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A shaft of selected material and of a given desired nominal diameter corresponding to nominal desired shaft extension diameter for a particular motor is cut and then treated with optional operations such as chamfering and washing; grinding; machining of flats; and phosphatizing to inhibit rust. A first accessory member is assembled in a predetermined position by heat shrinking on the shaft; and a rotor body is assembled with the shaft. A second accessory member is also assembled by heat shrinking. For ball bearing applications, concenntric journals are turned on accessory members for the inner races of bearings after the accessory members have been assembled with shaft. The inner races of ball bearings are lightly pressed onto the journals, and rotors, end frames, and stator are assembled. The concentric journals permit press fitting of ball bearings without substantially exceeding 0.0005 of an inch press fit and thus avoid damage to the bearings.
Shaft portions are stressed and maintained in a stressed condition so as to increase the stiffness of the rotor system and thereby increase the rotor system resonant frequency. Aluminum collars that conform to the shaft surface are preferably used. These collars establish a more thorough and uniformly stressed condition of the shaft.
1. A dynamoelectric machine including a stator, a pair of bearing units, a shaft supported by the bearing units and having two ends; a rotor body having first and second ends secured to a portion of the shaft between the ends of the shaft; and a pair of accessory members positioned on the shaft and each extending axially toward one end of the shaft from axial locations along the shaft at least substantially proximate to the first end of the rotor body, to other axial locations along the shaft; said accessory members each having a surface region at the end thereof nearest a respective end of the shaft disposed generally adjacent to a plane that is normal to the axis of the shaft and in proximity to an end face of the respective bearing unit supporting the shaft; said shaft being in a substantially permanently stressed condition at least along the surface regions thereof that extend from an axial position at least substantially proximate to the ends of the rotor body to the other axial locations.
2. A rotor assembly comprising a shaft; a rotor body secured to the shaft and located between the ends thereof; a first collar secured to the shaft with an interference fit and located between a first end of the shaft and a first end of the rotor body; a second collar secured to the shaft with an interference fit and located between a second end of the shaft and a second end of the rotor body; said collars having machined bearing seats which are concentric with the shaft; a first ball bearing unit secured to the first collar; and a second ball bearing unit secured to the second collar; said first and second ball bearing units having an interference fit with a bearing seat of not substantially more than about 0.0005 of an inch.
3. The rotor assembly of claim 2 wherein the first and second collars are secured to said shaft with a shrink fit.
4. A dynamoelectric machine including a stator, at least one ball bearing unit, a shaft supported by the at least one ball bearing unit at first end thereof; a rotor body having first and second ends secured to a portion of the shaft between the ends of the shaft; and at least one accessory member positioned on the shaft and extending axially toward the first end of the shaft from a first axial location along the shaft between the first end of the rotor body and the first end of the shaft; said at least one accessory member having a machined bearing seat which is concentric with the shaft, said accessory member being secured to the shaft by an interference fit, and said at least one ball bearing being seated on said at least one accessory member, said at least one ball bearing having an interference fit with the bearing seat of not substantially more than about 0.0005 of an inch.
5. A rotor assembly for a dynamoelectric machine comprising a shaft having two ends; a rotor body, having first and second ends, secured to a portion of the shaft between the ends thereof; and two accessory members positioned on the shaft and each extending axially toward an end of the shaft from axial locations along the shaft that are at least substantially proximate to an end of the rotor body, to other axial locations along the shaft; said accessory members each having a surface region at the end thereof nearest an end of the shaft for disposition generally adjacent to a plane normal to the axis of the shaft and closely proximate to an end face of a bearing unit for supporting a shaft end; said shaft being in a substantially permanently stressed condition at least along the surface regions thereof that extend from an axial position proximate to the ends of the rotor body to the other axial locations.
6. The rotor assembly of claim 5 wherein the accessory members are steel collars.
7. The rotor assembly of claim 5 wherein the accessory members are secured to said shaft with an interference fit.
8. The rotor assembly of claim 7 wherein the accessory members are secured to said shaft with a shrink fit.
9. The rotor assembly of claim 8 wherein the accessory members are aluminum collars.
10. The rotor assembly of claim 8 wherein each accessory member establishes a seat for a ball bearing unit.
11. The rotor assembly of claim 10 wherein each accessory member is an aluminum collar.
12. A dynamoelectric machine including a stationary stator structure, a pair of bearing units supported by the stationary stator structure, a rotatable shaft having first and second ends supported for rotation by the bearing units and having two ends; a rotor body secured to the shaft for rotation therewith, with the rotor body having first and second ends spaced from the first and second shaft ends so that the rotor body is secured to the shaft between the ends of the shaft; and a pair of accessory members positioned on the shaft with each extending, from closely proximate to the rotor body, axially toward a respective end of the shaft; said accessory members each having a surface region at the end thereof nearest each respective end of the shaft that is disposed adjacent to a plane normal to the shaft axis and that is disposed in close proximity to an end face of the respective bearing unit supporting the shaft; said shaft being in a substantially permanently stressed condition at least along the surface regions thereof that extend from an axial position at least substantially proximate to the ends of the rotor body to the above-mentioned planes in close proximity to each bearing end face, with the stressed condition bearing maintained by the accessory members.
13. A rotor assembly comprising a shaft; a rotor body secured to the shaft and located between the ends thereof; a first collar secured to the shaft with an interference fit and located between a first end of the shaft and a first end of the rotor body, said first collar having a first end disposed closely proximate to the first end of the rotor body; a second collar secured to the shaft with an interference fit and located between a second end of the shaft and a second end of the rotor body, said second collar having a first end disposed closely proximate to the second end of the rotor body; said collars having machined bearing seats concentric with the shaft at the second ends thereof which are also most proximate to each respective shaft end; a first ball bearing unit secured to the first collar on the bearing seat thereof; and a second ball bearing unit secured to the second collar on the bearing seat thereof; said first and second ball bearing units having an interference fit with the respective bearing seats of not substantially more than about 0.0005 of an inch; and wherein said first and second collars constitute means for strengthening the shaft between the ends of the rotor body and bearings whereby shafts of predetermined relatively small diameters may be utilized.
14. A rotor assembly for a dynamoelectric machine comprising a shaft having two ends; two bearing units; a rotor body, having first and second ends, secured to a portion of the shaft between the ends thereof; and two accessory members positioned on the shaft and each extending axially toward an end of the shaft from locations substantially proximate to an end of the rotor body, to other respective axial locations more proximate to an end of the shaft; said accessory members each having a surface region at the end thereof nearest the respective shaft end disposed adjacent to a plane normal to the shaft axis and closely proximate to an end face of a respective bearing unit; said shaft being in a permanently stressed condition along the surface regions thereof that extend from proximate to the rotor body ends to the bearing units.
This application is a division of my now co-pending application Ser. No. 554,454 which was filed Mar. 3, 1975 and which issued Nov. 9, 1976 as U.S. Pat. No. 3,990,191. The entire disclosure of said application is incorporated herein by reference.
The present invention relates generally to rotatable dynamoelectric machines, and, more particularly, to rotatable assemblies usable therein.
Shafts of rotary dynamoelectric machines, such as fractional horsepower electric motors of both ball and sleeve bearing types, often are machined from shaft stock that initially is of a relatively large diameter. Extensive machining of large diameter shaft stock often has been required, even though one or more external shaft extensions are required to be of a small diameter. In some cases, large diameter stock is used so that intermediate diameter seats, and large diameter shoulders may be provided thereon for ball bearings. Moreover, in the case of shafts designed to accommodate ball bearings, a groove may be required adjacent the ball bearing seat to provide clearance for the inner race of the bearing.
Some sleeve bearing motors are provided with straight shafts, i.e., shoulders, steps, etc. are not normally provided. However, for other sleeve bearing motors, it has sometimes been necessary to provide enlarged shafts in order to increase the stiffness thereof, and machine the shaft extensions to a smaller, acceptable size. This usually is done in order to avoid vibration and noise problems when either the horsepower of a motor or the distance between bearings is increased.
Although the above problems may be encountered with different motors having different diameter shaft extensions, the problem as it pertains to motors having one-half inch (12.7 mm) diameter shaft extensions will now be set forth in more detail.
For some ball bearing motors with a one-half inch diameter shaft extension, it has been necessary to machine the shaft from three-quarter inch (19 mm) diameter stock. In these cases, multiple machining operations have been performed on each end of the shaft to provide a central shaft portion that remained three-quarter inches (19 mm) in diameter, machined seats for a ball bearing [e.g., for a ball bearing with an inner race diameter of about 0.590 inch (15 mm)]; and one-half inch (12.7 mm) shaft extensions.
