises, the WLAN must first be engineered. In such engineering, the lay out of the premises, e.g., warehouse, office space, campus environment, etc. is first considered. In most installations, wireless coverage is desired across all areas of the premises. The deployment of the WAPs within the premises is the most critical step in the WLAN engineering. Because the conductance of Radio Frequency (RF) transmissions through building walls and other obstacles in the premises is dependent upon respective structure, the structural aspects of the premises must be carefully considered when determining WAP placement. However, most WAP placement decisions are subjectively made, based upon the care and experience level of the installer.
During the initial WLAN installation, the WAP placement is fixed. Thus, the WAP placement cannot address changes in the topology and structure of the premises. Such changes in the topology and structure may include the addition of walls, the additions of partitions, the addition of wiring that will affect propagation of RF transmissions, and other characteristics. Problems that typically result due to poor WAP placement include poor channel utilization, interference between WAPs, WAP capacity shortages, and other shortcomings. These operational problems, however, will typically only be seen as poor WLAN performance. The WLAN network installer/administrator, however, has no way of determining whether these problems are caused by equipment deficiencies, the nature of the premises, WAP placement, or lack of capacity in the WAPs.
Thus, there is a need in the art for improvements in the management of WAPs servicing a WLAN within a premises.

Wireless access point service coverage area management


In some examples a printing system includes purging manifolds. The printing system includes a fluid ejection device to dispense a fluid and a first reservoir to house a fluid. The system further includes a purging manifold to fluidically couple to the fluid ejection device, and the purging manifold to fluidically couple to the first reservoir. The purging manifold includes a second reservoir. The purging manifold further includes a supply port; a fluid inlet port; and a purging outlet port. The purging outlet port is disposed above the supply port to convey fluid to the first reservoir. The printing system also includes a fluid interface connector to fluidically connect to the supply port and fluidically connect to the fluid ejection device.

A printing system can include a fluid ejection device that has nozzles to dispense printing fluid to a target. In a two-dimensional (2D) printing system, the target is a medium, such as a paper or another type of substrate onto which fluid is dispensed. Examples of 2D printing systems include inkjet printing systems that dispense droplets of inks. In a three-dimensional (3D) printing system, the target can be a layer or multiple layers of build material deposited to form a 3D object.
Throughout the drawings, identical reference numbers designate similar, but not necessarily identical, elements. The figures are not necessarily to scale, and the size of some parts may be exaggerated to more clearly illustrate the example shown. Moreover, the drawings provide examples and/or implementations consistent with the description; however, the description is not limited to the examples and/or implementations provided in the drawings.

HEWLETT-PACKARD DEVELOPMENT COMPANY, L.P.


A pump and filter system for filtering effluent in a septic system including a filter housing with sides, a top and a bottom, a filtering system secured within the filter housing, a vertical tubular element secured to the outside of the filter housing in communication with unfiltered effluent within the septic system and with an opening in the bottom or side of the filter housing, and a pump for pumping filtered effluent through the filtering system. Preferably a check valve is secured within the bottom of the filter housing.

This invention relates to devices used for the treatment of waste water. More specifically, this invention relates to a pump and filter system used for the filtering of liquid effluent contained in a septic tank.
Waste water discharged from commercial or residential property contains both liquid and solid wastes which are typically collected in a waste water collector, such as a septic tank. In such septic tanks, the liquid and solids are generally distributed into three layers: an upper horizontal scum layer, a lower horizontal sludge layer, and a relatively clear, horizontal effluent layer located between the two other layers. During operation of these septic tanks, liquids from this horizontal effluent layer are intermittently discharged from the septic tanks. During such discharge the solids contained within the septic tanks are preferably retained in the septic tanks to be decomposed during the normal operation of the system. Intermittently, the septic tanks are cleaned to remove any excess solids contained therein.
During normal operations, some solids become mixed into the relatively clear horizontal effluent layer. These solids often migrate into this layer on gas bubbles produced during decomposition of solid material contained in the lower sludge layer. These solids will be discharged with the effluent if not filtered out of the effluent. Excess solids discharged with the effluent may gradually degrade the effectiveness of the entire septic system.
To reduce the likelihood of discharge of solids from the septic tank, a number of different types of filtering devices for the liquid effluent have been developed. For example, cylindrical mesh screen filtering systems which surround a gravity flow outlet system and discharge pump are disclosed in U.S. Pat. Nos. 5,207,896 and 4,439,323.
The effluent flows into the filtering system generally through openings in the side walls of the filter system which are designed to match up with the relatively clear, horizontal effluent layer. For example, the devices of U.S. Pat. Nos. 5,492,635 and 4,439,323 utilize a plurality of openings in the walls of the filtering system with these openings designed to be placed within the relatively clear, horizontal effluent layer.
Other devices placed within a septic tank which use a filtering system different from a mesh screen are disclosed, for example, in U.S. Pat. Nos. 5,482,621 and 5,382,357. These patents disclose filtration of the effluent using a specific flow pattern for the effluent through an open bottom of a filter element, out the sides of the filter element through an annular space adjacent to the filter element, and finally to a discharge opening of the device for discharging filtered effluent from the septic tank.
Other systems for filtering solids from the effluent of a septic system utilizing a stacked disk dam system as the filtering system are disclosed in U.S. Pat. Nos. 5,582,716, 5,207,896, 4,710,295, 3,332,552 and 2,900,084. See also U.S. Pat. No. 5,264,120 which utilizes both a mesh screen and a disk dam system to filter the effluent. See also U.S. Pat. No. 5,690,824 which utilizes a series of stacked mesh filters.
U.S. Pat. No. 5,591,331 discloses a different filtering system comprising a plurality of vertically extending removable side walls, each of which contains a filtering screen for filtering the effluent.
A filter system containing a removable filter with diagonal slits for filtering effluent present in a septic system is disclosed in U.S. Pat. No. 5,569,387.
In addition to systems which utilize a single filter element within a filter system, multiple filter element systems for filtering effluent in a septic system are disclosed in U.S. Pat. Nos. 5,580,453 and 5,492,635. Each of these patents mandates a specific flow pattern for the effluent entering the filter system and exiting through a discharge opening in the housing of the filter system.
Because of limitations on the flow of the effluent through these systems, problems may arise from clogging of the filters which necessitates frequent cleaning of these systems. In addition, some of the screen filter systems can collapse even in normal use, also necessitating cleaning and/or replacement.
Thus, a need exists for a more effective system for filtering solids from the effluent of a septic system which overcomes the problems present in prior art systems.
Accordingly, it is an object of this invention to disclose a pump and filter system for filtering effluent present in a waste water system.
It is a further object of this invention to disclose a pump and filter system utilizing a tubular element containing an opening which is in communication with the relatively clear, horizontal effluent layer, which opening permits the effluent to flow into the pump and filter system.
It is a further object of this invention to disclose a pump and filter system for filtering effluent from a waste water system where the filter system contains a significant amount of filtering surface, thus reducing the likelihood of clogging of the filters during normal operation.
It is a further object of this invention to disclose a pump and filter system containing multiple filter elements which are easy to clean and replace.
It is a further object of this invention to disclose a pump and filter system where the pump is located adjacent to the filter elements.
It is a further object of this invention to disclose a shoulder seal secured within the filter housing which supports a filter element holder for the filter elements and which seals the filter element holder and filter elements in place within the pump and filter system.
It is a further object of this invention to disclose a check valve located in the bottom of the filter housing which when opened permits accumulated particulates within the pump and filter system to be flushed out of the system.
These and other objects and features of the present invention will become apparent to those skilled in the art from a consideration of the following detailed description, drawings and claims. The description, along with the accompanying drawings, provides a selected example of construction of the device to illustrate the invention.


