Orificed check valve in wing circuit

A wing locking system for a harvesting header is provided. The wing locking system includes an accumulator, a fluid cylinder operably attached to a wing of the harvesting header, a hose fluidly connecting the accumulator and the fluid cylinder, and a valve operably disposed between the accumulator and the fluid cylinder. The valve includes a first selectable position configured to permit a first fluid flow rate between the accumulator and the fluid cylinder and a second selectable position configured to permit a second fluid flow rate from the accumulator to the fluid cylinder. The first fluid flow rate is greater than the second fluid flow rate.

FIELD OF THE DISCLOSURE

The present disclosure relates to agricultural harvesters, and, more particularly, to a system configured to facilitate hydraulic locking of a harvester header having pivoting wings using a blocker valve with an open free flow state and an orificed check valve state.

BACKGROUND

Crop harvesting is commonly performed by a harvesting system comprising a combine harvester (“combine”) equipped with a removable header designed for harvesting crops. In an attempt to increase the throughput of such harvesting systems, combines are being paired with increasingly wider headers. However, although the increased span of such wider headers may improve throughput by increasing the rate at which ground can covered by the harvesting system, the increased width of the header may result in a decrease in crop yield efficiency. In particular, given the rigid, flat configuration of headers typically used in such harvesting systems, the increased inability of wider, rigid frame header to conform to variations in terrain often results in a decrease in the amount of crop that is harvested as the harvesting system travels over uneven terrain.

Additionally, increasing the width of the header of a harvesting system often increases the structural loads imparted by the heavier, wider header onto the combine. As a result, many combines that are used in such wider header harvesting systems incorporate reinforced combine structures configured to support the added weight of a wider header and to withstand and resist the increased dynamic loads that such wider headers impart. In addition to increasing the material costs required to manufacture such reinforced combines, the added mass of such reinforced combines also typically increases the costs of operating the harvesting system.

SUMMARY

One implementation of the present disclosure is a wing locking system for a harvesting header. The wing locking system includes an accumulator, a fluid cylinder operably attached to a wing of the harvesting header, a hose fluidly connecting the accumulator and the fluid cylinder, and a valve operably disposed between the accumulator and the fluid cylinder. The valve includes a first selectable position configured to permit a first fluid flow rate between the accumulator and the fluid cylinder and a second selectable position configured to permit a second fluid flow rate from the accumulator to the fluid cylinder. The first fluid flow rate is greater than the second fluid flow rate.

The second selectable position of the valve may permit fluid flow from the accumulator to the fluid cylinder through an orificed check valve and may prevent fluid flow from the fluid cylinder to the accumulator. When the valve is in the second selectable position, the flow of fluid into the fluid cylinder may be configured to constrain an upward pivot angle of the wing. In some embodiments, the valve may be in the second selectable position when the harvesting header encounters a negative loading condition. The upward pivot angle of the wing may range from 0.05° to 1.0°. In other embodiments, the valve may be in the second selectable position when the harvesting header is in an integrated transport configuration. The upward pivot angle of the wing may range from 1.0° to 10.0° and may be constrained by a limitation of the fluid cylinder.

Another implementation of the present disclosure is method of operating a harvesting header. The harvesting header includes a center section, a left wing hingedly attached to the center section, a right wing hingedly attached to the center section, and a wing locking system. The wing locking system includes an accumulator, a fluid cylinder operably attached to at least one of the left wing and the right wing, a hose fluidly connecting the accumulator and the fluid cylinder, and a valve operably disposed between the accumulator and the fluid cylinder. The valve includes a first selectable position configured to permit a first fluid flow rate between the accumulator and the fluid cylinder and a second selectable position configured to permit a second fluid flow rate from the accumulator to the fluid cylinder. The first fluid flow rate is greater than the second fluid flow rate. The method further includes operating the valve in the second selectable position during at least one of a transient negative loading condition and a sustained negative loading condition caused by an integrated transport configuration of the harvesting header.

The second selectable position may permit fluid flow from the accumulator to the fluid cylinder through an orificed check valve and may prevent fluid flow from the fluid cylinder to the accumulator. In some embodiments, the flow of fluid from the hose into the fluid cylinder may cause at least one of the left wing and the right wing to pivot upwards relative to the center section by between approximately 0.05° and approximately 1.0° during the transient negative loading condition of the harvesting header. In other embodiments, the flow of fluid from the hose into the fluid cylinder may cause at least one of the left wing and the right wing to pivot upwards relative to the center section by between approximately 1.0° and approximately 10.0° during the sustained negative loading condition caused by the integrated transport configuration of the harvesting header.

In some embodiments, when the valve is in the first selectable position, the flow of fluid into the fluid cylinder and out of the fluid accumulator and out from the fluid cylinder and into the fluid accumulator may be configured to allow the fluid cylinder to move the at least one wing within a first range along a wing trajectory. When the valve is in the second selectable position, the flow of fluid out from the fluid accumulator into the fluid cylinder may be configured to allow the fluid cylinder to move the at least one wing within a second range along the wing trajectory. The second range may be smaller than the first range.

In some embodiments, the transient negative loading condition may be caused by uneven terrain. In other embodiments, the transient negative loading condition may be caused by flexure of a trailer transporting the harvesting head. In further embodiments, when the harvesting head is in the integrated transport configuration, the harvesting head may be supported by structural members and ground engaging wheels.

