Abstract:
A scale for precise weighing measurements utilizing a strain gauge load cell includes a weighing platform which is cantilevered to one side of the load cell in order to permit a high profile load cell to be used while retaining a low platform height. An overload protection system causes the platform to bottom out against a fixed supporting base when a predetermined load is exceeded.

Description:
BACKGROUND OF THE INVENTION 
     It is desirable that strain gauge load cells utilized in weighing systems have as high a profile as possible, in order to provide maximum vertical spacing between upper and lower flexure beams which aid in isolating the strain gauge-equipped sensing beam from extraneous forces and bending moments. An example of such a load cell is illustrated in my prior U.S. Pat. No. 4,181,011. 
     However, the high profile preferred for the load cell is incompatible with the low profile desired for the weighing platform, the latter being preferred to minimize the inconvenience and effort required in moving the object to be weighed on and off the scale platform. 
     It is also desirable that strain gauge load cells be provided with an overload protection system to prevent excessive loads from damaging the strain gauges or the load cell structure itself. 
     Accordingly, the primary objects of the present invention are the provision of an improved load cell permitting maximum load cell profile height and minimum weighing platform height, along with a safe and reliable overload protection system. 
     SUMMARY OF THE INVENTION 
     The weighing platform of the scale is cantilevered to one side of the load cell, and is normally maintained in a resilient free-floating condition by means of compression springs exerting equal and opposite horizontal pre-load forces between the load cell and the platform. A lower mounting point between the platform and a yieldable member of the load cell normally provides both horizontal and vertical reaction forces, while an upper mounting point normally provides only a horizontal reaction force. When a predetermined load is exceeded, the pre-load biasing force of the compression springs is overcome, causing the platform to bottom out on a fixed base and to by-pass the excessive vertical loads safely around the load cell. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a simplified schematic side view of an exemplary load cell which may be utilized in conjunction with the present invention. 
     FIG. 2 is a simplified side view showing the load cell, supporting base and weighing platform in their normal configuration. 
     FIG. 3 is a view similar to FIG. 2, but showing the position of the weighing platform in an overload condition. 
     FIG. 4 is a perspective view of a portion of the weighing platform and load cell, showing a portion of the mounting structure. 
     FIG. 5 is a fragmentary plan view of the details of the mounting between the weighing platform and the load cell. 
     FIG. 6 is a side view of the structure of FIG. 5. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Referring to FIG. 1, there is illustrated in simplified schematic form a suitable load cell for use in a weighing scale. The load cell is described in further detail in my earlier U.S. Pat. No. 4,181,011. 
     Briefly, load cell 10 comprises a fixed end constraint 12 and a movable end constraint 14 interconnected by upper and lower horizontal flexure beams 16, 18 as well as by a cantilevered sensing beam 20. The left end of sensing beam 20 forms an extension of fixed end constraint 12, while the right end of sensing beam 20 is loaded in a vertical direction by means of a load directing flexure 22 having neck portions 24 of reduced thickness in the horizontal direction in order to absorb horizontal loads and isolate sensing beam 20 therefrom. Movable end constraint 14 is provided with a pair of pin-receiving holes 26 through which the vertical load to be measured is transmitted into end constraint 14 and through flexure 22 into sensing beam 20. Sensing beam 20 is adapted to have strain gauges bonded to its horizontal surfaces for measuring the tensile and compressive strains induced by the vertical applied load, as will be understood by those skilled in the art. 
     Fixed end constraint 12 is rigidly secured to a base spacer 28, and it will be recognized that the structure generally defined by elements 12, 14, 16 and 18 functions as a parallelogram, the latter three sides of which are movable vertically relative to fixed end constraint 12. 
