Abstract:
In a side bearing pad assembly two housings are provided, each having a bore of such size and orientation that the housings slide telescopically one within the other. When assembled the bores constitute a single internal cavity which houses resilient members. Each housing is mounted onto a load bearing member. The biasing resilient members urge the load bearing members apart when a compressive load is imposed on either of such members. The resilient members respond in a non-linear manner to force exerted on them.

Description:
FIELD OF THE INVENTION  
         [0001]    The present invention relates generally to springs and is more specifically directed to devices that dampen lateral rolling motions that occur during the movement of railroad cars.  
         BACKGROUND OF THE INVENTION  
         [0002]    Railroad cars in transit exhibit lateral roll due to track irregularities, inertia while negotiating turns, and even cross winds. Their high profile, high center of gravity, and great mass amplify these influences so that roll control is necessary to allow higher speeds around turns and to facilitate passenger comfort. Such lateral roll is exacerbated when rail cars are loaded with passengers or cargo, further increasing the car&#39;s mass and elevating its center of gravity.  
           [0003]    In general, axles and wheels of a rail car are mounted on wheel trucks that in turn support a carriage. A two stage suspension system comprising a primary and a secondary stage is generally employed on the wheel trucks. The primary stage isolates the wheel truck, commonly referred to by those skilled in the art to which the present invention pertains as a bogie, from the wheels, while the secondary stage isolates the carriage itself from the bogie. The most common primary suspension systems employ wedges or chevron springs, typically made of rubber bonded to metal, and positioned between the bogie and the axles of the rail car. Primary suspension systems have little or no effect on controlling lateral roll.  
           [0004]    In the above-referenced suspension system the carriage usually rests on a beam that spans the bogie parallel to the axles. This beam is referred to as a bolster by those skilled in the art to which the present invention pertains. The secondary suspension system includes mounts for coupling both the bolster to the bogie, and the carriage to the bolster. Generally, the bolster is supported on steel helical coil springs called bolster springs. The way in which the carriage is mounted to the bolster can vary. For example, a cleat and pad arrangement referred to as a side bearer mount is commonly employed. In this arrangement, the cleat is mounted to the bolster and can be in the form of a metal block or a block holding a wheel or a pad. Generally, the pad is made of laminated rubber and steel, and is bolted to the carriage underbody. More recent pad designs employ urethane springs bonded with rubber. These mounting devices physically limit the extent of rail car lateral roll but do little to dampen roll forces. Because these devices are not in continuous contact with the carriage, and because they employ little if any resilient material, these side bearer mounts do little to dampen impact between the carriage and the bolster during movement of the rail car. The high initial impulse of the carriage contacting the bolster can jar unsecured cargo within the carriage.  
           [0005]    Secondary stage suspension systems for passenger carriages are generally more sophisticated than those for freight carriages, typically employing air suspension devices that may be used in conjunction with or in place of side bearer mounts. Air systems employ a rubber housing that defines an interior space filled with pressurized air from the rail car&#39;s pneumatic system. These air systems are mounted in pairs on either side of the bolster, at the center of the bolster, or both. They typically provide a smoother ride and better control of lateral roll than side bearer mounts. Some high speed trains employ computer controlled pressurized air suspension systems which further improves ride properties and lateral roll control. However, all of the existing air systems employ numerous interdependent components, making them expensive and prone to reliability problems. Recent innovations include using urethane springs bonded with rubber in the secondary stage suspension between the carriage and the bolster. However, the high compression forces generated during operation tends to degrade the bond between the disparate materials, leading to higher maintenance and replacement costs.  
           [0006]    It is the general object of the present invention to provide a secondary suspension system that overcomes the drawbacks and difficulties associated with known prior art systems. It is a more specific object of the present invention to provide an economical and reliable device for use in a rail car secondary suspension system that assures a smooth ride for rail cars carrying passengers.  
         SUMMARY OF THE INVENTION  
         [0007]    The present invention is directed to a side bearing pad assembly for absorbing and cushioning compression forces. The assembly comprises a first and second housing, a first and second load bearing member, and biasing means. The first housing has an exterior surface and defines a bore extending at least partway through the first housing. The first housing is coupled to the first load bearing member, thus defining a first abutment surface on the first land bearing member opposite the first housing. The second housing has an exterior surface and also defines a bore extending at least partway therethrough. The second housing also has a bore, of a shape complementary to the exterior surface of the first housing, and is adapted to slidably or telescopically receive the first housing therein. The second housing is coupled to the second load bearing member, thus defining a second abutment surface on the second load baring member opposite the second housing. Biasing means for urging the first and second load bearing members away from each other in response to a load being imposed on at least one of the abutment surfaces is also provided.  