On the other hand, for some sleeve bearing type motors that required a nominal one-half inch (12.7 mm) shaft extension, one-half inch diameter ends have been machined on a five-eights inch (15.9 mm) diameter shaft to provide bearing journals and one or more shaft extensions of the desired one-half inch (12.7 mm) size. Five-eights inch (15.9 mm) diameter shaft material has been used so that the unsupported length of the shaft between the bearings would be stiffer and have less tendency to bend or whip during operation and thus generate less noise (as compared to a one-half inch (12.7 mm) straight shaft). As will be understood, such noise is objectionable because it may be transmitted to the environment directly, or through the structural mechanisms that are interconnected with either the motor shaft or the motor shell. In other one-half inch (12.7 mm) shaft, sleeve bearing motor applications, the axial length of the rotor, and unsupported shaft length have been sufficiently small that one-half inch (12.7 mm) shaft material has been used with no particular problem.
In large volume production operations, the need to produce different shafts because of different rotor lengths or bearing types increases manufacturing costs not only due to extra material usage and machining operations; but also because of extra capital investment for machining equipment and because of the expense associated with maintaining different types of production equipment.
Still another expense associated with the use of differently sized shafts is more directly related to the manufacture of the rotor body. It should be recalled that squirrel cage rotors for induction motors are made up of laminations that have a centrally located bore for accommodating the shaft. All of the above specifically described motors typically would have rotors with a common outer diameter. However, laminations for each different motor would have a shaft receiving bore of one-half inch (12.7 mm), five-eights inch (15.9 mm), or three-quarters inch (19 mm), depending on the diameter of the central portion of the shaft.
It should now be understood that it would be extremely desirable to provide new and improved rotor arrangements that can be utilized to overcome any one or more of the above-mentioned problems.
Accordingly, it is a general object of the present invention to provide improved rotor arrangements, as well as dynamoelectric machines including such rotor arrangements, so that the above-identified and other problems may be overcome.
It is a more specific object of the present invention to provide a new and improved rotor assembly whereby motors that require a given single diameter shaft extension may utilize straight shafts of a minimum diameter, even for ball bearing or long rotor applications that have previously required stepped or otherwise machined shafts.
It is a more specific object of the present invention to provide a new and improved rotor assembly wherein accessory means, assembled on a straight shaft so as to form part of the rotor assembly, satisfy the previous need for stepped shafts.
In carrying out the above and other objects of the present invention in one form thereof, shaft material of a given desired nominal diameter corresponding to the nominal desired shaft extension diameter for a particular motor is selected.
Thereafter, shaft blanks are cut and, when desired, optional operations such as chamfering and washing of the shaft blank are performed. The shaft blank may then be ground, at least one flat may be machined thereon, and a rust inhibiting treatment (e.g., phosphatizing) is performed. A first accessory member is assembled in a predetermined position on the shaft (preferably by heat shrinking), a rotor body is assembled with the shaft, and a second accessory member is assembled on the shaft (again, preferably, by heat shrinking).
If the rotor assembly is to be utilized in a sleeve bearing application, thrust members preferably are assembled with the shaft, and thereafter the rotor assembly, stator, and end frames of the motor are assembled. On the other hand, if the rotor is to be utilized in a ball bearing application, concentric journals are finish turned on the accessory members for the inner races of such bearings after the second accessory member has been assembled with the shaft. The inner races of the ball bearings are pressed onto the journals and the rotor is assembled with parts such as end frames and a stator to form a complete motor. The concentric journals permit ball bearings to be press fit thereon without substantially exceeding a 0.0005 of an inch press fit and thus causing damage to the bearing units.
In the case of rotor assemblies that are to be used for sleeve bearing motors (and optionally for some that are to be used for ball bearing motors), it is preferable that the shaft portions which extend from a location proximate to the face of the rotor body to a location proximate to a bearing supported portion thereof are stressed, and this stressed condition of the shaft is maintained. The stressed condition of the shaft is maintained even after assembly of the motor has been completed, and this increases the stiffness of the rotor system and therefore also increases the resonant frequency of the rotor system.
Apparatus for manufacturing assemblies embodying the invention may include means for maintaining a desired perpendicular relationship between a first accessory member and a shaft while the two are being assembled together. The same or other apparatus also preferably includes means for establishing a first dimensional relationship between the face of a rotor body and the first accessory member while the rotor body is being assembled to the shaft. The same or other apparatus also preferably would be utilized to establish and maintain a desired dimensional relationship between the first and second accessory members as the second accessory member is assembled on the shaft.
When carrying out the invention in one preferred form, accessory members are produced from aluminum or aluminum alloy, heated to a temperature in a predetermined temperature range such as 400� to 700� F. (204� C. to 371� C.), slipped onto a steel shaft, and thereafter cooled so that the accessory members will shrink about the shaft as they cool to ambient, and tightly grip and stress the surface of the shaft. It is preferable that a material such as aluminum be selected so that it will conform to the shaft surface and establish a more thorough and uniformly stressed condition of the shaft. However, steel accessory members may be used although my preferred approach provides results that are believed to be generally unexpected and surprisingly advantageous. The auxiliary members extend from a location proximate to the end face of a rotor body, to a position proximate to the portion of the shaft that is to be supported by a bearing. Furthermore, the auxiliary members are each shrunk with a predetermined interference fit, and the members may include a bearing surface. In one form, such surface is a face against which a thrust runner may bear. In another form, such surface is a seat for a ball bearing.
When a ball bearing seat is provided, a ball bearing inner race is pressed onto the seat. In yet another form of the invention, collars are used that provide a shoulder and seat for a ball bearing without stressing the entire unsupported span of shaft between the rotor body and bearing location. When constructions according to the above-described forms are provided, it is preferably to establish sufficiently tight fits that the collars are not dislodged during subsequent handling or manufacturing operations.
The subject matter which I regard as my invention is particularly pointed out and distinctly claimed in the concluding portion of this specification. The invention itself, however, together with further objects and advantages thereof, may be better understood by reference to the following description taken in conjunction with the accompanying drawings in which like reference numerals have been used to identify the same parts, and in which:
FIG. 1 is a partially exploded perspective view (with parts broken away and other parts removed) of a motor that includes structures embodying the present invention in one form thereof, such structures having been made by using apparatus disclosed herein;
FIGS. 2 and 3 are schematic representations of prior constructions;
FIG. 4 is a view in elevation, with parts removed and parts in phantom, of part of the motor of FIG. 1;
FIG. 5 is a sectional view (to a somewhat enlarged scale) of one of the parts shown in FIGS. 1 and 4;
FIG. 6 is a side elevation, with parts in phantom and parts broken away, of another construction that has been used long prior to the present invention;
FIG. 7 is a side elevation, with parts in section, and parts removed, of a modified structure that may be used in motors embodying the invention in another form;
FIG. 8 is a view (to an enlarged scale), of a rotor assembly that embodies the invention in yet another form;
FIG. 9 is an enlarged perspective view of one of the parts illustrated in FIG. 7;
FIG. 10 is a flow chart of steps that may be followed when making assemblies embodying the present invention in one form thereof;
FIGS. 11, 12 and 13 are schematic representations of apparatus useful when carrying out the invention;
FIG. 14 is a view taken along the lines 14--14 in FIG. 13; and
FIG. 15 is a curve which is a plot of resonant frequency versus shaft deflection for prior constructions and for constructions that embody the invention.
In FIG. 1, an electric motor 20 has been illustrated to exemplify structures, embodying the invention in one form thereof, that may be made as taught herein, with or without the apparatus disclosed herein.
The motor 20 includes a conventional shell or housing 21 which accommodates a stator assembly 22, and also includes a pair of end frames or shields 23, 24, and a rotor assembly 26. Means for mounting motor 20 to a base, appliance, or other structure have not been shown, but it will be understood by persons skilled in the art that mounting rings may be placed on a hub 52 carried by each end shield 23, 24, and that such rings may then be disposed in any suitable cradle or base member. Alternatively, motor 20 may be provided with axially projecting studs on either of the end frames, or not shown clamp bolts (which pass through end frame holes 28, 29, 31, 32) may be used for motor mounting purposes. The description presented herein of various approaches for mounting motor 20 is for purposes of description only and any other desired mounting approach may be followed.
Also for purposes of description rather than limitation, it is noted that the stator assembly 22 includes a four-pole shaded salient pole magnetic iron core 33 and four concentrated coil excitation windings 34 (it being noted that one of these has been broken away for purposes of illustration). Moreover, the end frames 23, 24 have been shown as two aluminum die cast members that are identical to one another, even though motor 20 is a single shaft extension motor. Cover 36 is provided with a central shaft admitting aperture 37 but the corresponding cover for end frame 23 is not provided with a similar aperture.