A cutting tool retention mechanism, for example, typically used to retain a tool holder in a tool pocket of a tool changer magazine. A horizontal machine tool apparatus typically contains a plurality of tool pockets attached to a movable tool changer magazine and the mechanism of the present inventions provides an affirmative mechanism for retaining tool holders so that they do not separate from their respective tool pockets unless removal is desired. More particularly, a pair of opposed pivotal fingers each include a latch which can engage with or disengage from the internal groove of a tool holder to perform this function. Spring bias can be provided to encourage this affirmative engagement of the latches with the internal groove.

1. Technical Field of the Invention
The present invention relates to a tool retention mechanism, for example, typically used to retain a cutting tool holder in a tool pocket of a tool changer magazine. A horizontal machine tool apparatus typically contains a plurality of tool pockets attached to a movable tool changer magazine and the mechanism of the present inventions provides an affirmative mechanism for retaining tool holders so that they do not separate from their respective tool pockets unless removal is desired. More particularly, a pair of opposed pivotal fingers each include a latch which can engage with or disengage from the internal groove of a tool holder to perform this function. A biasing force can be provided, for example, by one or more springs, to encourage this affirmative engagement of the latches with the internal groove.
2. Brief Description of the Related Art
The present invention relates to a cutting tool retention mechanism. This mechanism is designed to be received in a tool pocket and to interface with and retain within the tool pocket a tool holder having an internal groove, such as, for example, a xe2x80x9chohlschaftkegelxe2x80x9d (or xe2x80x9cHSKxe2x80x9d) tool holder. An HSK tool holder is a special form of tool holder configured according to a xe2x80x9cDINxe2x80x9d (German engineering) standard and designates short, hollow, tapered tool shanks, wherein the tool shank includes a conical surface and a face formed on an integral tool changer gripping flange thereof, and wherein a machine tool spindle is adapted to grip both the conical surface and the face of the tool holder for positive rotation thereof. Unlike well-known ANSI (American National Standards Institute) standard solid tool holders, which are pulled into a spindle seat by way of a retention stud extending from the generally cylindrical shank thereof, an HSK tool shank has an internal relief, or retaining groove, so that, once inside a machine spindle, internal gripping fingers of the spindle assembly direct outward and rearward forces against the tool shank, to retain it securely.
Low-force analogues of spindle gripping arrangements are known for retaining hollow shank tools within tool storage pockets, for example, the employment of spring loaded balls which engage the tool retaining groove. Typically, an external actuating means is employed to release the tool from its tool storage receptacle.
The present invention relates to a cutting tool retention mechanism, for example, typically used to retain a tool holder in a tool pocket of a tool changer magazine. A tool changer magazine of a horizontal machining center contains a plurality of tool pockets, each of these tool pockets being adapted to store one tool such that, by the tool changer magazine, a plurality of tools are accessible to the machining center for performing a variety of machining operations, for example, utilizing a rotating spindle. In operation, when the machining center needs to utilize any specific tool for a specific machining operation, the tool changer magazine is moved such that the desired tool in its tool pocket is positioned in an index location where the desired tool can be removed from the pocket and mounted to the spindle. Typically, a machining center will retrieve (and replace) between 5 and 25 cutting tools during a complete machining cycle of a typical workpiece. With each tool change, the entire magazine, and as such, each of the tools held in the pockets thereof, moves. Therefore, because of the frequent, and sometimes jerky, movement of the magazine, it is desirable to provide for affirmative retention of the various tool holders in their respective tool pockets until such time as a specific tool is needed is desirable, and the current invention provides for this retention.
All of the embodiments disclosed herein have similar function. In function, a fulcrum supports at least a pair of opposed fingers which function as levers. Springs are used to provide a biasing force such that the bias portions of the opposed fingers are urged toward each other to a physical limit controlled, in one embodiment hereof, by a pair of channels provided in a spring plate. The finger bias portions are on one side of the fulcrum and the finger latch portions are on an opposite side of the fulcrum, such that, in this configuration, opposed latches toward the end of the finger latch portions are spaced a furthest distance from each other. In this configuration, the latches are spaced to engage an internal groove in an HSK tool holder to retain that tool holder in its respective tool pocket.
A tool holder can be forced on and off the latches. For example, when pushing a tool holder into the receiving portion of the tool pocket body, the holder will engage the opposed latches. As these latches are spaced a distance apart greater than the smallest diameter of the holder, a force will be applied to the latches overcoming the biasing force, provided by the springs, which is applied toward the opposite end of the fingers on the other side of the fulcrum. When the holder is pushed into the receiving portion a sufficient distance for engagement of the latches with the HSK tool holder internal groove, the springs will force the latches away from each other to affirmatively hold the tool holder. Alternatively, the finger bias portions can have a force applied thereto to overcome the force of the springs to push the finger bias portions away from each other, as permitted by the geometry of the spring plate channel. The separation of the finger bias portions causes the opposed latches on the finger latch portions on the opposite side to the fulcrum to move toward each other. This action can be initiated for insertion or removal of a tool holder and would cause less parts xe2x80x9cwear and tearxe2x80x9d, but requires additional components to implement.
The preferred embodiment of the present invention employs a unitary tool retention mechanism constructed of plastic. In another embodiment, a unitary plastic tool retention mechanism employs a wear-resistant surface in the form of, in one embodiment hereon, shields attached to the finger latch portions. The shields can be of metal or other material with high wear resistance to prolong the life of the mechanism. Alternatively, the mechanism, itself, can be constructed of a wear-resistant material, in which case, the shields are unnecessary. In yet another embodiment, a plurality of components are employed to permit the fingers to be made of a wear-resistant metallic material, such as steel, with the inclusion of the lever pivot by insertion of pins through bores in a retention support and each finger.
In still another embodiment hereof, a plurality of pairs of opposed fingers, or an odd number of individual fingers, are spaced equidistantly around the support. In an even further embodiment hereof, the pair of opposed fingers is replaced with a single finger, in which case, the latch distance and the bias distance are defined as the distance of the latch and the bias portion, respectively, to a reference, such as, for example, the central axis of the support.
More particularly, in the preferred embodiment hereof, the present invention comprises a retention mechanism having a pair of opposed fingers, each of the fingers extending from a support, each of the fingers having a latch spaced from the support, the support permitting each of the fingers to be pivoted to vary a latch distance between the latches.
Further, where each of the fingers has a latch portion including the latch and a bias portion, and where, when at least one of the fingers is pivoted to vary the latch distance, a bias distance between the bias portions varies oppositely thereto, as permitted by the support. That is, where at least one of the fingers is pivoted to decrease the latch distance, the bias distance will increase, although not necessarily inversely thereto. Additionally, each bias portion may have a spring to exert a biasing force on the bias portion, thereby urging the bias portion in a direction toward the bias portion of the other finger.
As the retention mechanism is designed to permit the latches to engage an internal groove of a tool holder, the latches preferably have an orientation away from each other, although the latches may have any configuration suitable to engage the internal groove of the tool holder.
These and additional objects, features and advantages of the present invention will become apparent to those reasonably skilled in the art from the description which follows, and may be realized by means of the instrumentalities and combinations particularly pointed out therein.