           [0008]    In the preferred embodiment of the present invention, the biasing means includes at least one spring, preferably two springs made of a solid resilient material each in the shape of a toroid. This is particularly advantageous for rail car suspension systems due to the spring characteristics imparted by that particular shape as described in detail below. Where more than one such toroidal spring is employed, a separating plate may be provided between them to ensure proper alignment of the multiple springs respecting an imposed load. This plate may be flat, or alternatively may be adapted with contours or conformations to increase surface contact between the plate and the springs under minimal or no load conditions. These contours may be formed in the material of the plate, or may be provided via a deformable laminate such as rubber, polyurethane, or similar such material.  
           [0009]    Preferably, one or more slip linings are provided between the first housing exterior surface and the second housing bore. Slip linings help minimize side loading by occupying the space between the housings, thereby ensuring that the axis along which the housings move relative to each other is substantially parallel with a compression force vector from an imposed load. When the slip lining is made of a material having a coefficient of static or sliding friction less than that of the housing material, it also facilitates sliding. One or more removable slip linings may be employed, or alternatively slip linings may be bonded to the exterior surface of the first housing, the interior surface of the second housing bore, or both.  
           [0010]    The present invention may also incorporate means by which to impose a compression force along its telescopic axis independent of a load imposed on an abutment surface. Such means may comprise hooks, “U” bolts, welded or bonded loops, recesses in the abutment surfaces, or any other such appurtenances by which an external device, such as a turnbuckle with threaded rods, may attach and compress the present invention along its telescopic axis. Such means to effect compression facilitates removal and replacement of the present invention without requiring that the entire carriage be supported. To facilitate this, an external compression device may be engaged on the present invention at one side of the bolster to secure the carriage while the present invention at the opposite side of the bolster is removed and repaired or replaced. This is especially valuable when the present invention is adapted to maintain continuous contact with the carriage underbody. 
       
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
       [0011]    [0011]FIG. 1 is an exploded view of the preferred embodiment of the present invention.  
         [0012]    [0012]FIG. 2 is a cross-sectional side elevational view of the apparatus as shown in FIG. 1.  
         [0013]    [0013]FIG. 3 is a graphical representation of force versus compression for two laterally unrestrained toroidal rings. 
     
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS  
       [0014]    As shown in FIG. 1, a side bearer pad assembly of the present invention is generally designated by the reference number  10  and is comprised of a plurality of components all positioned coaxially along a longitudinal axis  20 . A first housing  30  is provided and includes a first exterior surface  32 , and defines a first housing bore  34  extending through the first housing. The first housing  30  is fixedly joined to a first load bearing member  36  that defines a first abutment surface  38  opposite the first housing  30 .  
         [0015]    Similarly, a second housing  40  is provided having a second exterior surface  42  and defines a second housing bore  44  extending therethrough. The second housing  40  is fixedly joined to a second load bearing member  46  that defines a second abutment surface  48  opposite the second housing.  
         [0016]    Still referring to FIG. 1, first and second slip linings,  50  and  52  respectively, are provided. The first slip lining  50  has a first lining exterior surface  54  and defines a first lining bore  56  extending therethrough. The first lining bore  54  has a shape complementary to the first housing exterior surface  34 , and is adapted to receive the first housing therein. Similarly, the second slip lining  52  has a second lining exterior surface  58  and defines a second lining bore  60  extending therethrough. The second lining exterior surface  58  defines a shape complementary to and adapted to be received in the second housing bore  44 . The first slip lining exterior surface  54  is also similar in shape but slightly smaller in size as compared to the second slip lining bore  60 , so that the first slip lining  50  is slidably received within the second slip lining bore  60 . Thus the first housing  30 , the first slip lining  50 , the second slip lining  52 , and the second housing  40  all telescope along the axis  20 .  
         [0017]    The slip linings  50  and  52  ensure that the present invention, when subjected to a load, compresses essentially along its assembly axis  20  by occupying space between the first and second housings  30  and  40 , respectively. The slip linings  50  and  52  also serve to reduce friction between the housings when the material of the slip lining has a lower coefficient of friction than that of the housings, and to disrupt direct noise transmission between the bolster and the carriage that would exist if the two housings contact each other. Preferably, the slip linings are made of a suitable material such as, but not limited to polypropylene due to its resistance to degradation by dirt, oil and grease. While two slip linings have been shown and described, the present invention is not limited in this respect as more or less than two slip linings may be employed without departure from the broader aspects of the present invention.  