As will be understood, the end frames 23, 24 are each provided with a seat which accommodates a bearing; and the covers 23, 24 in fact each have a sleeve bearing 38 assembled therewith. However, it also will be understood that the bearing hubs of the end frames used in a motor intended for use in a different application may seat the outer race of a ball bearing.
The rotor assembly 26 includes a rotor body 39 which comprises a laminated magnetic core and cast aluminum conductors which are short circuited with one another at each end by cast aluminum end rings 41, all as will be understood. The rotor body 39 may be secured to a shaft 42 by heat shrinking or by other means, e.g., by an adhesive, by a mechanical press fit, mechanical deformation of end laminations against the shaft, and so forth. Rotor assembly 26 includes a thrust runner 43 which is normally pressed onto shaft 42, but which is removed therefrom in FIG. 1 for purposes of illustration. Thrust runner 43 is made of graphite impregnated nylon, e.g., "Nylation" as sold by the Polymer Corporation, but any other suitable low friction material may be used.
Also included, as part of rotor assembly 26, are two accessory members which are heat shrunk onto shaft 42 so as to stress at least that portion of the shaft material along the surface of the shaft. One of these members is shown in FIG. 1 as an aluminum collar 47. The portion of the shaft 42 that extends from an axial location on the shaft that is proximate to the face 44 of rotor body 39 to an axial location that is proximate to the end face 46 of collar 47 is held continuously in compression during all normal temperature conditions, due to the hoop tension in collar 47.
Arrangements embodying the invention thus far described provide advantageous results in terms of motor generated noise during operation of motor 20. These improved results are presently believed to be due to the stressed condition of the shaft (as just described) at each end of rotor body 39; and also perhaps due to some increase in shaft strength due to the mass of collar 47. Since these beliefs and present understanding are discussed in more detail hereinbelow, it is only noted further at this point that collars 47 and 48 (See FIG. 4) were machined from 2011-T3 aluminum, that shaft 42 was made from cold drawn low carbon steel; (e.g., one having an AISI designation of C1211 to C1215) and that collars 47, 48 were heated to a temperature in the predetermined temperature range of 400� F. to 700� F. (204� C. to 375� C.) before they were relatively slipped along shaft 42 (while the shaft was held at room ambient temperature of about 21� C.) to predetermined axial locations, and allowed to shrink against the shaft at such locations.
The degree to which the collars must be heated may vary, depending on the material from which the collars are made, the diameter of the shaft, and the bore diameter of the collars. It is preferable to size the bore of collars (that are to fit on one-half inch or 12.7 mm shafts) so that there would be an interference fit on the shaft of from about 0.0009 inch to 0.0020" (0.0228 mm to 0.0508 mm). More specifically, I have obtained entirely satisfactory results when the collar bore diameter has been machined to a tolerance of 0.4987 inch (12.67 mm) maximum and 0.4980 inch (12.65 mm) minimum; and the shaft diameter has been held to a dimension within the range of from 0.4995 inch (12.69 mm) to 0.5000 inch (12.7 mm).
Exact dimensions have now been described for the purpose of providing a full and complete teaching, but it should be understood that departures could be made therefrom while still utilizing the invention. When the various parts are made of the materials described hereinabove and dimensioned as noted, the collars 47, 48 (after cooling to room ambient) can be moved along shaft 42 only by applying a push-off force of from about 1,500 to about 3,500 pounds (680 kg. to 1,590 kg.).
When the shaft stress is to be caused by the shrinking of collars thereon (or by the expansion of a previously cooled shaft against the bore of a room ambient collar), the amount of heating or cooling of one part relative to the other may be readily calculated by using the well known relationship: (ΔT) (D)(k)=ΔD; where k is the coefficient of thermal expansion of the material that is being heated or cooled, ΔT is the temperature difference (or gradient) under consideration, and ΔD is the change in diameter due to the change in temperature.
With reference now to FIGS. 1 and 4, it is noted that, after final assembly of the motor 20, the shaft 42 is received in a pair of sleeve bearings 38, 51 which are carried by hubs 52, 53 of end frames 24, 23 respectively. Also shown in FIG. 4 are parts of thrust systems which include thrust plates 54, 56, and the thrust runners 43, 57. It will be understood that the thrust runners have both a lubricant slinger portion and a thrust washer portion. Details of arrangements such as these are now available elsewhere (e.g., in commonly owned J. Stokke et al U.S. Pat. No. 3,793,543, which issued Feb. 19, 1954 and the entire disclosure of which is incorporated herein by reference), and detailed discussions pertaining to the subject matter disclosed in that patent are not repeated herein.
With reference to FIG. 4, the spatial relationships between the shaft 42, collars 47, 48, rotor body 39, and bearings 38, 51 should be noted. It will be appreciated that the rotor body 39 is secured to the shaft 42 between first and second ends 58, 59 thereof. Accessory members (in the form of collars 47, 48) are positioned on the shaft so that they each extend axially from a first axial location on the shaft (adjacent a face 44 or 61 of the rotor body) toward an end of the shaft. The collars thus each extend to a respective second or third axial location on the shaft. Each collar has a surface region (e.g., face 46 of collar 47 against which the thrust runner 43 abuts) that is disposed adjacent the respective second (or third) axial location.
More specifically, such surface region is located so that it may be disposed closely proximate to a plane that is normal to the axis of the shaft 42 and passes through (or closely adjacent to) bearing means that support the shaft. For example, and as can be quickly ascertained from a review of FIG. 4, the face 46 is closely proximate to a plane represented by the dashed line 63. It is again emphasized that the shaft 42 is in a compressed (and therefore stressed) condition along the surface region that is grasped by the collar 47. In order to provide a frame of reference for "closely proximate", it is noted that the normal spacing between the face 46 and the end of the hub 52 (and therefore the bearing 38) is only on the order of about one-eighth of an inch (3.17 mm) for motor 20.
FIGS. 2 and 3 illustrate constructions that have been used long prior to the present invention. More specifically, FIG. 2 illustrates an arrangement wherein a rotor body 66 of conventional construction is heat shrunk onto a straight steel shaft 67 and two aluminum thrust collars 68, 69 (with bore dimensions as set out above for collar 47) are heat shrunk onto the shaft 67. The faces of the collars 68, 69 have been used to provide faces against which thrust runners substantially identical to the thrust runners 43 were pressed. FIG. 3 shows yet another prior approach wherein a rotor body 71 was heat shrunk onto steel shaft 72. In this approach, aluminum collars 73, 74 were heat shrunk at predetermined positions onto the shaft 72 and provided faces against which thrust runners could be positioned prior to final assembly of a motor.
The straight shaft of FIG. 2 was one-half an inch, while the stepped shaft of FIG. 3 was five-eighths inch diameter in the central portion thereof, with one-half inch shaft extensions. The arrangement shown in FIG. 2 has been, and continues to be, utilized when the axial length of the rotor body 56 is relatively small. The approach represented by FIG. 3 was used when the rotor body was relatively long with an increased shaft length between bearings, and the enlarged portion of the shaft provided more rigidity as compared to a one-half inch straight shaft for the same application. It will be appreciated from a comparison of FIGS. 2 and 3 that a construction according to FIG. 3 would be more expensive to manufacture. This is not only because of the stepped shaft, but also because the laminations for rotor body 71 have a different shaft bore diameter than the laminations for rotor body 66.
In FIG. 5, an enlarged sectional view of the collar 47 has been illustrated. It will be noted that collar 47 may be quickly manufactured by boring a piece of round stock and then cutting a step therein with conventional machined tools.
FIG. 6 illustrates a prior art construction for a ball bearing motor wherein a rotor body 76 is heat shrunk onto a portion 77 of a stepped shaft 78. The shaft portion 77 was three-quarters of an inch (19 mm) in diameter. Portions 79 and 81 of shaft 78 were machined to provide a one-half inch diameter shaft extension; and approximately 15 mm diameter seats 82, 83 were machined so that the inner races of commercially available 15 mm inner diameter ball bearings 87 could be pressed against the shoulders 84, 86.
Reference is now made to FIG. 7 for a description of another embodiment of the present invention. More specifically, the rotor assembly 88 there shown may be used in lieu of the rotor assembly shown in FIG. 6 at a substantial savings in expense. For example, the rotor body 89 was made with laminations having the same shaft bore size as those used for the rotor bodies shown in FIGS. 2 and 4. Accessory members, illustrated as collars 91 and shown in more detail in FIG. 9, were heat shrunk onto a one-half inch diameter straight shaft 92. The collars 91 were made from the same materials, and processed in substantially the same way as the collars illustrated in FIG. 4; except that bearing seats 93 were machined on each collar so that the inner race of a bearing 87 could be pressed thereon in abutting relation with a shoulder or face 94. Fully satisfactory results have been obtained when the seats 93 were turned (while the collars are on shaft 92) to a diameter of from 0.5905 to 0.5908 inches and a bearing having a nominal inner diameter of 15 mm (0.5903 to 0.5906 inches) was pressed thereon. The precise axial location of the bearing seats 93 along shaft 92 are determined by precisely locating collars 91 on the shaft, all as is described in more detail hereinafter.
