FIGS. 1-8 show a drawer safety latch 10 made in accordance with the present invention. Referring to FIGS. 2, 4, 5, and 6, the safety latch 10 is a substantially "L" shaped body (seen best in FIG. 6), including a vertical leg 12, a horizontal leg 36 projecting inwardly from said vertical leg 12, and an engaging arm 20 projecting forward from said horizontal leg 36. The vertical leg 12 lies in one plane, and the engaging arm 20 extends along a second plane that is parallel to and offset from the vertical leg. The engaging arm 20 is cantilevered from the horizontal leg 36, and pivots upwardly and downwardly parallel to the vertical leg 12 by means of flexing of the latch material between the engaging arm 20 and the horizontal leg 36. The engaging arm 20 may be deflected by pushing it down until the apex 38 of the second ramp 28 is below the cross bar 32, allowing the drawer to open. The engaging arm 20 is naturally biased to spring back up when it is not being deflected downwardly. As seen in FIGS. 1 and 3, the cabinet 34 has a frame and a front face which includes the cross bar 32. The front face defines an opening 46 through which the drawer 22 passes as it moves forward and backward relative to the cabinet 34. The front face and its cross bar 32 have a front-to-back depth, and the trough 30 on the latch 10 is deep enough to receive the cross bar 32. The drawer 22 has left and right sides 23, 25 and a bottom 27. The safety latch 10 is mounted inside of the drawer 22 such that the outside face 16 of the vertical leg 12 of the safety latch 10 lies against the inside surface 42 of the left side 23 of the drawer 22. The protective sheet 24 has been peeled off of the outside face 16, allowing the vertical leg 12 to be adhered to the side 23 of the drawer 22. To facilitate the installation, the safety latch 10 is mounted such that the upper surface 18 of the vertical leg 12 is parallel to, and flush with, the upper edge 44 of the side 23 of the drawer 22. As seen in FIG. 8, as the drawer 22 is first opened, the cross bar 32 portion of the front face of the cabinet 34 bears down on the front ramp 26 of the engaging arm 20. The ramp 26 rides along the cross bar 32, flexing the engaging arm 20 further and further downwardly as the drawer 22 is pulled out, until the trough 30 reaches the cross bar 32. At that point, the engaging arm 20 snaps back and receives the cross bar 32 within the trough 30 (as seen in FIG. 3). Now, the rear vertical surface of the trough 30 abuts th...
FIGS. FIGS are in the business of, among other things, producing, directing, and editing motion pictures; FIGS intends on forming an entity (partnership or corporation) tentatively named "Top Secret Surf Productions".
FIGS. 1 - 3 show the simulation results of witness-bunches with a maximum length, which create an accelerating wakefield of the plateau type, for different values of the transformer ratio. Due to the finiteness and continuity of the field, it can be understood that the transformer ratio is closely related to the distance between the witness-bunch and the driver-bunch. This is clearly seen from the data presented in these figures. Hence, it can be noted that with an increase in the transformer ratio, the maximum length of the studied witness-bunches should decrease. For comparison, let's look at the situation with a very long bunch-driver and a short bunch-witness (Fig. 4). It can be seen that under these conditions it is possible to achieve a significant transformer ratio. Figure 5: Dependence of the transformer ratio and the maximum length of the witness-bunch, depending on the distance between the witness-bunch and the driver- bunch. The driver length is 0.06 times the bubble length. Figure 6: Dependence of the transformer ratio and the maximum length of the witness- bunch, depending on the distance between the witness-bunch and the driver-bunch. The driver length is 0.23 times the bubble length. Figure 7: Dependence of the transformer ratio and the maximum length of the witness-bunch, depending on the distance between the witness-bunch and the driver- bunch. The driver length is 0.33 times the bubble length. 13/18 To confirm this assumption, a series of numerical simulations were carried out for three different bunch-drivers (Figs. 5-7). For different values of the transformer ratios, the witness-bunches with the maximum length were built. From the data obtained, it can be seen that, indeed, there is an inverse relationship between the value of the transformer ratio and the value of the maximum length of the witness-bunch. Also, it can be noted that with an increase in the size of the driver-bunch, the value of the maximum length of the witness-bunch increases, for the same values of the transformer ratio. The formation of a longitudinal accelerating field for witness bunches of various lengths is investigated. Very long witness bunches were obtained, which form a self-consistent accelerating field, such as a plateau. For this system, the assumption about the local influence of small sections of the witness-bunch on the longitudinal accelerating field was confirmed.
FIGS. 5 and 6 give the objective and subjective metrics for the lobby scenario. The objective metrics indicate that socially normativeness leads to a penalty in having to take longer and less smooth paths with more maneuvers. For the sociable behavior, we observe even more maneuvers which is expected for a robot serving cocktails at a party while respecting relations between persons. Also as expected, the rude behavior results in the most efficient paths. The results in the subjective metrics reinforce the message from the objective counterparts in that social normativeness results in minimal number of intrusions into people’s spaces while being rude leads to the opposite. The sociable behavior gets the robot close to people (large numbers of intrusions into personal and intimite spaces in Fig. 6), while minimizing the number of social relation disturbances. People in goups are correctly approached without breaking social ties at the expensive of more maneuvers as observed in the decreased smoothness metric in Fig. 5.
FIGS. 1 and 7 show head 32 in operation. Head 32 is shown in close proximity to submerged elongate object 68. The gripping operation of claws 44 is actuated by hydraulic rams 46. Head frame 40 and claws 44 are held against elongate object 68 by actuation of boom Section 12d. Head frame 40 is oriented so as to engage V-shaped bracket 66 against the surface of submerged elongate object 68 by the operation of hydraulic cylinder 41 which pivots head 38 about a generally horizontal axis on hinge 36. Hydraulic motor 38 rotates head 32 about the longitudinal axis of shaft 38a. As seen in FIG. 15, a remote operator 70, who may be situated on barge 34, controls the articulation of articulated boom 10 and head 32 by means of remote controls 72, which, as illustrated, may be an opposed pair of articulated pistol grips. Remote operator 70 monitors a real time display (not shown) of the video image captured by video camera 48. Remote operator 70 may also monitor a real time computer simulation 74 of the deployment status of articulated boom 10 deployed beneath barge 34. Such spacial orientation status information about the deployment of articulated boom 10, combined with the video real time image from video camera 48, provides the information which is of assistance to the remote operator 70. Inputs required to produce the real time computer simulation 74 may be provided by rotary position transducers known in the art. They may be mounted on the boom tower, at the tower to boom joint, and at boom joints 76a, 76b, 76c, and 76d (see FIGS. 3 and 15), and at the rotation, tilt and grip articulation locations 36 (see FIG. 6), 62 for head 32 (see FIG. 7). The position transducers provide a signal which is proportional to relative movement, both between 0 and 10 volts, to an analog-to-digital converter, and thence to a remote computing device, as for example a computer located on barge 34. The operation of the boom tower is better described below. Rotary position transducers 87 as shown in FIG. 10 are mounted at the boom joints and may comprise a rotatable gear at the transducer on one boom section and a non-rotatable sprocket mounted to the hinge pin 14 connecting the two boom sections. Pin 14 rotates with one boom section, while the other pinned section of boom is freely rotatable on the hinge pin. The gear and sprocket are connected by a drive chain which rotates cooperatively as the hinge pin is rotated during relative movement of the boom sections. The enabling software of the ...
FIGS. 4, 5 and 6 show views of the cap of the above embodiment.
FIGS. 7, 8 and 9 show views of the motor mount of the above embodiment.