An improved eyeglasses fastening device has a fastening belt, a pair of decoration attachments, a pair of connecting pieces and two elastic rubber rings. Each decoration attachment having one side provided with an artistic printing has a two-staged engagement through hole in the diametric direction which is a round hole in communication with an oval hole. Each connecting piece has a central extension finger provided with a pointed piercing end. The decoration attachments are movably guided through the ends of the fastening belt respectively and the rubber rings are also secured to the terminals of the fastening belt by way of the connecting pieces respectively so that the decoration attachments can be adjustably engaged with the rubber rings when the rubber rings are attached to the temples of an eye glasses. Such a structure enables the terminals of the fastening belt covered with the connecting pieces to be concealed in use.

The present invention relates to an improved eyeglasses fastening device including a fastening belt, a pair of decoration attachments, a pair of connecting pieces and two elastic rubber rings. Each decoration attachment having one side provided with an artistic printing has a two-staged engagement through hole in the diametric direction which is a round hole in communication with an oval hole. Each connecting piece has a central extension finger provided with a pointed piercing end. The decoration attachments are movably guided through the ends of the fastening belt respectively and the rubber rings are also secured to the terminals of the fastening belt by way of the connecting pieces respectively so that the decoration attachments can be adjustably engaged with the rubber rings when the rubber rings are attached to the temples of a pair of eyeglasses. Such a structure enables the terminals of the fastening belt covered with the connecting pieces to be concealed in use.
The fastening belt of the present invention permits a pair of eyeglasses to be firmly engaged with the fastening device of its temples so that the fastening device will not be easily disengaged from the temples of a pair of eyeglasses due to violent external force in use in one aspect and the temples of a pair of eyeglasses will not be abraded by the fastening device of the present invention in another aspect.
Referring to FIGS. 1, 2, the conventional eyeglasses fastening device is comprised of a fastening belt 10, two rubber rings 20, two metallic retainers 30 and two decoration articles 40. Each decoration article 40 has a round decoration disc 41 which is provided with a pair of parallel locking plates 42 on one side thereof. The terminal ends of the fastening belt 10 are led through the rubber rings 20 and are bent backwards first. Thereafter, the reversely led terminal ends of the fastening belt 10 are in locking engagement with the locking plates 42 which are punched to firmly encompass the terminal ends. Afterwards, the retainers 30 are engaged with the rubber rings 20 respectively, rendering the rubber rings 20 in a digit 8 shape to complete the assembly.
Referring to FIGS. 3, 3A, in practical use, the 8-shaped rubber rings 20 are engaged with the ends of the temples of a pair of eyeglasses 50 first, and then the 8-shaped rubber rings 20 are pushed outwardly to lock the fastening belt in place with respect to the temples of the eyeglasses 50.
Such a prior art eyeglasses fastening device has the following disadvantages in practical use:
1. The temples of a pair of eyeglasses can readily push the retainer moving in such a manner that the 8-shaped rubber rings 20 will widely expand to make the fastening belt 10 separated from the temples. PA0 2. The metallic retainers 30 are in constant contact with the temples 50 of a pair of eyeglasses, causing abrasive damage to the temples thereof easily. PA0 3. The metallic retainers 30 can not be fixedly engaged with the rubber rings, so they are easily lost in use. PA0 4. The decoration disks 41 of the decoration articles 40 are not exposed externally for sure every time in use, making their function less effective. PA0 5. The ends of the fastening belt 10 are fixedly engaged with the decoration articles 40 only by two punched locking plates 42, causing them to be easily disengaged in use. PA0 6. The decoration articles 40 are commonly made of metal, making a wearer feel uncomfortable when in direct contact in one aspect and they are easily oxidized by sweat in long use.