In FIG. 8, still another embodiment of the present invention is illustrated wherein a rotor assembly 96 includes a rotor body 97, a one-half inch diameter straight shaft 98, a pulley end collar 99 and an opposite pulley end collar 101. The collars 99 and 101 are formed of the same aluminum materials as the collars described hereinabove, and extend between axial positions substantially determined by rotor body end faces 102, 103, and planes 104, 106 (which are substantially normal to the axis of shaft 98 and closely adjacent to axial ends of the bearings 87).
It should now be appreciated that the collars 99 and 101 tightly grip and continuously stress the shaft 98 in predetermined regions thereof, substantially in the same manner and for the same reasons that collars 47 and 48 grip the shaft 42 (see FIG. 4). The collars 99, 101, and rotor body 97 are assembled with shaft 98 in generally the same manner as has been described above in connection with the other illustrated embodiments of my invention.
FIG. 10 is a flow chart of steps for one process that may be followed when making the illustrated embodiments. At the outset, it is noted that specific materials and nominal dimensions of parts have been identified in FIG. 10 only for purposes of disclosure and not necessarily for reasons of limitation. The referred to process includes selecting a desired size and type of material for use in making shafts. Thereafter, shafts of the desired length are cut from the stock material and chamfered at the ends. Then, in sequence, the shafts are straightened and washed, and ground to establish a desired concentricity; flats are provided on the shaft extensions (when desired); and a rust inhibiting treatment (such as phosphatizing) is performed. Collars which have previously been manufactured are then heated and shrunk onto the shaft, after which a rotor body is heated and shrunk onto the shaft. The second collar is then heated and shrunk onto the shaft.
If the ultimately resulting rotor assembly is to be utilized in a sleeve bearing motor, the appropriate collars will have been selected, and the rotor subassembly has thrust runners assembled therewith. However, in the case of rotor assemblies intended for ball bearing applications, the first and second collars are finish turned to provide a bearing seat or journal, and ball bearings are press-fit onto the journals before the resultant rotor assembly is advanced to final motor assembly.
In FIGS. 11 through 14 I have illustrated apparatus of one simplified and useful type which may be utilized to produce preferred embodiments of the invention. FIG. 11 schematically depicts a portion of the apparatus which is utilized during the assembly of firt collar 91 to shaft 92 when the assembly of FIG. 7 is to be constructed. Briefly, the fixture of FIG. 11 includes a base plate 107 with a guide ring 108 fastened thereto and a bottom plate 110 fastened thereto. Slidably received by the bottom plate is a stop block 111. Stop blocks of various thicknesses may be used in the fixture so that the axial distance between a top surface 112 thereof, and the surface 113 of the base may be varied in any predetermined manner.
Also included in the fixture of FIG. 11 are means for guiding a shaft during the assembly operation and for insuring that the shaft is maintained perpendicular relative to the surface 113. Once such means for guiding is illustrated in the form of conventional vee-blocks 114 and a support 115 for the vee-blocks. The collar 91, after being heated to a predetermined range (e.g., 400 to 700 F.), is positioned with a face 94 thereof engaging the surface 113, and with the collar held in an aligned position by a guide ring 108. Thereafter, the shaft 92 is hand placed through the bore of the collar until the shaft end 116 comes to rest against stop block 111. A vee-block 114 is used to maintain the shaft 92 in centered relation with the collar 91 until the shaft has been seated against surface 112 of the stop block 111. After a very short interval of time (e.g., 1 or 2 seconds), the collar 91 will have cooled sufficiently to be tightly locked to the shaft 92 whereupon the shaft and collar are positioned in a fixture that is schematically depicted by FIG. 12.
The fixture 118 includes a base 119 which is provided with a hole 121 that will accept the shaft 92 with a slip fit, and insure that the shaft 92 is held perpendicular to a surface 122 of the fixture. Projecting from surface 122 is a removable spacer ring 123 which is selected to be of an axial length corresponding to a predetermined axial dimension that is to be established and maintained between the face 94 of collar 91 and face 124 of a rotor body 89.
Having selected a ring 123 having a desired height, and positioned it (or suitably fastened it) relative to the fixture 118, the shaft 92 with collar 91 shrunk thereon is positioned in the fixture. Thereafter, a preheated rotor body 89 is slipped down shaft 92 until the face 124 of the rotor body seats against the spacer ring 123. The operation just described may readily be accomplished by hand, so long as caution is used and the preheated rotor body is handled with gloves or tongs.
FIG. 13 illustrates yet another part of the apparatus which is utilized to position a second heated collar 91 so that a face 94 thereof will be a predetermined desired axial distance from the face 94 of a collar that is resting against surface 126 of a machine base 127. The apparatus of FIG. 13 includes not shown supporting structure which supports and upper frame member 128 in fixed relation to base 127. Fastened to upper frame member 128 is a pneumatic cylinder 129 which is thus held a predetermined fixed distance from the upper surface 126 of the machine base 127.
A rod 131, which is driven by the cylinder 129, is permitted to travel (upon actuation of the cylinder) until a stop nut 132 carried on the free end thereof bears against a spacer block 133. The actual travel of piston rod 131 thus depends on the height of the particular spacer block 133 which has been selected. It will be understood that a spacer block 133 having a relatively small axial dimension will permit a relatively long rod travel. The apparatus of FIG. 13, in actual practice, is inclined so that the axis of piston rod 131 is disposed approximately 45� to a horizontal plane. With the piston 131 completely retracted, the shaft 92 (having the rotor body 89 and lower collar 91 fastened thereto) is positioned in the fixture with the rotor body 89 held in centered relation by a large vee-block 136. Moreover, the bearing seat 93 of the lower collar 91 is seated against a concentric guide surface 137 which is carried by the machine base. The vee-block and guide seat 137 cooperate to hold the shaft 92 perpendicular to the surface 126 of the machine base and in alignment with the piston rod 131.
A heated collar 91 is then snapped into a collar holder 135 and cylinder 129 is actuated to slip the upper collar 91 to a desired final position along shaft 92 so that the faces 94 of the collars 91 are a predetermined desired distance apart. it should now be understood that the selection of a spacer block 133 (or plurality of the same) having a desired total axial height will insure that the upper spacer 91 is moved to a precise axial location along shaft 92 when the surface 94 of the lower collar is seated against the surface 126 of the base member. Since the preheated upper collar 91 will loosely slide along the shaft 92 while it is in a heated condition, it is necessary to provide some means for holding the collar to insure that it does not travel further than desired toward the end face 138 of rotor body 89. Various means may be provided to frictionally engage the surface 93 of the collar 91.
FIG. 14 clearly reveals that the collar holder is formed with a major portion thereof to conform to the configuration of collar surface 93. The collar holder also has seated therein a pair of commercially available spring plunger pins 139. For example, the pins 139 were manufactured by the Vlier Engineering Corporation, 8900 Santa Monica Boulevard, Los Angeles, California. The spring plunger pins are so located that they may be depressed to permit seating of collar 93 against the collar holder. Then, as the center of the collar moves beyond a line passing through the two plunger pins, the plungers move outwardly to frictionally grasp the collar. After a collar is shrunk on the shaft, the holder 135 withdraws and the pins slide along the collar. Holder 135 should be made of a mineral filled phenolic material or other suitable material to minimize heat loss from the heated collars.
The assembly of a collar with shaft 92 in the manner just described establishes a permanently stressed condition along first and second sections of the shaft which are substantially co-extensive with the collars. In the case of the structures shown in FIGS. 4 and 8, a permanently stressed condition is established along first and second sections of the shaft. The first such section extends between first and second axial shaft locations; and the second such section extends between third and fourth axial locations. As will be appreciated from a review of FIGS. 4 and 8, first and second faces of the rotor body are disposed substantially at the second and third axial locations, respectively. Moreover, after final assembly of a motor that includes the structure of FIGS. 4 and 8, the first and fourth axial shaft locations will be proximate to an end of a bearing unit.
In the case of ball bearing units 87 (see FIG. 8), the first and second locations are nearer to the outboard faces of ends of the bearing units and in the vicinity of planes 104, 106. However, in the case of sleeve bearing units 38, 51 (see FIG. 4), the first and fourth axial shaft locations are more proximate to the imboard axial ends or faces of the bearing units and in the vicinity of planes as indicated for example at 63.
