Abstract:
A system for reducing oscillating movement of a boom assembly about a fore-and-aft aligned axis defined by a pivotal connection of a suspension arrangement independent of a carrier frame is provided. The system includes an accumulator, a cylinder actuator mechanically interconnected between the carrier frame and the boom assembly, and a metered orifice connected in fluid communication to restrict a fluid flow between the accumulator and the cylinder actuator. In response to rotation of the boom assembly in a first direction relative to the carrier frame, the system creates a force resisting the rotation of the boom assembly in the first direction. Thereby, the system deadens oscillating pivotal movement of the boom assembly relative to the carrier frame and exerts a biasing force to assist in returning and/or maintaining the boom assembly at a generally horizontal alignment.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application is related to U.S. application entitled “System For and Method of Locking a Roll Suspension Arrangement For a Boom Assembly Mounted on an Agricultural Sprayer,” filed simultaneously with this application and hereby incorporated herein by reference in its entirety. 
     
     BACKGROUND OF THE INVENTION 
       [0002]    1. Field of the Invention 
         [0003]    The invention relates to an agricultural sprayer with a boom assembly, and more specifically, relates to a roll suspension arrangement in combination or including a system configured to reduce undesired oscillating movement of the boom assembly. 
         [0004]    2. Description of the Related Art 
         [0005]    Boom assemblies are commonly used on agricultural vehicles or self-propelled implements, such as sprayers or planters, to dispense seed, fertilizer, insecticide, herbicide, etc. and other miscellaneous agricultural materials. A typical boom assembly includes a pair of booms configured to pivot or fold between operative and inoperative positions relative to the boom support vehicle. In the operative position, the booms commonly extend in a laterally outward direction from the boom support vehicle such that the agricultural applicator covers a large surface area with each pass across a field. The weight of the boom assembly generally correlates with its operative length. 
         [0006]    Upon completing distribution of the agricultural materials to the field, the booms are generally swung, pivoted or folded in a forwardly or rearwardly direction to a folded, inoperative position. The preferred folded, inoperative position of the booms are generally parallel to the direction of travel of the support vehicle such that the boom assembly and support vehicle have a narrow profile for transport from the field and on a roadway. Folding or swinging the booms is typically performed manually or by a hydraulic or pneumatic system mounted between the booms and the boom support vehicle. Before transport, the booms are generally seated in or on a boom cradle or saddle structure such that the boom assemblies are supported for travel on the roadway. 
         [0007]    To accommodate the requirement for wider booms, manufacturers have developed a suspension arrangement for the boom assembly that is operable to reduce miscellaneous stresses imposed on the booms, the support framework, and/or the boom vehicles that are associated operation in the field. In addition, the suspension arrangement is designed to maintain a uniform distance or parallel altitude between the booms and the ground to maintain ideal spray coverage. A certain known “roll-suspension” arrangement includes a single pivot connection operatively connected between the boom assembly and the carrying or stationary frame in a manner that allows the boom to swing in a pendulum-like manner that is independent of the stationary frame. The addition of mechanical-type tools such as springs and/or rubber-composition shocks and/or gas-charged shocks are beneficial in damping or reducing oscillating movement of booms relative to the boom-support implement and/or vehicle when operating in rough terrain. 
         [0008]    However, known suspension arrangements employed to adjust a height of the boom assembly from ground have drawbacks. For example, known mechanical-type of suspension arrangements that solely employ springs and shock absorbers can be difficult to adjust, especially in the field. Also, known automatic suspension systems that use cylinder actuators to adjust a height of the boom assembly from the ground need fast reaction times. Otherwise, suspension arrangements that react too slowly will increase opportunities of instability of the boom assembly. 
         [0009]    Therefore, there is a need or desire for a suspension arrangement operable to address the drawbacks described above. The damping system should also be configured to be utilized with a wide variety of boom supported implements and/or vehicles in addition to those related to agriculture. 