An arrangement for cleaning contaminated ground water and a ground region through which it flows comprises a shaft extending to a region of ground water to be cleaned, the shaft having a shaft wall with two water permeable wall regions located above and below a ground water level so that a separating region is formed in the shaft between the water permeable regions under the ground water level, a throughgoing passage extending through the separating region and ending above the ground water level in the shaft, a filter arranged in the shaft, a circulating pump arranged in the shaft so that the throughgoing passage forms a part of a flow path. The circulating pump provides a ground water circulation which passes through the shaft, through the water permeable wall regions, through the surrounding ground region and through the filter arranged in the shaft. The filter includes a pourable and fluid filter material which fills a shaft chamber located under the separating region. The throughgoing passage has a portion which is permeable for the ground water and not permeable for a filtering material and which extends into the filter material filling, and an additional passage extends through the separating region and provided for a pipe which passes from above for influencing the ground water or the fluid filter material.

The present invention relates to an arrangement for cleaning contaminated ground water.
More particularly, it relates to an arrangement which has a shaft extending to the region of ground water to be cleaned and provided with two separate water permeable regions located above and below a ground water level and a separating region therebetween, with a throughgoing passage extending through the separating region and ending above the the ground water level in the shaft.
Arrangements of the above mentioned general type are known in the art. One such arrangement is disclosed in the German patent DE-PS 3,931,012.
The German document DE-OS 3,612,468 discloses a filtering well in which a bore hole after removing the sand is filled with filter gravel.

Arrangement for cleaning contaminated ground water


A haptic is provided for use in an accommodating intraocular lens. The haptic has multiple filaments, each connected to the edge of the optic at one end. Each filament has a shape that conforms to an equatorial region of the capsular bag. The haptic couples the forces exerted by the capsular bag of the eye during accommodation radially to the edge of the optic, produce a diametric expansion or compression of the optic. This diametric motion distorts the optic, producing a change in any or all of the anterior radius, the posterior radius, and the thickness. These changes affect the power of the lens and/or location of the image. The haptic may optionally have a thin membrane joining the filaments at the optic end, and may optionally have a connecting ring that joins the filaments at the end opposite that of the optic.