From tests that have now been performed on motors embodying the invention as illustrated herein, I have concluded that substantial savings can be realized in practice by using one-half inch straight shafts in many applications where larger diameter stepped shafts have been used heretofore. For example, in many applications where oversized stepped shafts have been provided because of the need to provide ball bearing seats and shoulders, use of the teachings presented herein can result in substantial cost savings without sacrifice in product quality. In applications where stepped shafts have been used to avoid noise problems, savings may be realized without undue degradation of product quality. Somewhat surprisingly, utilization of shrink fitted aluminum collars provides extremely good results.
In FIG. 15, a number of points have been plotted based on test data that was taken on motors constructed according to the prior art and from motors that were constructed to embody different aspects of the present invention. A number of different motors, designated A1, A2, B1, B2, C1, C2, and D1, D2 were each soft mounted on a test fixture and driven with an electromagnetic driver positioned in spaced relation to the motor shell. The electromagnetic driver was then excited at different frequencies by the amplified output of an oscillator. The motors were supported so as to be free to vibrate, and an accelerometer was attached to the shell of each motor under test. The output of the accelerometer was then fed into an oscilloscope so that the relative magnitudes of acceleration would be displayed on the vertical axis, and the output of the oscillator was fed into the oscilloscope's horizontal input. The oscilloscope then revealed the resonant frequency for the motor under test when the oscillator frequency was varied.
Prior to the tests just described, the deflection of the shaft for each motor was determined for a condition where each shaft would be supported at the bearing journal locations and a two hundred pound concentrated load would be applied to a point on the shaft midway between the two bearing journals. The resonant frequency (in Hz) and the shaft deflection (in mils, or thousandths of an inch) for each motor is plotted in FIG. 15, and a curve has been fitted to the points so plotted. The points A1, A2, correspond to two different sleeve bearing motors made according to the prior art wherein a three-quarter inch stepped shaft (one-half inch shaft extensions) was utilized. Motor A1 had a 4.82 inch long shell whereas motor A2 had a 5.32 inch long shell.
Motors B1 and B2 used a one-half inch straight shaft, with motor B1 having a 4.82 inch long shell, and motor B2 having a 5.32 inch long shell. Motors C1 and C2 had 4.82 inch and 5.32 inch shells, respectively, and each had a straight one-half inch straight shaft with steel collars (otherwise similar to collars 47, 48 in FIG. 4) heat shrunk thereon. Motors D1 and D2 has 4.82 inch and 5.32 inch shells respectively; one-half inch straight shafts, and aluminum collars shrunk thereon (as shown in FIG. 4).
It will be recognized that motor C2 represented measurable improvement over the prior art motor B2. A comparison of motors C1 and B1 suggested that some degradation of performance could result by using a steel collar. When data points D2 and C2, are considered, it will be understood that straight shafts with aluminum collars may deflect more than similar shafts with steel collars. However, the resonant frequency of motors D2 was significantly higher than that of motors B2 and C2. The motor D1 on the other hand had a higher resonant frequency and less shaft deflection, as compared to motors B1 and C1.
Generally, a motor resonant frequency of about 600 Hz or greater means that a motor will normally have an acceptable noise level. Thus, the increase in resonant frequency for the motors D1 and D2 is an advantageous result. It is somewhat surprising, however, that the resonant frequency for the motors with aluminum collars was greater than the resonant frequency for the motors with steel collars (i.e., motors C1 and C2). It is at least partly because of the data shown in FIG. 15 that it is presently believed that advantages are associated with maintaining a permanently stressed condition along predetermined unsupported lengths of a motor shaft, and that desirable increases in resonant frequency of such motors are apparently due to an increase in the spring stiffness of the overall motor system due to such stressed conditions. Moreover, it is believed that better results were achieved with aluminum collars than with steel collars because the aluminum collars (being relatively soft as compared with a steel shaft) conformed to shaft surface irregularities and caused a more uniform stressed condition. On the other hand, it is believed that when both the shaft and a steel collar are provided with concentric, regular surfaces, it should also be possible to attain a more uniform stressed condition.
While one preferred method of producing embodiments of the invention has been described, it will be understood that other mechanisms may be used to maintain prestressed shaft sections. Moreover, it may be desired to first secure a rotor body to a shaft and then stress predetermined shaft sections, e.g., by shrinking collars on the shaft substantially adjacent or proximate to each end of the rotor body. This sequence also may be followed, of course, when structures of the type shown in FIG. 7 are manufactured. Reference has just been made to "substantially" adjacent or proximate to a rotor body end face. In the context of laminated cores, this may actually mean that a collar will be within one or two lamination thicknesses from a rotor end face, since predetermined dimensions between precisely machined collars are easily maintained in my process, whereas a laminated core usually will vary plus or minus one lamination from a nominal length. Thus, if one collar abuts a rotor end face, the other collar may be as much as two lamination thicknesses (typically one lamination is 0.020 to 0.025 inches thick) from the opposite end face.
While a number of different embodiments have now been described, it should be undestood that modifications will readily suggest themselves to those of ordinary skill in the art. Moreover, different aspects of the invention may be combined together, or only some aspects of the presently disclosed inventions may be practiced. Accordingly, the scope of the present invention is to be measured only by that of the appended claims.
Patent Citations
Non-Patent Citations
Referenced by
Original Image


text:
Sign up for Yardbarker's daily Top 10 newsletter, the Morning Bark! Customize to get news on your favorite sports and teams.
Found September 01, 2013 on TWNP-Wrestling News & Information:
PLAYERS: Justin Gabriel, Chris Jericho, Daniel Bryan, Randy Orton, John Cena
Tonight's show opens with Jo Jo watching Justin Gabriel stretch. Her and Eva ask Chris Jericho if Justin is single and he makes fun of her a bit. Then, clips from a match of Daniel Bryan, Kane and Randy Orton facing The Shield are shown. Bryan walks up to Brie after the match to greet her. Jo Jo and Eva tease her a bit. Jo Jo is then shown talking to Gabriel. Eva says she is worried because she doesn't think Jo Jo is ready to be with someone yet. Jo Jo and Eva watch a Gabriel match backstage. Jo Jo and Eva mention they're having a house warming party and that they will be inviting Justin. Then, things head to NXT and the Bellas are training with the Funkadactyls. Nattie walks up and says she is drained because of working things out about the wedding. Nikki talks about throwing her a bachelorette party. They talk about it for a few moments. Nattie then talks about the guy from last week that expressed his feelings for her. Brie says that him being at the wedding could cause a disaste...
Original Story: http://www.twnpnews.com/2013/09/wwe-t...
What do you think?To leave a comment, you can:
Triple H Addresses Fans Who Says He's "Bullying" Daniel Bryan
Total Divas Report – Natty's Bachelorette Party (Vibrators, Handcuffs & Drinks)
Jericho Talks About Most Recent WWE Run and His WWE Future
WWE RAW Preview – September 2nd, 2013
WWE Raw Highlights: Cody Rhodes Fired, Daniel Bryan vs The Big Show, More
Rumored WWE Hell In A Cell **SPOILERS** + Plans
Backstage News on Plans for Daniel Bryan vs. Randy Orton, Possible Match for WWE Hell In a Cell
Latest Vignette for Los Matadores, Chris Jericho Working on His Next Book, The Bella Twins
Notes on Tonight's SmackDown & Main Event Tapings, Preview for Total Divas, More
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subset: commoncrawl


text:
I am worried a neighbor woman elder to me might file a false stalking report.
She sent me an email saying that I am stalking her...she is kinda jerk/crazy...
so am worried she might actually accuse me for stalking...
Is it wise to file a police report against false accusation...(she gave me in writing that am stalking her)
also is it better for me legal point of view if I file a proactive police report that she might file a false stalking charge?
I am not sure what you should do. I need more info. Consult with an attorney.
At your service,
I'd love to tell you that if the accusations are false, you won't be charged. However, that's simply not the case. Cops often do very lop-sided investigations that end up in innocent people getting charged. You should do whatever you need to proactively to protect yourself. If you feel filing a report is necessary, then it probably wouldn't hurt to do so. Try doing it as passively as possible, such as filing it online or making a written statement and dropping it off at the police station. That way, you're not needlessly tying up police resources.
If she's making any specific allegations of your actions, keep records and proof of any alibis you may have. If you end up being contacted by the police about this, decline to make any statements and consult immediately with a lawyer. A lawyer will be able to communicate with the police in a way that will protect you.
If you don't already have a lawyer, hire one to help you. The law is complex and there may be things that can be done that you didn't know about. Good luck!