       SUMMARY OF THE INVENTION 
       [0010]    The present invention provides a system in combination with or part of a suspension arrangement operatively connected between a boom assembly and a carrier frame supported on a boom support implement or vehicle that meets the desires and needs described above. The system of the present invention thus enhances operation of the suspension arrangement in regard to balance of a boom assembly, especially over rough terrain, as well as enhancing smooth transition in the folding of the boom assembly between the extended, operative position and the folded, inoperative position for transport. 
         [0011]    In a first exemplary embodiment of the present invention, a suspension arrangement is operatively connected between the boom assembly and the carrier frame is provided. The boom assembly is pivotally supported by the suspension arrangement about a fore-and-aft axis independently of the carrier frame in support of the boom assembly from a wheeled frame assembly of the sprayer for travel in a forward direction. The sprayer includes a fluid drive system configured to move the boom assembly between an extended position for operation in a field and a folded, non-operative position relative to the wheeled frame assembly for transport. In combination with the suspension arrangement, the system includes an accumulator, a cylinder actuator mechanically interconnected between the carrier frame and the boom assembly, and a metered orifice connected in fluid communication to restrict a fluid flow between the accumulator and the cylinder actuator. The system automatically creates a force resisting rotation of the boom assembly relative to the carrier frame. Thereby, the system reduces oscillating pivotal movement of the boom assembly about the relative to the carrier frame. 
         [0012]    The exemplary embodiment of the system further includes a pressure reducing valve configured to maintain a predetermined fluid pressure at the actuator cylinder, as well as an accumulator discharge valve to relieve fluid pressure when a fluid drive source or pump is disengaged. The pressure reducing valve can be manually set or set automatically via a remote controller. The remote controller is located remote of the pressure reducing valve and configured to send a signal to the pressure reducing valve representative of a desired change in pressure at the cylinder actuator. In response to the signal, the pressure reducing valve adjusts the fluid pressure between the cylinder actuator and the accumulator. The preferred system further includes a check valve located to isolate fluid communication, as well as to maintain fluid pressure, between the accumulator and the actuator cylinder. 
         [0013]    Each accumulator is pre-charged with gas pressure so as to provide an opposing force to the rotation of the respective boom about the pivot of the suspension arrangement. This spring force provided by each accumulator is adjustable by varying the pre-charged gas pressure of the accumulator. The suspension arrangement further includes an accumulator discharge valve connected in fluid communication with the accumulator in a manner so as to automatically “bleed off” or release pressurized fluid flow from the accumulator upon detecting, via a pilot line, a loss of pressurized fluid flow from the fluid drive source. 
         [0014]    The exemplary cylinder actuator includes a first cylinder actuator and a second cylinder actuator each in parallel fluid connection as separated by check valves to the fluid drive source. The first cylinder actuator and the second cylinder actuator each are mechanically connected at the boom assembly at a lateral offset distance from the fore-and-aft axis. Rotation of the boom assembly about the fore-and-aft axis in a first direction from horizontal causes a fluid flow in a first flow direction from the cylinder actuator through the metered orifice and into the accumulator, and rotation of the boom assembly in a second direction, opposite the first direction, from horizontal causes a fluid flow in a second flow direction from the accumulator into the actuator cylinder. The fluid flow in the first flow direction through the metered orifice creates the force resisting the rotation of the boom assembly in the first direction, and the fluid flow in the second flow direction through the metered orifice creates the force resisting the rotation of the boom assembly in the second direction. The metered orifice is a needle valve or flow control valve having an orifice selectively adjustable in size, and adjustment of the size of the orifice adjusts the force resisting the rotation of the boom assembly. 
         [0015]    The preferred embodiment of the system includes generally identical arrangements of a pressure reducing valve, check valve, accumulator, and accumulator discharge valve configured to operatively interact with the first and second cylinder actuators, respectively, so as to apply generally equal and opposing forces at the cylinder actuators in a manner that balances the generally horizontal alignment of the boom assembly about the suspension arrangement relative to the ground. 