Field of the Invention
The present invention is directed to intraocular lenses, and more particularly to accommodating intraocular lenses.
Description of the Related Art
A human eye can suffer diseases that impair a patient's vision. For instance, a cataract may increase the opacity of the lens, causing blindness. To restore the patient's vision, the diseased lens may be surgically removed and replaced with an artificial lens, known as an intraocular lens, or IOL. An IOL may also be used for presbyopic lens exchange.
The simplest IOLs have a single focal length, or, equivalently, a single power. Unlike the eye's natural lens, which can adjust its focal length within a particular range in a process known as accommodation, these single focal length IOLs cannot accommodate. As a result, objects at a particular position away from the eye appear in focus, while objects at an increasing distance away from that position appear increasingly blurred.
An improvement over the single focal length IOLs is an accommodating IOL, which can adjust its power within a particular range. As a result, the patient can clearly focus on objects in a range of distances away from the eye, rather than at a single distance. This ability to accommodate is of tremendous benefit for the patient, and more closely approximates the patient's natural vision than a single focal length IOL.
When the eye focuses on a relatively distant object, the lens power is at the low end of the accommodation range, which may be referred to as the "far" power. When the eye focuses on a relatively close object, the lens power is at the high end of the accommodation range, which may be referred to as the "near" power. The accommodation range itself is defined as the near power minus the far power. In general, an accommodation range of 4 diopters is considered sufficient for most patients.
The human eye contains a structure known as the capsular bag, which surrounds the natural lens. The capsular bag is transparent, and serves to hold the lens. In the natural eye, accommodation is initiated by a series of zonular fibers, also known as zonules. The zonules are located in a relatively thick band mostly around the equator of the lens, and impart a largely radial force to the capsular bag that can alter the shape and/or the location of the natural lens and thereby change its power.
In a typical surgery in which the natural lens is removed from the eye, the lens material is typically broken up and vacuumed out of the eye, but the capsular bag is left intact. The remaining capsular bag is extremely useful for an accommodating intraocular lens, in that the eye's natural accommodation is initiated at least in part by the zonules through the capsular bag. The capsular bag may be used to house an accommodating IOL, which in turn can change shape and/or shift in some manner to affect the power and/or the axial location of the image.
The IOL has an optic, which refracts light that passes through it and forms an image on the retina, and a haptic, which is a structure that mechanically couples the optic to the capsular bag. During accommodation, the zonules exert a force on the capsular bag, which in turn exerts a force on the optic. The force may be transmitted from the capsular bag directly to the optic, or from the capsular bag through the haptic to the optic.
A desirable optic for an accommodating IOL is one that distorts in response to a squeezing or expanding radial force applied to the equator of the optic (i.e., by pushing or pulling on the edge of the optic, circumferentially around the optic axis). Under the influence of a squeezing force, the optic bulges slightly in the axial direction, producing more steeply curved anterior and/or posterior faces, and producing an increase in the power of the optic. Likewise, an expanding radial force produces a decrease in the optic power by flattening the optic. This change in power is accomplished in a manner similar to that of the natural eye and is well adapted to accommodation. Furthermore, this method of changing the lens power reduces any undesirable pressures exerted on some of the structures in the eye.
One challenge in implementing such an optic is designing a suitable haptic to couple the optic to the capsular bag. The haptic should permit diametric (or, equivalently, radial) motion of the optic by coupling the force exerted by the capsular bag to the edge of the optic, which is generally not available with known haptics.
For instance, consider a haptic disclosed in United States Patent Application Publication No. US 2005/0131535, published Jun. 16, 2005 to Randall Woods. The haptic of Woods is a generally resilient, discoid-shaped body that fits inside the capsular bag. The posterior side of the haptic houses a lens that is typically kept in contact with the posterior wall of the capsular bag. During accommodation, so that the eye can focus on near objects, the capsular bag compresses radially and bulges axially, and the optic, which is held in contact with the posterior wall of the capsular bag, distorts and thereby changes its power.
In Woods, the optic itself is surrounded diametrically by a solid body, referred to by Woods as a "resilient body". Such a resilient body limits the coupling of radial forces to the optic itself. For instance, a compressive radial force exerted by the capsular bag on the haptic would be partially absorbed by the haptic itself, which would couple the compressive force partially into compressing its own material in the region surround the optic. Likewise, an expansive force exerted by the capsular bag on the haptic would also be largely absorbed by the haptic, which would have to stretch in a tangential manner in the region surrounding the optic.
Haptic designs that are used with other IOL styles are generally unsuitable as well. As an example, consider the haptics used in a style of accommodating IOL in which the forces applied by the capsular bag result primarily in an axial translation of the optic, without a significant distortion of the optic. As a specific example, U.S. Pat. No. 5,275,623, issued Jan. 4, 1994 to Faezeh Sarfarazi, discloses a lens that uses a pair of optics and a flexible haptic that responds to the forces of the capsular bag by changing the separation between the optics. Both optics have individual powers, and the total optical power of the eye is adjusted by altering the separation between the optics. The optics themselves are not significantly distorted. Indeed, the haptic largely prevents distortion of the optics by encircling the circumference of the optic with a ring that axially translates the optic under the influence of the capsular bag forces, but retains its own shape under said forces. In general, a haptic in which the optic is encircled by a thick supporting ring is unsuitable, because the forces imparted by the capsular bag are not sufficiently coupled to the edge of the optic.
As yet another example that known haptics are generally unsuitable for coupling the capsular bag forces directly to the diameter of the optic, consider United States Patent Application Publication No. US 2004/0181279, published Sep. 16, 2004 to Yehoshua Nun. Nun discloses a lens that has an optic located between a rigid haptic and the posterior wall of the capsular bag. As the zonules exert force on the capsular bag, the optic is compressed or expanded against the rigid haptic, leading to a change in the radii of the optic as well as the optic thickness. A potential drawback of the Nun IOL is that the haptic is biased anteriorly by pressure from the optic, and may lead to fatigue at the points where the haptic is mounted against the ciliary body in the eye. In addition, distortion of the optic is accomplished by longitudinal (or, equivalently, axial) forces, exerted between the capsular bag wall and the rigid haptic. Indeed, this haptic is also unsuitable for coupling the capsular bag forces to the edge of the optic.
Accordingly, there exists a need for an intraocular lens with a haptic that permits diametric motion of the optic by efficiently coupling the force exerted by the capsular bag and zonules to the edge of the optic. Such a haptic would enable use of a desirable style of optic, which changes its power (i.e., radius of curvature, shape and/or thickness) in response to a squeezing or expanding force applied radially to its edge.

Haptic for accommodating intraocular lens


The present invention relates to a composition comprising an antimicrobial effective amount of a biocide selected from the group consisting of aromatic 2-N-hydroxy-thiourea and N-hydroxy-quinazolinone, and derivatives and combinations thereof, and at least one component selected from the group consisting of soaps, shampoos, skin-care medicaments, cosmetics, plastics and paints. Also disclosed is a novel process for making the biocide.

Compounds exhibiting excellent biocidal activity are well-known in the art. For example, pyrithione salts, such as zinc pyrithione, are known to provide excellent biocidal activity, including broad spectrum anti-bacterial and anti-fungal activity. There are many uses for these pyrithione biocides. By way of illustration, U.S. Pat. No. 4,818,436 discloses the use of pyrithiones in metalworking fluids; U.S. Pat. No. 4,401,770 discloses urethane shoe inserts having antimicrobial activity; and U.S. Pat. No. 4,935,061 discloses their use in paints.
Despite the excellent biocidal (particularly fungicidal) activity attributable to the pyrithione salts, these compounds do have drawbacks for certain applications, most notably poor ultraviolet ("uv") light stability. Accordingly, new compounds exhibiting excellent biocidal activity but also exhibiting enhanced uv light stability would be highly desired by the biocides manufacturing community.

Compositions comprising N-hydroxyquinazolinone and 2-N-hydroxythiourea benzoate compounds as biocides


In a system that executes air fuel ratio feedback control based on air fuel ratio signals of a pair of air fuel ratio sensors arranged at locations upstream and downstream of a catalyst of an internal combustion engine, an abnormality diagnosis apparatus can diagnose abnormality in a fuel system of the internal combustion engine in an accurate manner by using a signal of the air fuel ratio sensor downstream of the catalyst. A control unit in the form of an ECU (30) includes a feedback operation state determination section (32), an oxygen storage saturation determination section (33), an averaging start determination section (34), an averaging section (35), and an abnormality determination section (36). An abnormality in the fuel system of the internal combustion engine is determined by using a second air fuel ratio signal (V2) output from the second air fuel ratio sensor downstream of the catalyst only when the amount of oxygen storage in the catalyst is saturated.