     Referring now to FIGS. 2-6, the base spacer 28 is secured to base 30 of the scale, and projects slightly above the rest of the base, for purposes to be described below. Scale platform support 32 is cantilevered horizontally toward the left from load cell 10, which is viewed from the same side in FIG. 2 as in FIG. 1. Platform support 32 is connected to the load cell by means of a resilient system including upper and lower pins 34, 36 which are received by holes 26 in the load cell and on which are pivotally mounted upper and lower eye bolts 38, 40. Each of the eye bolts retains a compression spring 42 between a nut and washer at the threaded end of the bolt and a portion of platform support 32, as will be described below. Lower pin 36 is received within slot 44 of platform support 32 as best shown in FIGS. 4 and 6. Lower eye bolts 40 project through clearance holes 46 in platform support 32, as shown in FIG. 6, and lower compression spring 42 thus is compressed against that vertical wall of platform support 32 immediately surrounding clearance hole 46. In this fashion, the lower compression spring biases platform support 32 toward the left, as viewed in FIG. 6, relative to laterally immovable eye bolt 40, forcing lower pin 36 into the V-groove at the right end of slot 44. The shape of this slot enables both horizontal and vertical forces to be generated at this interface. 
     Upper eye bolts 38 pass through clearance holes 48 in platform support 32, and it will be recognized that upper compression springs 42 generate a rightward force on platform support 32, which forces vertical edge 50 of platform support 32 into engagement with upper pin 34. It should be noted that there is no contact between upper pin 34 and horizontal edge 52 of platform support 32 (see FIGS. 2, 4 and 6). 
     As best shown in FIGS. 4-6, the relative length of upper pin 34 and the space between the inner opposed faces of centering flanges 54 of platform support 32 permit pin 34 to be freely received between flanges 54, but such flanges function to keep platform support 32 centered, in plan view, on load cell 10. 
     Referring to FIG. 2, it will be appreciated that the load of an object to be weighed is applied downwardly through the scale platform (not shown) onto the left end of platform support 32, as schematically shown by arrow &#34;L&#34;. As long as that load is below the predetermined safe limit, an equal and opposite upward vertical reaction force is applied to the right end of platform support 32 at the point of tangency of lower pin 36 with the inclined upper face of the V-groove of slot 44. As will be understood by those skilled in the art, if moments are summed about lower pin 36, it will be seen that a horizontal force is applied toward the right against the upper portion of platform support 32 by upper compression string 42. This rightward horizontal force must be offset by an equal and opposite leftward horizontal force applied by lower compression spring 42 against platform support 32. 
     As long as load &#34;L&#34; is below a predetermined amount, the pre-load force of the compression springs is sufficient to keep the platform support 32 in the position shown in FIGS. 2 and 6, with upper pin 34 bearing against the vertical edge 50 and lower pin 36 nested into the V-groove of slot 44. In this condition, platform support 32 remains spaced above base spacer 28 and base 30. The load of the weighed object is transmitted into vertically yieldable end constraint 14 of load cell 10 by means of the downward force of platform support 32 on lower pin 36. The nut and washer on each eye bolt provide a convenient means for adjusting the magnitude of the pre-load biasing force. 
     As load &#34;L&#34; increases, a point is reached when the pre-load biasing force of compression springs 42 is exceeded and platform support 32 pivots counter-clockwise and downwardly on the left until it bottoms out on base 30 and base spacer 28, as shown in FIG. 3. When this condition is reached, upper and lower pins 34, 36 have &#34;collapsed&#34; or moved away from their abutting engagement with vertical edge 50 and slot 44, respectively, and thereby transmits no further load into load cell 10. 
     Those skilled in the art will recognize that as the point of application of load &#34;L&#34; moves further to the left on platform support 32, it will have an increasing tendency to cause collapse of the system into its condition of FIG. 3. This is an advantageous feature because the same relationship of load magnitude and point of application would also increase the load cell-damaging potential. 
     As an alternative to coil springs, Belleville washers could be used for higher capacities. Another alternative construction could reverse the illustrated location of V-slot 44 and vertical edge 50, so that the V-slot would receive and engage upper pin 34, while vertical edge 50 would engage lower pin 36. 
     This invention may be further developed within the scope of the following claims. Accordingly, the above specification is to be interpreted as illustrative of only a single operative embodiment of this invention, rather than in a strictly limited sense.