         [0016]    Another embodiment of the present invention is an agricultural sprayer having a boom assembly with a central frame structure in pivotal support of a first boom and a second boom, a lift linkage in combination with a carrier frame configured to move the boom assembly between a lowered, operative position and a raised, inoperative position, a suspension arrangement in pivotal support of the boom assembly about a fore-and-aft axis independent of the carrier frame, and a system interconnected to reduce oscillating movement between the boom assembly and the carrier frame. The first and second booms each pivot about a vertical axis between an extended, operative position and a folded, inoperative position relative to the central frame structure. The system includes an accumulator, a cylinder actuator mechanically interconnected between the carrier frame and the boom assembly, and a metered orifice connected in fluid communication between the accumulator and the cylinder actuator. Fluid communication is isolated between the actuator cylinder, the accumulator, and a pressure regulating valve via a check valve. The metered orifice limits the flow of fluid therethrough, thereby reducing pivotal or oscillating movement of the boom assembly about the pivot connection of the suspension arrangement with respect to the carrier frame. 
         [0017]    In accordance with yet another aspect of the invention, a method of damping rotation of a boom assembly about a suspension arrangement of an agricultural sprayer is provided, substantially in accordance with the foregoing summary. 
         [0018]    Other objects, features, and advantages of the invention will become apparent to those skilled in the art from the following detailed description and accompanying drawings. It should be understood, however, that the detailed description and specific examples, while indicating preferred embodiments of the present invention, are given by way of illustration and are not limiting. Many changes and modifications may be made within the scope of the present invention without departing from the spirit thereof, and the invention includes all such modifications. 
     
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0019]    Preferred exemplary embodiments of the invention are illustrated in the accompanying drawings in which like reference numerals represent like parts throughout. 
           [0020]      FIG. 1  illustrates a fluid circuit diagram of a system of the present invention. 
           [0021]      FIG. 2  illustrates a rearward elevation view of the system of the present invention in combination with or part of a roll suspension arrangement on an agricultural sprayer supporting a boom assembly, the boom assembly in an extended, operative position. 
           [0022]      FIG. 3  illustrates a rearward side elevation view of the system of the invention in combination with or part of the roll suspension arrangement on the agricultural sprayer supporting the boom assembly of  FIG. 2 , the boom assembly in an extended, operative position rotated in a clockwise direction. 
           [0023]      FIG. 4  illustrates a rearward side elevation view of the system of the invention in combination with or part of the roll suspension arrangement on the agricultural sprayer supporting the boom assembly of  FIG. 2 , the boom assembly in an extended, operative position rotated in a counter-clockwise direction. 
           [0024]      FIG. 5  illustrates a partial perspective view of a known agricultural sprayer in support of a boom assembly, the boom assembly in an extended, operative position. 
       
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       [0025]      FIG. 1  illustrates a system  20  in accordance with the present invention in combination with or part of a roll suspension arrangement  25 , the system  20  generally configured to restrain or reduce undesired oscillating movement associated with operation of a “roll-suspension” arrangement  25  in pivotal support of a boom assembly  30  on a boom support implement  35  illustrated in  FIG. 5 . 
         [0026]    Referring to  FIG. 5 , the exemplary boom support implement  35  is a conventional agricultural sprayer of a type commonly used to apply crop pesticides, nutrients or animal/human waste (sludge) to soils, typically before and after planting in the spring and/or after harvest in the fall. The boom support implement  35  generally includes a main frame  40  supported on plurality of oversized wheel assemblies  45  and a hitch  50  operable to be towed by a tow vehicle (not shown) across a field. The main frame  40  is generally configured in support of a reservoir or storage tank  55 . With the booms assembly  30  in the extended, operative position (as illustrated in  FIG. 5 ), agricultural product is communicated in a known manner from the reservoir  55  to a series of spray nozzles (not shown) for distribution across a wide surface area of the field. 