1. Field of the Invention
The present invention relates to an abnormality diagnosis apparatus for an internal combustion engine capable of diagnosing the presence or absence of abnormality in the internal combustion engine in which a three-way catalytic converter (hereinafter simply referred to as a "catalyst") for purifying an exhaust gas is arranged in an exhaust system, with a pair of air fuel ratio sensors being disposed at locations upstream and downstream of the catalyst.
2. Description of the Related Art
As a conventional abnormality diagnosis apparatus for an internal combustion engine, there has hitherto been known one in which a pair of air fuel ratio sensors are arranged at locations upstream and downstream of a catalyst, so that an abnormality in the catalyst is detected based on detection signals from the individual air fuel ratio sensors (see, for example, a first patent document: Japanese patent application laid-open No. H6-129240).
Also, there has been proposed an apparatus in which a pair of air fuel ratio sensors are arranged at locations upstream and downstream of a catalyst, and an abnormality in an air fuel ratio feedback control system is detected based on an oxygen sensor downstream of the catalyst (see, for example, a second patent document: Japanese patent application laid-open No. 2004-204716).
In addition, there has been proposed an apparatus in which the amount of oxygen storage during a fuel-cut operation is calculated so that an abnormality in an oxygen sensor downstream of a catalyst is diagnosed in accordance with the amount of oxygen storage (see, for example, a third patent document: Japanese patent application laid-open No. 2003-14683).
In the conventional abnormality diagnosis apparatuses for an internal combustion engine, in case of the first patent document, there is a problem that an abnormality in the catalyst can be determined, but an abnormality in the fuel control system can not be detected.
Also, in case of the second patent document, an abnormality in the feedback control system is detected by the oxygen sensor downstream of the catalyst, but no consideration is given to the state of the oxygen storage in the catalyst, and no account is taken of the case where the amount of feedback control by means of the oxygen sensor downstream of the catalyst is limited to a small value because of the amount of oxygen storage in the catalyst, or the case where the signal of the oxygen sensor downstream of the catalyst is output in a delayed manner, so there is a problem of possibility of making an incorrect abnormality determination.
Moreover, since no consideration is given to the state of the catalyst, there is a problem of possibility of making an incorrect abnormality determination when the output signal of the oxygen sensor downstream of the catalyst is disturbed or fluctuated due to deactivation or degradation of the catalyst.
In addition, in the third patent document, the amount of oxygen storage in the catalyst is calculated but only an abnormality in the oxygen sensor downstream of the catalyst is diagnosed, thus posing a problem that an abnormality in the fuel control system can not be detected.
Further, in the feedback control according to the signals of the oxygen sensors upstream and downstream of the catalyst, as in the conventional apparatuses described in the above-mentioned first through third patent documents, there arises the following problem. That is, in case where there occurs a situation where an amount of fuel more than estimated is injected due to the occurrence of abnormality in the fuel system, e.g., abnormality in a fuel injector only for one cylinder in a multicylinder internal combustion engine, it becomes impossible to control the exhaust gas downstream of the catalyst within a normal range because of the construction or configuration of each of the conventional apparatuses.

Abnormality diagnosis apparatus for internal combustion engine


An engineers wrench has at least one open end forming a mouth which defines a mouth opening. The mouth opening is laterally delimited by a pair of mutually oppositely disposed lateral, surfaces which define a wrench width. At least inwardly disposed sections of the lateral surfaces have a slight convex-cylindrical curvature defined by a finite radius of curvature so that the mouth opening widens in the direction towards respective outer edges to a mouth width which exceeds the wrench width. The mouth opening is inwardly delimited by a mouth base; two substantially flat surfaces are interconnected at the mouth base as well as connected to associated ones of the lateral surfaces through respective connecting surfaces. The connecting surfaces have a concave-cylindrical curvature defined by a smaller radius of curvature than the finite radius of curvature of the convex-cylindrically curved lateral surfaces.

The present invention relates to a new and improved construction of an engineers wrench. Such wrench is a tool for tightening or loosening threaded joints and engages, during such process, a polygonal or multi-edged member of the threaded joint like, for example, the hexagonal or square head of a screw or a hexagonal nut. The wrench typically comprises a shaft and either at one or both of its ends a recess which is open on one side and defines the mouth of the wrench. The mouth is laterally delimited by two mutually oppositely disposed lateral surfaces at a spacing which defines a wrench width across the lateral surfaces. The wrench width is slightly wider than the diametral spacing between mutually opposed surfaces of the polygonal or multi-edged member of the threaded joint to be engaged by the wrench.
The two lateral surfaces of conventional wrenches like the associated surfaces of the multi-edged member to be engaged by the wrench, are mutually parallel flat surfaces. Due to the slight clearance existing between the lateral surfaces laterally delimiting the mouth opening of the wrench and the associated surfaces of the polygonal or multi-edged threaded joint member onto which the wrench is placed, the wrench will be tilted relative to the threaded joint member by a small amount during tightening or loosening of the threaded joint. As a result, the lateral surfaces of the wrench engage the edges of the threaded joint member, particularly the inner edge with respect to the mouth opening on one side and the outer edge with respect to the mouth opening on the opposite side. The torque for tightening or loosening the threaded joint, then, is transmitted via the edges.
During such operation, high surface pressures occur at the edges. Particularly upon repeated tightening and loosening of the threaded joint member, these high surface pressures will lead to wear at the respective edges whereby the function of the members will be negatively affected during the course of time.
The invention specifically relates to an engineers wrench which engages not the edges but the lateral surfaces of the polygonal or multi-edged member of the threaded joint.
Various constructions are known to realize such engagement.
German Patent No. 231,581 relates to a wrench in which the engagement surfaces of the jaws, i.e. the lateral surfaces delimiting the mouth opening, are formed by two flat surface portions which adjoin each other in a roof-like manner. Edges are formed between the surface portions and face each other. Outer surface portions of each one of the two lateral surfaces are disposed at a spacing, which corresponds to the wrench width, from inner surface portions of each one of the two mutually opposite lateral surfaces. Also in this wrench construction, the lateral surfaces delimiting the mouth opening press onto the edges of the polygonal or multi-edged member of the threaded joint during torque transmission.
German Patent No. 697,361 shows a wrench having a mouth opening which is delimited by flat surfaces and which is substantially adapted to the shape of a hexagonal nut. All of the corners of the mouth opening define cylindrical recesses. By virtue thereof, the wrench is intended to engage the nut only outside of the corners of the nut. Line contact of an edge will cause notching.
International Published Patent Applications Nos. 93/10945 and 94/23902 show a wrench in which the lateral surfaces delimiting the mouth opening initially, i.e. adjacent the outer edges which define the mouth opening, comprise respective mutually parallel flat surface portions. Adjoined thereto in the lateral surfaces, are disposed respective indentations which, in turn, are adjoined by convex-cylindrical sections. The convex-cylindrical sections, then, continuously merge with an arcuate mouth base. The radii of curvature of the convex-cylindrical sections are equal to half the wrench width. High surface pressures result also in this construction due to the small radii of curvature.
German Published Patent No. 1,088,437 shows a wrench in which protrusions are formed in the mouth opening which only engage the lateral surfaces of screw heads or nuts.