You need to keep her email, keep a diary of dates, times, events, etc. in the event you are charged in the future. If concerned, consult with a criminal defense attorney to advise you.
Get free answers from experienced attorneys.
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text:
If the game freezes, just click inside it (games can get unresponsive if you click elsewhere on the page).
This is probably the most realistic parking sim in the world! Everything like in the real life – steering, gearbox, pedals and rearview mirrors. Parking is the biggest problem for the novice drivers, so here you will have an opportunity to practice in it!
A / D - Turn left and right.
K - Press to accelerate.
J - Brake.I - Change forward gear.
L - Camera view.
P- Pause.
Add this game to your web page!
Copy this code to your page


text:
SCROLL DOWN FOR FAQs
Q: Is Presentation College an accredited institution?
A: Yes, the College and its various programs are accredited by the Higher Learning Commission of North Central Association of Colleges and Schools.
Q: There have been media reports the nursing program is not accredited. Is this true?
A: No, our ACEN accreditation status remains the same, pending the disposition of our appeal. Nursing programs in South Dakota and Minnesota must be approved by the respective States' Board of Nursing. The nursing program at Presentation College holds full approval by these States. It is important to note that graduation as a BSN, eligibility for NCLEX, and licensure once the NCLEX is passed, is in place with the approvals.
Q: What's at issue?
A: Standard 2 Faculty and Staff, Criteria 2.1, All faculty are not credentialed with a minimum of a master's degree with a major in nursing.
Q: How does this issue affect current, future and past nursing students?
A: This does not affect your graduation, your eligibility for the NCLEX, nor your licensure once you have passed the NCLEX. We will do whatever we are able to ensure continuing accreditation and help with application processes if needed. Please check our online page http://www.presentation.edu/ACENstatus for updates.
Q: What effect does this have on previous graduates?
A: None. The accreditation appeal does not affect the previous graduates of the nursing program.
Q: Does the status of ACEN accreditation affect any other PC programs?
A: No. The other programs have separate accreditations. The ACEN accreditation is specifically for the Nursing program.
Q: Would the loss of ACEN accreditation affect my eligibility to obtain financial aid?
A: No. The loss of ACEN accreditation would not affect your ability to apply, and if eligible, to receive financial aid for your program of study in any of PC's academic programs. Financial Aid is dependent upon the College's regional accreditation through the Higher Learning Commission.
Revised – 04/15/2014


text:
|By PR Newswire
Article Rating:
|December 28, 2012 08:30 AM EST
BELLEVUE, Wash., Dec. 28, 2012 /PRNewswire/ -- Voip-Pal.Com Inc. ("Voip-Pal") (OTC Pink Sheets: VPLM) is pleased to announce the completion of the Share Purchase Agreement to acquire Digifonica (International) Limited ("Digifonica, Gibraltar"), a private company registered in Gibraltar. The date of completion of the Share Purchase Agreement was December 27, 2012. As a result of the acquisition, all Digifonica, Gibraltar shares are being converted into VPLM stock.
Included in the assets owned by "Digifonica, Gibraltar", are Patent Pending Applications listed as RBR (Routing, Billing and Rating), Lawful Intercept, Mobile Gateway, Short Code/Emergency Dialing and Advanced Interoperability Solutions.
About the Patent Pending Applications
1. Routing, Billing and Rating engine (RBR): ("Producing routing messages for VoIP communications") US Patent Publication No. 20100150328 (Link to RBR USPTO filing): RBR allows new Licensees to perform subscriber management from their own existing subscriber management and billing platforms. This series of patented technologies allow Licensees to setup and deploy Digital Voice solutions virtually anywhere in the world in a matter of days, without fear of infringing on mainstream VoIP patents. (see Verizon/Vonage litigation[1])
2. Lawful Intercept ("Intercepting VoIP communications and other data communications") US Patent Publication No. 20100150138, (Link to Digifonica Lawful Intercept USPTO filing): Lawful Intercept is a revolutionary technology that addresses the national and international demands by governments to enable law agencies the ability to perform scheduled and live intercepts on Digital Voice telephone conversations. Network Service providers such as Skype may soon want to be in compliance with government regulations regarding Lawful Intercept.
3. Mobile Gateway, US Patent Publication No. 20110122827, (Link to Digifonica Mobile Gateway USPTO filing): This patent is designed to allow a single subscriber device to connect automatically to WiFi/WiMax and other wireless data connections.
4. Enhanced 911 ("Emergency Assistance calling for VoIP communications") International Application No. PCT/CA2008/000545: This is a patented technology which allows for Short Code/Emergency Dialing; in other words, the ability to enable true Emergency Calling solutions to Digital Voice subscribers.
5. Advanced Interoperability Solutions ("Uninterrupted Transmission of Internet Protocol Transmissions during Endpoint Changes") International Application No. PCT/CA2009/001317: This patent allows the transfer of in-session digital voice calls between disparate wireless technologies, enabling subscribers to roam seamlessly between different WiFi, WiMAX, 3G and 4G antenna technologies without losing a call.
About Voip-Pal.Com Inc.
Voip-Pal.Com Inc. is a broadband VoIP telecom company offering local and long distance VoIP services to residential and business customers. The company also provides VoIP communication and reseller solutions for its partners. Voip-Pal.Com Inc. is the enabler of international calls using VoIP technology on the internet, smartphones and PC Tablets. Voip-Pal's goal is to provide a quality, high-speed and cost-effective telephone solution for the casual and business international traveler who must rely on their smartphones, laptops or tablets in order to communicate. Voip-Pal.Com, through its wholly owned subsidiary "Digifonica (International) Limited Gibraltar", is a technical leader in the VoIP services market which had revenues of $58 Billion in 2011 and is experiencing double digit year-over-year growth[2]. The addition of Digifonica Gibraltar's patent portfolio greatly enhances shareholder value and will contribute to significant revenue growth for Voip-Pal.Com.
Retail Website: www.platinumphone.com.
Corporate Website: www.voip-pal.com
Company Contact: [email protected] and [email protected]
IR inquiries: [email protected]
US Telephone IR Contact: (954) 495-4600
Stock Quote: www.otcmarkets.com/stock/VPLM/quote
All statements contained in this news release, other than those identifying historical facts, constitute "forward-looking statements" within the meaning of Section 21E of the Securities Exchange Act of 1934 and the Safe Harbor provisions as contained in the Private Securities Litigation Reform Act of 1995. Such forward-looking statements relating to the Company's future expectations, including but not limited to revenues and earnings, technology efficacy, strategies and plans, are subject to safe harbors protection. Actual Company results and performance may be materially different from any future results, performance, strategies, plans, or achievements that may be expressed or implied by any such forward-looking statements. The Company disclaims any obligation to update or revise any forward-looking statements.
[1] http://news.cnet.com/2100-1036_3-6165747.html
SOURCE Voip-Pal.Com Inc.
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- i-Technology Blog: Zero-Cost Telephony, the 6-Ton Elephant in the Telco Room
- Mobile Music Gets Boost From New W600 "Walkman Phone"


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Just Fake It: The MockDataObjects Module
7 Nov
Hello from the antipodes! It's been a while since I've made any updates to my blog, and I just wanted to break the silence by demonstrating a new module that I've been working on called MockDataObjects. This extension gives DataObjects the ability to populate themselves intelligently with realistic-looking data. It comes with a variety of CMS enhancements and CLI tools for creating, populating, and managing mock data. It's very useful in the early phases of a project when you need data to use for testing.
Also, frontend developers will enjoy the model-independent data generation, which offers new template tags that generate mock data on the fly, without requiring any database fields.


text:
Jul 24, 2011 at 07:34AM EDT
I can get over the smile.BUT THE EYES. JESUS CHRIST THE EYES.
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text:
just a heads up I moved over to this blog; this one is (probably) gonna be inactive from now on.
"Ace Hardware: No screwing, just lots of screws."
"Ace Hardware: Nail your roof, not your partner."
"Ace Hardware: For when it really is just a hammer in your pocket"
One of my friends wanted to see a photomanip of the ace hardware logo in ace flag colors, and then I thought of these terrible puns, so here you go.
At first I wasn't going to reblog this but then I saw it again and just started laughing
my two favorite things: asexuality, and puns
and those puns are literally the best
I NEED more asexual puns
those are indeed the best
"Ace Hardware: Lube for your motor, not your junk"
"Ace Hardware: Erecting buildings, not your penis"
"Ace Hardware: Where nuts aren't genetalia"
"Ace Hardware: The hammer is not our penis. Its just a hammer."
"Ace Hardware: Where muff, is short for muffler"
"Ace Hardware: Yes that is a hammer, but we're still happy to see you."