         [0018]    Referring to FIGS. 1 and 2, biasing means for urging the first and second load bearing members,  36  and  46 , respectively, away from each other in response to a load being imposed on either or both abutment surfaces,  38  and  48 , are provided in the form of two toroidal rings  62 . A separating plate  64  is interposed between the toroidal rings  62  with the rings and the separating plate being sized so as to be received within the first housing bore  32 . The separating plate  64  ensures that the axis of compression of the toroidal rings  62  does not become offset in relation to the assembly axis. While a flat plate  64  is illustrated, the present invention is not limited in this regard as a plate with surface depressions or conformations that increase surface area contact with one or both toroidal rings under a minimal or no-load condition may be substituted without departing from the broad aspects of the present invention. In addition, the plate  64  should be made from a suitable material. Polypropylene, laminated steel and rubber, laminated steel and a polymer, or other similar materials or combinations can be used to fashion such a formed plate.  
         [0019]    Referring to FIG. 2, the toroidal rings  62  are made from a suitable material, such as, but not limited to polyurethane. While toroid shaped rings have been shown and described, the present invention is not limited in this regard as other shapes, such as square, can be employed without departing from the broader aspect of the present invention.  
         [0020]    The toroidal ring shape is preferable for a rail car application since a toroid yields a non-linear spring (i.e.: a spring in which the relationship between compression and force defines a line whose slope is not constant). This non-linear characteristic is negligible until the toroidal rings are compressed beyond a certain minimal threshold. Compression of a laterally unrestrained toroidal ring can be calculated by the following formula:  
           F /(π dDE   O )=1.25[ x/d ] (3/2) +50( x/d ) 6    
         [0021]    where  
         [0022]    F=force applied  
         [0023]    d=uncompressed height of the toroidal ring  
         [0024]    D=diameter of the toroidal ring  
         [0025]    E O =modulus of elasticity  
         [0026]    x=reduction in height of the toroidal ring  
         [0027]    The above relationship is plotted graphically for two rings at FIG. 3. Due to the two exponential relationships on the right side of the above equation (i.e. [x/d] (3/2)  and (x/d) 6 ), compression of a toroidal ring exhibits significant non-linearity only when x/d&gt;0.2. This gives the advantage of low initial impulse but high ultimate resistance, two characteristics particularly advantageous for an application in dampening the lateral roll of rail cars. Initial contact of the rail carriage with such a non-linear spring will feel gentler to passengers, and will not jolt unsecured cargo as severely as the side bearer mounts of the prior art. The present invention can be adapted to maintain continuous contact with the carriage such that the carriage ‘rides’ on the present invention much like more complicated air suspension systems. Such design advantages may allow rail cars to negotiate curves at speeds higher than those allowed by side bearer mounts of the prior art.  
         [0028]    The preferred embodiment of the present invention exploits a lateral restraint characteristic for use in rail cars by employing toroidal rings whose largest diameter is slightly smaller than that of the first housing bore  32 . This arrangement provides no lateral restraint during initial application of a compression force, resulting in a gentle initial cushioning of a rail car&#39;s lateral roll which is represented by the shallow slope at the left end of the graph in FIG. 3. Upon further compression the toroidal rings become laterally restrained, resulting in a higher ultimate force resistance and a better ability to control very large lateral forces. Such a large force may be encountered when a rail car traverses an unbanked curve at high speed. Graphically, actual response mirrors the low loading section at the left end of the graph in FIG. 3. At higher loadings where the housing laterally constrains the toroidal rings, actual response is a slope steeper than that portrayed at high loadings in FIG. 3, since FIG. 3 reflects unrestrained toroidal rings.  
         [0029]    An alternative embodiment employs eye hooks on the load bearing members  36  and  46  or housings ( 30  and  40 ) by which a turnbuckle with threaded rods or similar such apparatus may attach to compress the present invention independent of a load imposed on the abutment surfaces  38  and  48 . This modification allows the present invention on one side of a bolster to be compressed so that the present invention on the opposite side of the bolster may be easily removed and replaced, without the need for high capacity jacks to support the carriage. This modification is particularly valuable when the present invention is adapted to maintain continuous contact with the carriage similar to air suspension systems, since the biasing means will always be under some level of compression even when the rail car is at rest. A compression jack may alternatively attach to holes, slots, or cavities within the housings ( 30  and  40 ), the load bearing members ( 36  and  46 ), or combinations thereof.  
         [0030]    The above preferred and alternative embodiments are illustrative rather than exhaustive, and may be combined in whole or in part to attain a particular set of advantages. Such combinations, and modifications thereof, are within the scope of this disclosure and will be apparent to those skilled in that art consistent with the teachings herein. The scope of the following claims encompass such modifications and variations in accordance with the Doctrine of Equivalents.