         [0027]    Still referring specifically to  FIG. 5 , the boom assembly  30  generally includes a left boom  70  and a right boom  75 , each mounted by the series of nozzles in fluid connection with the reservoir  55 . The boom assembly  30  further includes a central frame  80  in pivotal support of the left and right booms  70  and  75 . The left and right booms  70  and  75  each are pivotable by a pivot actuator mechanism(s)  85  about a generally vertical axis in a known manner so as to move (as illustrated by arrow and reference  86 ) the booms  70  and  75  in a generally horizontal direction between the extended, operative position (see  FIG. 5 ) and the folded, inoperative position (illustrated in dashed line and by reference  88  also in  FIG. 5 ). The exemplary pivot actuator mechanism  85  is a conventional hydraulic-driven mechanism. Yet it is understood that other types of actuator mechanism  85  (e.g., pneumatic-driven, electrical-driven, etc.) can be used. 
         [0028]    The central frame  80  of the boom assembly  30  is coupled to a lift linkage assembly  90  by a carrier frame  95 . The carrier frame  95  is generally a conventional frame structure coupled in support of the boom assembly  30  at the lift linkage assembly  90  (See  FIG. 5 ). The lift linkage assembly  90  is generally operable to move the carrier frame  95  and attached boom assembly  30  between a lowered, operative position ( FIG. 6 ) and a raised, inoperative position (not shown). The exemplary lift linkage assembly  90  generally includes an upper left linkage  100  and a lower left linkage  105 , and an upper right linkage  110  (See  FIG. 2 ) and lower right linkage  115 . One end of each of the upper and lower left linkages  100  and  105  and the upper and lower right linkages  110  and  115  is pivotally attached at the carrier frame  95  so as to rotate about a horizontal axis. The other end of the each of the upper and lower left linkages  100  and  105  and the upper and lower right linkages  110  and  115  is pivotally attached at the main frame  40  so as to rotate about a horizontal axis. 
         [0029]    Still referring specifically to  FIG. 5 , a conventional lift actuator mechanism(s)  130  (e.g., hydraulic cylinder, pneumatic cylinder, etc.) is configured to drive or cause the lift linkage  90  to move the carrier frame  95  and supported boom assembly  30  in a generally vertical direction between the lowered, operative position (See  FIG. 5 ) and the raised, inoperative position (not shown). Once the lift linkage  90  has moved the boom assembly  30  upwardly in the vertical direction to the raised, inoperative position, the conventional pivot actuator mechanism  85  is operable to move the boom assembly  30  in a horizontal direction to the folded, inoperative position (illustrated in phantom line in  FIG. 5 ) for transport. 
         [0030]    Referring now to  FIGS. 2-5 , the “roll” suspension arrangement  25  operatively connects the carrier frame  95  and the boom assembly  30  such that the boom assembly  30  is operable to roll or rotate independent of the carrier frame  95  and lift linkage  90 . Thereby, the suspension arrangement  25  is generally operable in a conventional manner to maintain a uniform distance or parallel altitude between the booms  70  and  75  of the boom assembly  30  and the ground  135 . The conventional suspension arrangement  25  includes a generally central pivot connection  140  connected between the central frame  80  of the boom assembly  30  and the carrier frame  95 . The pivot connection  140  defines a generally horizontal, fore-and-aft aligned axis  142  (See  FIG. 5 ) about which the boom assembly  30  swings in a pendulum-type manner independently of the carrier frame  95 . 
         [0031]    FIGS.  1  and  2 - 4  illustrate the system  20  of the invention in combination with or part of the suspension arrangement  25  so as to restrain or reduce oscillating movement of the boom assembly  30  about the pivot connection  140  of the roll suspension arrangement  25  relative to the carrier frame  95  and lift linkage  90 . The exemplary system  20  includes a first fluid line  155  connected to receive a pressurized fluid flow from a conventional fluid drive source  160  (see  FIG. 1 ) located at a tow vehicle  165  (also illustrated in dashed line and by reference  165  in  FIG. 1 ). In addition to connection to the system  20 , the fluid drive source  160  (see  FIG. 1 ) is connected in fluid communication via fluid line  170  to drive operation of the pivot actuator mechanisms  85  configured to move the booms  70  and  75  of the assembly  30  in the horizontal direction between folded and extended positions (illustrated in  FIG. 5 ). The fluid drive source  160  (see  FIG. 1 ) is further connected in fluid communication via third fluid line  175  to drive operation of the actuator mechanisms  130  so as to move the carrier frame  95  and boom assembly  30  between raised and lowered positions (illustrated in  FIG. 5 ). The system  20  may further include one or more miscellaneous springs (not shown) and/or mechanical and/or gas-charged shocks (not shown) or the like configured to enhance isolation of vibration and miscellaneous forces from transmission between the boom assembly  30  and the carrier frame  95 . 