"Ace Hardware: You can get Off™ in our repellent aisle"
(via ironicpeaches)
(via ironicpeaches)
Best moment in the whole series.
(via ironicpeaches)
This is what time lapse photography was invented for.
I legit just stared at this for like… 30 minutes giggling my face off
The longer you stare, the funnier it is.
(via ironicpeaches)
This is from the slut walk. One of the arguments is that girls ask for rape because they wear slutty clothes, short skirts, tight, low-cut tops. This girl is an example of the fact that rape victims can look like anyone, you, me, this girl. Rapists. Dont. Discriminate.
I promised a long time ago that I'd reblog this whenever I saw it on my dash. No regrets, it breaks my heart every single time.
an incredibly important message, rape is rape. no one is ever asking for it. a woman has the right to dress how ever they want - it is society that identifies risque dressing as 'asking for it', and in my opinion, that way of thinking needs to be diminished.
Seriously if you see this and don't reblog it, I have NO respect for you
(via ironicpeaches)
Teen Titan Rings
Top: Starfire, Raven
Bottom: Robin, Cyborg, Beast Boy
(via fyeahteentitans)
I made a thing. Found the ace on google.
"40% of Afghanistan's skateboarders are female.100 % of those are tough as nails. "
Source: @Skateistan
(via cliones)
Never judge.


text:
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text:
Sign up for Yardbarker's daily Top 10 newsletter, the Morning Bark! Customize to get news on your favorite sports and teams.
Found November 07, 2011 on MyTeamRivals.com:
PLAYERS: Mark Messier, Mario Lopez, Apollo AntonOhno
TEAMS: New York Rangers
TEAMS: New York Rangers
Sunday's New York City Marathon was a record breaking event, and i dont mean just in the number of attendees or the fact that course records were all but abolished. The event was highly publicized and thanks to a few big time names, raised alot of money for alot of great causes. Among the big timers were 8-time Olympic speed skating medalist Apollo Anton Ohno, six-time stanley cup champion Mark Messier, and two time Olympic softball gold medalist Jenny Finch. All three of these athletes made their contribution to their cause and did it in style. Ohno raised $26,000 for Special Olympics from Subway, simply by finishing the race in under 4 hours. And as Ohno, 29, says, "This actually hurts my short-track training, but the toughness you can gain from this crazy marathon is applicable." For Ohno the cause was more than just a minor set back in his short track training, and seeing as he has close to 3 years to go before he sets foot on the Olympic stage again. I guess you could sa...
Original Story: http://www.mtrmedia.com/mtr/2011/11/o...
Comments are closed.
What do you think?To leave a comment, you can:
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In-Game: Jets at Rangers, 11/6/11
Surgery to sideline Wolski
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Fastest CPU for MSI PM8M2-V motherboard
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text: Public Policy and the State of Florida's Handling of Catastrophic Risk By Donald D.Brown Former State Representative Former Insurance Committee Chair Introduction – A Change in Public Policy Public policy in the State of Florida regarding the handling of catastrophic risk, predominately wind from hurricanes, has changed rapidly over the course of the last five years. As homeowners insurance rates became a political issue during the 2007 elections, the solution offered by most politicians was to expand the Florida Hurricane Catastrophe Fund (FHCF) in order to "replace" private reinsurance with "lower cost" state provided reinsurance. It was thought that by expanding the roll of the FHCF homeowners insurance rates would drop about 24% statewide and "solve" the crisis. Other provisions were enacted into law to lower the rates for Citizens Property Insurance Corporation (Citizens) and allow it to compete with the admitted insurance market rather than serve the role of an insurer of last resort. This abrupt shift in public policy has changed the nature of both the FHCF and Citizens. Their original role of stabilizing and maintaining the market has changed to one of being mechanisms to lower insurance rates and to replace the private market with government insurance programs. In an effort to provide an easy and quick "fix" many ratemaking and risk management fundamentals important at the time when both the FHCF and Citizens were created have been ignored. In doing so, the state has assumed a tremendous amount of risk, which now has the potential to bankrupt the state. The potential exists that losses in the billions may not be funded due to the current crisis in the financial markets. The state of Florida has highly leveraged the homeowners insurance markets and has shifted loss payments from the private sector to the citizens of the state. Lower insurance rates have been accomplished at the cost of transferring tremendous risk to the citizens of Florida. In many or most cases, the citizens of the state have been unaware of how the rate reductions have been achieved. To make matters worse, the expected rate reductions have not resulted in the promised savings to policyholders. The 2004 and 2005 hurricane seasons resulted in assessments from the FHCF, Citizens, and the Florida Insurance Guarantee Fund (FIGA). These assessments are being spread to a broader base of policyholders as a result of the cross subsidization of homeowner 1 insurance rates. Those being assessed are not happy. The state is relying heavily on uncertain financial markets in order to finance losses with future debt rather than building capital and/or transferring risk to insurers and reinsurers. The state is one storm away from a major economic and financial crisis. If this happens, there is the expectation that the federal government will come to the rescue. Even if the federal government steps in to pay claims (which is by no means a certainty), it is doubtful that there will be a viable market the day after. Emergency assessments used to fund future capacity may not be viable if Florida citizens balk at increasing their exposure to additional losses (increasing assessments to fund future capacity). Also, there is no guarantee that the level of bonding needed to fund future losses will be available when needed. Subsequent season capacity may not be available and certainly not enough will be available to avoid major problems. If the federal government bails out the state, the federal government may insist that the state rely on the private market rather than agreeing to bail out the state a second time with U.S. taxpayer dollars. The way things are currently structured, the day after a federal bailout will be when Florida's problems become unmanageable. Anyone relying on a federal solution is stopping short of thinking the situation through and is only focusing on the immediate short term. The Florida Hurricane Catastrophe Fund Created to Stabilize the Market and Add Insurance Capacity Sixteen years have passed since Hurricane Andrew made landfall. Following Hurricane Andrew, world reinsurance capacity contracted, the private sector insurers were unable to maintain sufficient capacity to enable Florida residents to obtain property insurance. State action was needed to maintain a viable and orderly insurance market. The Florida Hurricane Catastrophe Fund was created to "…provide a stable and ongoing source of reimbursement to insurers for a portion of their catastrophic hurricane losses..." The idea was to "create additional insurance capacity sufficient to ameliorate the current dangers to the state's economy and to the public health, safety, and welfare." The statute that created the FHCF says that "it is therefore the intent of the Legislature that this program be structured as a state trust fund under the direction and control of the State Board of Administration and operate exclusively for the purpose of protecting and advancing the state's interest in maintaining insurance capacity in this state." The major benefit of the FHCF was originally intended to stabilize the market, to provide a level of coverage that is reliable and dependable, to provide additional reinsurance to supplement the private reinsurance market (not to replace private reinsurance), and to help maintain a viable and orderly marketplace. The FHCF was meant to be operated exclusively and solely to maintain insurance capacity in the state. 2 A New Public Policy – Lower Residential Property Insurance Rates Beginning in 2006, reinsurance prices spiked following Hurricanes Katrina, Rita, and Wilma. This caused homeowners rates in Florida to increase significantly. In January 2007, the Legislature met in special session in order to address the crisis. Most politicians ran for office based on a promise to reduce homeowners insurance rates. The expansion of the FHCF was seen as the solution to the "insurance crisis" since the high cost of private reinsurance was recognized as the primary cause of the problem. Thus, the FHCF's capacity was expanded by provisions that allowed for optional coverage both above the FHCF's existing capacity and below its insurance industry retention. The coverage above the FHCF known as TICL (Temporary Increase in Coverage Limit) potentially expanded coverage by $12 billion. The TICL coverage was priced using the same methodology as the pricing for the FHCF's mandatory coverage. As such, the pricing was far below market rates for private reinsurance. Another $4 billion on top of the $12 billion TICL layer was provided at the option of the State Board of Administration (SBA) under the same pricing terms. The coverage below the FHCF's existing industry retention (about $6 billion at the time) allowed for insurers to cut their retentions in half as well as provide such coverage for two events. This was known as TEACO (Temporary Emergency Additional Coverage Option) coverage. The potential increase in capacity below the FHCF was $6 billion. The pricing was very aggressive at 85% rate-on-line or 85 cents for each dollar of coverage for each insurer's share of a $3 billion retention, 80% rate-on-line for $4 billion, and 75% rate-on-line for $5 billion. Additionally, coverage was provide to limited apportionment companies of up to $10 million with a trigger of 30% of their surplus at a cost of 50% of the coverage chosen – 50% rate-on-line. The sum total of all potential coverages would total $38 billion. However, the SBA did not offer the top $4 billion and no insurers purchased the TEACO coverage. This reduced the overall capacity to $28 billion. Summary The public policy designed to lower homeowners insurance rates has actually resulted in the creation of a "catastrophic financial risk" to the state. Risk has been shifted from the private insurance industry to the policyholders of the state. The funding of the FHCF capacity is heavily reliant on the financial markets. Currently, the financial markets are in a liquidity crisis, and it is uncertain whether the FHCF could issue the needed amount of revenue bonds to fully fund its $28 billion of capacity. There is the potential that the FHCF could fall $10-$18 billion (or more) short of the capacity needed to fund its full capacity. With backup by the Federal government, the 3 state might be able to survive a "bad" year, but it is certain that the FHCF could not continue to provide sufficient capacity to keep rates low. Insurers will likely be forced to turn to the private reinsurance markets and consumer prices and the availability for residential property insurance will be adversely impacted. Without regard to whether or not the federal government steps in to bail Florida out, the insurance market will be decimated the day after a large event. For the benefit of all Floridians an alternative to the current "solution" must be found. We all have a financial stake in the outcome. Donald D. Brown, POB 866, DeFuniak Springs, FL 32435 – (850) 865-9280 email@example.com 4


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May election is fast approaching as Kapuso actress Heart Evangelista sizzles the cover of Esquire Philippines' May 2013 issue.