A printing apparatus includes a recording medium for recording image data and recording medium information, a recording medium read-out device, a print control device for giving a print command for printing the image data, a recording device for recording the recording medium information of the recording medium and information on automatic print records and a comparator. When the print control device has detected that a battery for a power source will run down during printing, the comparator detects, after turning on of the power source again, that the recording medium information of the recording device is coincident with that of the recording medium and then, the print control device gives a further print command for continuously printing, in accordance with the information on the automatic print records recorded in the recording device, the image data designated by the print command given prior to turning on of the power source again.

1. Field of the Invention
The present invention relates to a printing apparatus for automatically printing image data shot by a photographic device such as a digital still camera and a digital video camera and recorded in a recording medium.
2. Description of the Prior Art
In recent years, the market is expanding for imaging devices such as a digital still camera and a digital video camera, which are capable of recording a high-quality digital still image on a nonvolatile memory card. Meanwhile, demands and applications for not only viewing on a television monitor or a personal computer but converting to a hard-copy print the digital still image recorded in the digital still camera and the digital video camera are increasing. Under such circumstances, many printing apparatuses employing various printing types such as a sublimation type, a heat transfer type and an ink jet type, which read digital still images from a memory card so as to record the digital still images on a recording paper sheet are put on the market.
In accordance with automatic print setting files for setting desired digital still images to be printed and print quantities of the desired still images, which are formulated in the memory card, these known printing apparatuses automatically print the desired digital still images in order to print the desired digital still images easily. Alternatively, some of the known printing apparatuses may have an automatic print function of automatically printing, in case the automatic print setting files are not formulated in the memory card, all the digital still images recorded in the memory card.
FIG. 5 shows a conventional printing apparatus. The conventional printing apparatus includes a memory card 1, a memory card control unit 2 for performing read-write of the memory card 1, a power source 3, an image memory 6 for storing image data recorded in the memory card 1 and a control unit 4 for controlling recording of digital still images in the image memory 6 and controlling automatic print so as to continue or stop the automatic print by judging whether or not a detected remainder of a battery capacity enables printing. The conventional printing apparatus further includes an operating unit 5, a print engine 7 for printing the data of the image memory 6 and a thermal head 8.
FIG. 3 shows one example of a configuration of a directory recorded in the memory card 1. The directory includes digital still images 13 to 18 and folders 11 and 12 for storing the digital still images 13 to 18. Meanwhile, FIG. 4 shows one example of automatic print setting files 19 to 22 recorded in the memory card 1. The automatic print setting files 19 to 22 correspond to the digital still images 13 to 16, respectively. In the automatic print setting files 19 to 22, the descriptions "PRT PID=001" and "PRT PID=002" denote JOB numbers, while the description "PRT PID=STD" denotes output of one digital still image to one recording paper sheet. Meanwhile, the descriptions "PRT QTY=1" and "PRT QTY=3" denote a print quantity of one sheet and a print quantity of three sheets, respectively, while the description "IMG FMT=EXIF2-J" designates a recording format of the images. Furthermore, the description  of the automatic print setting file 19 designates the digital still image 13, the description  of the automatic print setting file 20 designates the digital still image 14, the description  of the automatic print setting file 21 designates the digital still image 15 and the description  of the automatic print setting file 22 designates the digital still image 16.
Hereinafter, operation of the conventional printing apparatus is described with reference to FIGS. 3 to 5. By operating the operating unit 5 so as to turn on the power source 3, the control unit 4 delivers to the power source 3 a command for turning on the power source 3. When an AC adapter is connected to the power source 3, power is supplied to the power source 3 from the AC adapter. When only a battery is connected to the power source 3, power is supplied to the power source 3 from the battery. Subsequently, the control unit 4 detects whether or not the memory card 1 in which the automatic print setting files and the digital still images are recorded is connected to the memory card control unit 2. If the control unit 4 has detected that the memory card 1 is connected to the memory card control unit 2, the memory card control unit 2 reads the memory card 1 and the control unit 4 judges whether or not the automatic print setting files 19 to 22 are recorded in the memory card 1. In case the control unit 4 has judged that the automatic print setting files 19 to 22 are recorded in the memory card 1, the control unit 4 reads from the memory card 1 data of the digital still image 13 designated by the automatic print setting file 19 and expands the data of the digital still image 13 into image information so as to store the image information in the image memory 6. Upon delivery of a print command from the control unit 4 to the print engine 7, the print engine 7 supplies the image information of the image memory 6 to the thermal head 8 through pulse signals such that the digital still image 13 is printed on one sheet in accordance with the description "PRT QTY=1" in the automatic print setting file 19. Thereafter, automatic print of the digital still images 14 to 16 is likewise performed in accordance with the automatic print setting files 20 to 22, respectively. Thus, the automatic print of the digital still images 13 to 16 is completed.
On the other hand, in case the control unit 4 has judged that the automatic print setting files 19 to 22 are not recorded in the memory card 1, the conventional printing apparatus outputs one print of the digital still images 13 to 18. Alternatively, if the conventional printing apparatus has a function of setting a plurality of prints by a print quantity setting menu or the like, the conventional printing apparatus may output a plurality of prints of each of the digital still images 13 to 18.
However, in the conventional printing apparatus, automatic print in which power is supplied to the power source 3 from the battery might be interrupted in a run-down state of the battery. In such a case, even if print can be performed subsequently by connecting the recharged battery or the AC adapter to the power source 3, the automatic print cannot be resumed subsequently to a printing stage attained at the time of interruption of the automatic print. Therefore, an operator of the conventional printing apparatus should confirm up to which printing stage the automatic print has been completed. In case set data of completed printing has been erased from the automatic print setting files or print quantities have been set, the operator has to confirm that the set print quantities and the completed print quantities are correct. If the set print quantities and the completed print quantities are not correct, the operator should perform resetting of the automatic print setting files by resetting the print quantities, etc.
Meanwhile, in case the automatic print has been interrupted when the automatic print setting files are not recorded in the memory card, some of the digital still images, whose printing has been completed, should be erased from the memory card.
Therefore, in case the automatic print has been interrupted in the conventional printing apparatus, such a problem as very poor operating efficiency arises due to the necessity for resetting of the automatic print setting files or erasure of the digital still images from the memory card.
In such a case, it is needless to say that the automatic print can be performed again from an initial printing stage without taking any countermeasures. However, in this case, already outputted prints become useless disadvantageously.