         [0032]    Referring specifically to  FIG. 1 , the fluid line  155  is in fluid communication with a left-hand circuit  185  connected in parallel to a right-hand circuit  190 . The left-hand and right-hand circuits  185  and  190 , respectively, are operatively configured to apply forces at opposed lateral distances from the pivot connection  140  so as to control oscillating movement of the boom assembly  30  about the suspension arrangement  25 . The left-hand circuit  185  includes a pressure regulating valve  192 , and right-hand circuit includes a pressure regulating valve  194 . The pressure regulating valves  192  and  194  are selectively adjustable by an operator either manually at the valve or from a remote controller  195  located at the tow vehicle  165  so as to regulate a desired fluid pressure of the left-hand and right-hand circuits  185  and  190 , respectively, of the system  20  in a manner so as to control a degree of restraint or resistance exerted by the system  20  so as to accommodate varying types of terrain. Generally equal set fluid pressures between the pressure regulating valves  192  and  194  causes generally equal and opposite forces on opposing sides of the boom assembly  30  so as to balance the boom assembly  30  at a generally horizontal alignment. For example, when operating in rough terrain, the operator may adjust the pressure regulating valves  192  and  194  so as to increase the fluid pressure of the left-hand and right-hand circuit  185  and  190 , respectively, of the system  20  in a manner that increases resistance or restraint of oscillating movement of the boom assembly  30  about the pivot connection  140  of the suspension arrangement  25 . When traveling over more smooth terrain, an operator may adjust the pressure regulating valves  192  and  194  so as to decrease the fluid pressure in the left-hand and right-hand circuits  185  and  190  of the system  20  in a manner that reduces resistance or restraint to movement of the boom assembly  30  about the pivot connection  140  of the suspension arrangement  25 . Pressure sensors  196  and  198  are located to indicate a fluid pressure of the at the left-hand and right-hand circuits  185  and  190 , respectively of the system  20  as controlled by the pressure regulating valves  192  and  194 , respectively. 
         [0033]    Although the following description is generally in reference to the left-hand circuit  185  in relation to the boom assembly  30  and the suspension arrangement  25 , one skilled in the art would understood that the right-hand circuit  190  is of a similar construction and operates in similar manner with respect to the boom assembly  30  and suspension arrangement  25 . 
         [0034]    The left-hand circuit  185  includes an accumulator  200  connected in series with a metered orifice  205 , which both are parallel connected in fluid communication with an cylinder actuator  210 . The accumulator  200  is a conventional cylinder pre-charged to a pre-determined pressure with a fluid or gas that is different than the fluid flow through the system  20 . The metered orifice  205  is located to adjustably restrict fluid flow between the accumulator  200  and the cylinder actuator  210 . In a similar construction, the right hand circuit  190  includes an accumulator  215  is connected in series with a metered orifice  220 , which both are parallel connected in fluid communication with an actuator  225 . The preferred metered orifices  205  and  220  are needle valves. Yet, the metered orifices  205  and  220  can be a remotely controlled pulse-width modulated control valves or another type of control valves and is not limiting on the invention. The metered orifices  205  and  220  can be manually adjustable or remotely controlled from the remote controller  195  located at the tow vehicle  165 . 