As she posed wearing a skimpy black bikini and a white tank top emblazoned with the word "VOTE", the controversial actress and girlfriend of re-electionist Chiz Escudero made her cover shoot one of the sexiest ever.
Grab your copies of Esquire PH's May 2013 issue is available in all leading magazine stands nationwide.


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Gavin Rossdale is out with the video to his new single 'Forever May You Run', the second release off the former Bush/Institute frontman's debut solo album 'WANDERlust', out now on Interscope. Watch it below.
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Islamism: A long-feared Mideast nightmare is beginning, thanks to a poisonous mixture of dormant historical forces and misguided U.S. policy. Cairo and Tehran, once America's allies, are forming a new axis of evil.
It would be bad enough if two once-dependable U.S. allies in the most strategically vital region of the world were becoming enemies of the West in isolation. But the top-level meeting of the Middle East's two most populous Islamic powers takes place as a historic upheaval within the region continues — a disruption largely of President Obama's doing.
Soon-to-be-nuclear-armed Islamofascist Iran's President Mahmoud Ahmadinejad seems willing to do anything and everything to engineer a strategic alliance with Muslim Brotherhood-dominated Egypt.
In the first visit of an Iranian premier to Cairo since Iran's Khomeini revolution and Egypt's post-Camp David peace treaty with Israel, Ahmadinejad got the red-carpet treatment from Egyptian President Mohammed Morsi.
He then proceeded to dangle cash before Morsi, tell the Egyptian press that "the only option is to set up this alliance because it is in the interests of the Egyptian and Iranian peoples and other nations of the region," and fanned the flames of an already burning Islamic paranoia about outside forces "striving to prevent these two great countries from coming together."
The land of the pharaohs and the onetime kingdom of the shahs have not restored diplomatic relations since U.S. ally President Hosni Mubarak was overthrown in the 2011 "Arab Spring" — ties have been broken for more than three decades — but formal relations will now obviously be patched up within months, perhaps sooner.
With Egypt's economy in deep trouble, its foreign currency reserves down 10% in just the last month, Ahmadinejad promised "a big credit line to the Egyptian brothers, and many services."
Ahmadinejad on Wednesday began taking part in the ominously named Organization of Islamic Cooperation summit in Cairo, along with 25 other leaders of Muslim states. Morsi, the first-ever Islamist Egyptian president, is taking his turn as the OIC's president.
The summit's agenda includes French attacks on Islamist militants in Mali, Israeli settlements and Muslim minorities' troubles. But the spectre of a radicalized Sunni alliance of Egypt, Saudi Arabia and Turkey, the objective of some Islamists, looms alongside the possible future Shiite-Sunni cooperation between Ahmadinejad and Morsi.
Those are but two nightmare scenarios for the Middle East in the Obama era. It was President Carter, who, in the name of human rights, naively thought abandoning our ally, the shah of Iran, and bolstering the exiled hard-core Islamist Ayatollah Khomeini would liberate the nation. Instead, he created a monster.
Similarly, Obama traveled to Cairo and apologized for the 1953 Iranian coup — which saved Iranians from Marxism-Leninism — after which it was no coincidence that instability swept the Mideast in an "Arab Spring" that is more accurately an Islamist hurricane.
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Surrey police confirm Alps killings arrest
Police in the UK have confirmed the arrest of a man in France in connection with the murder of four people in the Alps.
British engineer Saad al- Hilli, his wife Iqbal, her mother Suhaila al-Allaf and French cyclist Sylvain Mollier were all killed in the attack on September 5 2012.
In a statement Surrey police said:
"Surrey Police can confirm that an arrest has been made in France today in connection with the murders of four people near Annecy, southern France in September 2012.
"The arrest has resulted from a line of enquiry in France and is not as a result of the investigation carried out in the UK."


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Longer Length Shirtdress Dress
Knack for Numbers Dress$59.99Price: $59.99
With this navy shirt dress in your wardrobe, your ensemble always adds up to fashion perfection! Thisred-belted A-line is a geometrical delight with its fit-and-flare silhouette, angle-detailed V-neck, and curved, cap sleeves. Button up this matchable midi for a look with infinite possibilities!


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Easter Sunday Mass with Cardinal Timothy Dolan at St. Patrick's in Manhattan
Many worshipers gathered for Easter Sunday Mass by Cardinal Timothy Dolan, Catholic archbishop of New York, at St. Patrick's Cathedral in Manhattan. (March 31, 2013)
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|View woodnot's:
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50 posts in 2239 days
Location: Mount Vernon WA
I enjoy all facets of wood working, from large decks to fine boxes. I do more cabinets with multi wood types than anything else. I just started to learn to turn fine urn's and vases. I do some veneering as well.
The conference table in my icon was built for the board room of a local credit union. It's 20' long and 9' wide in the middle. it took 5 full sheeets of particle board and 5 full sheets of laminate.The top is wrapped in 2" bullnose oak and has spalted maple faces on the legs.
-- NW wood worker
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13 comments so far
#1 posted 2239 days ago
Welcome to LJs !! Glad you have joined us !!
-- Paul D - Lawrenceville, Georgia
#2 posted 2239 days ago
Welcome to Lumberjocks. The projects are an inspiration, the information is priceless and the people are supportive. The only problem is, the site can get addictive.
God Bless
-- Mc Bridge Cabinets, Iowa
#3 posted 2239 days ago
Glad to see that you have made Lumberjocks a part of your Woodworking experience… Welcome
-- Max "Desperado", Salt Lake City, UT
#4 posted 2239 days ago
Hello Woodnot,
Welcome to LJs. I hope that you will find this to be an exciting and rewarding part of your woodworking journey.
-- Challenges are what make life interesting; overcoming them is what makes life meaningful- Joshua Marine
#5 posted 2239 days ago
Welcome to lumberjocks. I hope you take advantage of all the possibilities LJ's offers
-- Kip Northern Illinois ( If you don't know where your goin any road will take you there) George Harrison
#6 posted 2238 days ago
Welcome to Lumberjocks . This is a great community of people with like interests.There is much to learn here & you will have the opportunity to share your skills & ideas with others. I hope you enjoy LJ's as much as I do.
-- Grumpy - "Always look on the bright side of life"- Monty Python
#7 posted 2238 days ago
Welcome to LJ's.
-- My favorite piece is my last one, my best piece is my next one.
#8 posted 2238 days ago
Welcome to LJ. You will like it here.
#9 posted 2237 days ago
Welcome to LumberJocks. Glad to have you aboard.
-- I've been blessed with a father who liked to tinker in wood, and a wife who lets me tinker in wood. Southern Delaware firstname.lastname@example.com †
#10 posted 2209 days ago
Welcome to LumberJocks.
-- jeanmarc manosque france
#11 posted 2209 days ago
Hay whats up woodnot. I like you name. Your work is very porfessnal. Nice to meet you.
-- Dennis Zongker
#12 posted 1880 days ago
Congratulations on your upcoming 1st anniversary as a Lumber Jock! Thanks for helping make this site a great place to be!
-- gjd Southcentral Wisconsin
#13 posted 1509 days ago
Another year has rolled by. We must be having too much fun, cause it seems like just yesterday when I congratulated you on 1 year. Congratulations on your 2nd anniversary at Lumber Jocks. Thanks for helping make LJ a great place to visit and happy anniversary!
-- gjd Southcentral Wisconsin
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