Matsushita Electric Industrial Co., Ltd.


The invention relates to a device for measuring quantities of heat while simultaneously measuring the evaporation kinetics and/or condensation kinetics of the most minute amounts of liquid in order to determine thermodynamic parameters. The aim of the invention is to determine low thermal outputs, which are absorbed or released by the sample, as well as small differences between thermal outputs with regard to a reference measurement of the same magnitude. To this end, a most minute amount of liquid is located inside a measuring chamber having a constant temperature and air humidity. At least one thermal sensor is provided for repeatedly measuring the thermal radiation emitted from the most minute amount of liquid. A measuring means serves to determine the time-dependent change in the most minute amount of liquid. A computer is assigned to the measuring chamber in order to register, display, evaluate and/or subsequently process the measured values.

This invention relates to a device for measuring quantities of heat while simultaneously measuring the evaporation kinetics and/or condensation kinetics of most minute amounts of liquid in order to determine thermodynamic parameters according to the species of patent claims. The quantities of heat can be absorbed during evaporation and/or released during condensation by very minute samples being mainly composed of liquid.
The inventive device predominantly serves to simultaneously measure the specific evaporation heat and vapor pressure of solutions at almost room temperature. Provided that a chemical equilibrium exists in the liquid and the evaporation process and/or condensation process are/is combined with a displacement of the chemical equilibrium, this device also serves to measure the specific chemical heat of reaction. For compound systems consisting of a solution being in contact with a solid (crystalline) phase of the solute, this device is used to measure the concentration of the saturated solution and the specific heat of solution, too. The most minute amount of liquid can also be a gel-like solvent-binding substance. The device is designated for measuring such kinds of solutions for which the vapor pressure of the solvent does not exceed the vapor pressure of the saturated water vapor in terms of magnitude and for which the vapor pressure of the solute above the solution has such a low value compared with the vapor pressure of the solvent that it can be ignored.
For all calorimeter principles to date the current state of art allows to derive the finding according to which the output that can still be measured becomes the smaller the faster the quantity of heat is released. The resulting characteristic time determines the minimum possible time constant required by the calorimeter to be able to measure the total quantity of heat released. Therefore, for maximum time constants of about 1000 s which are technically feasible today the output that can still be reliably measured is about 0.1 μW; it decreases down to about 10 nW for a time constant of 30 s. Consequently, the desired miniaturization of calorimeters for the application of very minute amounts of substances, e.g. when using thermally controlled micrometering cells based on chips, will only offer advantages for quantities of heat in the nJ range, if this quantity of heat is available within some seconds. This state-of-the-art finding is quite contrary to the demands placed on the measuring task to be solved by this inventive device.

Device for measuring quantities of heat while simultaneously measuring the evaporation kinetics and/or condensation kinetics of the most minute amounts of liquid in order to determine thermodynamic parameters

IMB Institut Fuer Molekulare Biotechnologie E.V.


A military tank with a heavy weapon suspended to pivot in elevation in a turret that rotates on a chassis. The turret (2) is on the rear half (1.2) of the chassis (1) and its drive mechanisms are in the forward half. At least the section of the upper surface (1.2) below the turret slopes back and down at a prescribed angle (.alpha.) to the horizontal. The vertical longitudinal cross-section (LM) of the turret is a wedge that tapers together forward with its bottom (2.1) paralleling the upper surface of the chassis and its top (2.2) at another prescribed angle (.beta.) to the horizontal.

The invention concerns a military tank with a heavy weapon suspended to pivot in elevation in a turret that rotates on a chassis.
The turret in known military tanks usually rotates around a vertical axis through the center of the chassis. The turret is often shaped like a squat parallelipiped, sometimes with beveled corners and sloping walls. The weapon is usually secured to the turret with at least the end behind the trunnions extending inside.
Also known (from German OS 3 642 920) are what are called armored howitzers. The turret that accommodates the heavy weapon in an armored howitzer is behind the center of the chassis and the drive mechanisms are forward.