         [0035]    The system  20  further includes an accumulator discharge valves  226  and  227  connected in fluid communication with the accumulators  200  and  215 , respectively. The accumulator discharge valves  226  and  227   a  are each configured to automatically “bleed off” or release pressurized fluid flow from the respective accumulator  200  and  215  upon detecting a loss of pressurized fluid flow from the fluid drive source  160 . 
         [0036]    As illustrated in  FIG. 1 , the left-hand cylinder actuator  210  is a linear-actuated cylinder that includes a cylinder portion  230  and a rod end  235  movable in a linear direction (illustrated by arrow and reference  240 ) with respect to the cylinder portion  230 . As shown in  FIGS. 2-4 , the cylinder portion  230  of cylinder actuator  210  is connected at the carrier frame  95 , and the rod end  235  is connected at the central frame  80  of the boom assembly  30 . The left-hand cylinder actuator  210  is located laterally offset in a horizontal direction from the pivot connection  140  of the suspension arrangement  25 , and the right-hand actuator  225  is located laterally offset in an opposite horizontal direction from the pivot connection  140  relative thereto. Alternatively, the fluid cylinder actuators  210  and  225  can be combined into a double-extendible rod actuator having a single cylinder portion operatively connectively to move spaced apart rods connected at opposite left-hand and right-hand lateral distances from the pivot connection  140 . 
         [0037]    Still referring specifically to  FIG. 1 , the left-hand circuit  185  also includes a check valve  245  located to prevent fluid flow from the left-hand circuit  185  to the right-hand circuit  190 . As such, the check valve  245  restricts one-way fluid flow and maintains a selected fluid pressure, as selectively controlled by the pressure regulating valve  192 , in fluid lines connecting the accumulator  200 , the metered orifice  205 , and the cylinder actuator  210 . In a similar manner, the right-hand circuit  190  includes a check valve  250  that restricts one-way fluid flow and generally maintains the selected fluid pressure in fluid lines connected between the accumulator  215 , the metered orifice  220 , and the actuator  225 . The exemplary check valves  245  and  250  are pilot-operated, and spring-biased toward a closed position. For sake of illustration, the combination of the pressure regulating valve  192 , the pressure sensor  196 , the metered orifice  205 , the accumulator discharge valve  226 , check valve  228 , and the check valve  245  in  FIG. 1  is shown by reference  252  in  FIGS. 2-4 . In a similar manner, the combination of the pressure regulating valve  194 , the pressure sensor  198 , the metered orifice  220 , the accumulator discharge valve  227 , the check valve  229 , and check valve  250  in  FIG. 1  is shown by reference  254  in  FIGS. 2-4 . 
         [0038]    The pressure regulating valves  192  and  194  generally set at fluid pressure values so as to prevent the communication of a fluid flow from the drive source  160  at a pressure which would cause the cylinder actuators  210  and  225  to initiate movement of the boom assembly  30  about the pivot connection  140  of the suspension arrangement  25 . Instead, the pressure regulating valves  192  and  194  are set at fluid pressure values such that the cylinder actuators  210  and  225  are free to react as sensors mechanisms operable to detect pivotal movement of the boom assembly  30  about the pivot connection  140  of the suspension arrangement  25 . 
         [0039]    In example and as illustrated in  FIG. 2 , assume that the lift linkage  90  holds the carrier frame  95  and attached booms  70  and  75  of the boom assembly  30  in a lowered, operative position (See  FIG. 5 ) for spraying and distribution of product across the field. Also assume that the accumulators  200  and  215  are pre-charged to generally the same pressure, that the pressure regulating valves  192  and  194  are set at generally equal pressure settings, and that the terrain is generally level such that the boom assembly  30  and the carrier frame  95  are generally aligned with one another and horizontal aligned in parallel to the ground contour. Alternatively, the accumulators  200  and  215  can be pre-charged at different pressures relative to one another and/or the pressure-regulating valves  192  and  194  set at different pressure settings relative to one another in a manner that biases alignment of the boom assembly  30  at angle differing from general horizontal alignment in parallel with the carrier frame  95  and/or the ground contour. This embodiment may be desirable when operating the implement  35  along a side of a hill, for example. 
         [0040]    Referring now to  FIG. 3 , assume that the implement  35  is traveling over a sloped-terrain such that miscellaneous gravitational forces cause the boom assembly  30  to rotate in a clockwise direction (illustrated by arrow and reference  260 ) about pivot connection  140  of the suspension arrangement  25  relative to the carrier frame  95 . The clockwise rotation of the boom assembly  30  relative to the carrier frame  95  causes the cylinder actuator  210  to compress, forcing fluid from the cylinder portion  230  of the cylinder actuator  210  to the accumulator  200 . The metered orifice  205  restricts the fluid flow into the accumulator  200 , which translates to a linear force at the cylinder actuator  210  in a direction opposite to the compression of the cylinder actuator  210  that slows the pivotal movement of the boom assembly  30  relative to the carrier frame  95 . Also, the pre-charged accumulators  200  and  215  exert typically equal and opposite centering forces on the actuators  225  and  230 , and thereby resists the miscellaneous inertial forces associated with pendulum or rocking movement of the boom assembly  30  about the suspension arrangement  25  and causes the boom assembly  30  to self-center in a generally horizontal alignment parallel to the ground. 
         [0041]    In a similar yet opposite manner, the clockwise rotation  260  of the boom assembly  30  causes extension of the actuator  225 , creating a vacuum at the cylinder portion  230  which draws a fluid flow from the accumulator  215 . The metered orifice  220  restricts the fluid flow leaving the accumulator  215 , creating a force that resists and slows the clockwise pivotal rotation  260  of the boom assembly  30  about the suspension arrangement  25 . If the boom assembly  30  oscillates or moves in an opposite direction about the pivot connection  140 , the pressurized accumulator  215  exerts a damping force that resists the fluid flow leaving the actuator  225 . 
         [0042]    In accordance with the above description, the accumulators  200  and  215  of the system  20  absorb the miscellaneous inertial forces associated with causing pendulum- or rocking-type movement of the boom assembly  30  about the suspension arrangement  25 , as well apply generally equal and opposite centering forces that bias the boom assembly  30  toward a self-center position in a horizontal alignment parallel to the carrier frame  95  and the ground. 
         [0043]      FIG. 4  illustrates operation of the system  20  with counter-clockwise pivotal rotation (illustrated by arrow and reference  265 ) of the boom assembly  30  about the suspension arrangement  25  with respect to the carrier frame  95 . The counter clockwise rotation  265  of the boom assembly  30  causes the cylinder actuator  210  to contract in a manner that forces fluid flow from the cylinder actuator  210  through the metered orifice  205  and into the accumulator  200 . The counter-clockwise pivoting boom assembly  30  also causes the actuator  225  to extend, forcing fluid flow from the accumulator  215  through the metered orifice  220  to the actuator  225 . The pre-charged accumulators  200  and  215  in combination with the metered orifices  205  and  220 , respectively, slows the pivotal movement of the boom assembly  30  and furthermore dampens the oscillating pendulum movement of the boom assembly  30  about the suspension arrangement  25 , in a similar manner as described above in regard to reaction of the system  20  to clockwise rotation of the boom assembly  30 . 
         [0044]    While the system  20  of the invention has been shown and described with respect to particular embodiments, it is understood that alternatives and modifications are possible and are contemplated as being within the scope of the present invention. For example, although the system  20  is described in reference to an agricultural sprayer, one skilled in the art will recognize that the present invention is not so limited. A wide variety of boom support implements  35  and/or vehicles could employ the system  20  of the invention. In addition, although a certain suspension arrangement  25  is described operatively connected between the carrier frame  95  and the boom assembly  30 , it should be understood that the system  20  of the present invention can be employed to restrain a wide variety of suspension arrangements  25  and is not limiting on the invention. 
         [0045]    Many changes and modifications could be made to the invention without departing from the spirit thereof. The scope of these changes will become apparent from the appended claims.