Yet another implementation of the present disclosure is a harvester system. The harvester system includes a center section, a left wing hingedly attached to the center section, a right wing hingedly attached to the center section, and a wing locking system. The wing locking system includes an accumulator, a fluid cylinder operably attached to at least one of the left wing and the right wing, a hose fluidly connecting the accumulator and the fluid cylinder, and a valve operably disposed between the accumulator and the fluid cylinder. The valve includes a first selectable position configured to permit a first fluid flow rate between the accumulator and the fluid cylinder and a second selectable position configured to permit a second fluid flow rate from the accumulator to the fluid cylinder. The first fluid flow rate is greater than the second fluid flow rate.

The second selectable position of the valve may permit fluid flow from the accumulator to the fluid cylinder through an orificed check valve and may prevent fluid flow from the fluid cylinder to the accumulator. In some embodiments, the flow of fluid from the hose into the fluid cylinder may cause at least one of the left wing and the right wing to pivot upwards relative to the center section by between approximately 0.05° and approximately 1.0° during a transient negative loading condition. In other embodiments, the flow of fluid from the hose into the fluid cylinder may cause at least one of the left wing and the right wing to pivot upwards relative to the center section by between approximately 1.0° and approximately 10.0° during a sustained negative loading condition caused by an integrated transport configuration of the harvesting header. In further embodiments, the harvester system may include structural members and ground engaging wheels.

DETAILED DESCRIPTION

Referring generally to the FIGURES, a suspension system200for a harvester100configured to reduce structural loads is shown. As will be described in more detail below, suspension system200is configured as a variable spring rate suspension system, which allows the header104to more closely and easily follow terrain while the harvester100is in a harvesting mode, while also providing the header104with the ability to flex during an elevated, non-harvesting transport configuration of the header104. In doing so, the suspension system200reduces the structural loads that the combine102supporting the header104is subject to during operation of the harvester100. As such, the suspension system200allows the width of the header104to be increased (so as to, e.g., increase harvesting throughput) without requiring reinforcement of the structure of the combine102to support the increased mass of the wider header104.

Referring toFIGS. 1A-1C, an agricultural harvester100according to one embodiment is shown in various harvesting configurations as the harvester100travels over terrain having varying contours. As illustrated inFIGS. 1A-1C, according to various embodiments, the harvester100includes a combine102and an agricultural harvesting header104supported on the front of the combine102.

As illustrated by the simplified block diagram ofFIG. 2, according to various embodiments, the header104defines an articulated structure comprising a center section142to which a left wing144ais hingedly connected by a left hinge joint146aand to which a right wing144bis hingedly connected by a right hinge joint146b. The connection of the left wing144ato the center section142via left hinge joint146aallows the left wing144ato pivot upwards or downwards relative to the center section142about a generally horizontal axis along which the left hinge joint146aextends. Similarly, the connection of the right wing144bto the center section142via right hinge joint146ballows the right wing144bto pivot upwards or downwards relative to the center section142about a generally horizontal axis along which the right hinge joint146bextends. As will be understood, given the independent hinged attachment of each of the left wing144aand the right wing144bto the center section142, the left wing144amay pivot in any direction (i.e. upwardly or downwardly) and to any degree, irrespective of any pivoting of the right wing144babout the center section142, and vice versa.

Although, as described below, the harvester100comprises a suspension system200configured to maintain the header104in a generally flat configuration, according to some embodiments, such as, e.g., illustrated inFIG. 2, a manually or automatically actuated lock148may be provided between left wing144aand center section142and/or between right wing144band center section142which may optionally be used in situations in which a user may desire to fixedly and rigidly restrain the pivoting movement of left wing144aand/or right wing144brelative to the center section142.

As the harvester100transitions from travelling along generally flat terrain (during which the center section142, left wing144aand right wing144beach extend along a generally horizontal plane, such as, e.g., illustrated inFIG. 1A, that is substantially parallel to the terrain on which the header104is supported) to uneven terrain, the hinged connections of the left wing144aand right wing144bto the center section142allow the header104to more closely adapt to and conform to the contours of the variable terrain (such as, e.g., illustrated inFIGS. 1B and 1C).

In addition to increasing crop yield, by allowing the left wing144aand right wing144bto independently flex and adapt to changing terrain, the mass of the header104that is accelerated as the header104travels over uneven terrain is decreased, thereby minimizing the structural loads on the combine102. Thus, the articulated configuration of the header104allows the width of the header104to be increased (as compared to a rigid, non-articulated header) without necessarily resulting in increased stress on the combine102, thereby obviating the need to reinforce the combine102to support the wider width header104.

The combine102generally includes a combine harvester vehicle106and feederhouse108pivotally attached about a rear end to a lower portion of the combine harvester vehicle106(such as, e.g., to a chassis of the harvester vehicle106). A forward end of the feederhouse108is configured to support the header104. According to various embodiments, one or more feederhouse actuators (not shown) are operably coupled between the rear end of the feederhouse108and the combine harvester vehicle106. The feederhouse actuators may comprise any number of known actuator arrangements, with selective manual and/or automatic activation of the feederhouse actuator(s) being configured to cause the rear end of the feederhouse108to pivot relative to the combine harvester vehicle106, thereby resulting in a vertical movement of the forward end of the feederhouse108, as well as the resultant vertical movement of the attached header104, in an upwards or downwards direction, such as illustrated, e.g., inFIG. 3.

As will be understood, the activation of these feederhouse actuators may allow the harvester100to transition between a harvesting configuration in which the weight of the header104is at least partially supported by the ground, to a non-harvesting transport configuration in which the header104is elevated with reference to the ground (and in which configuration the weight of the header104is supported entirely by the combine102), such as, e.g., illustrated inFIG. 3.

In light of the articulated configuration of the header104, when feederhouse actuator(s) are activated to raise the header104to an elevated, non-harvesting transport configuration such as shown inFIG. 3, the hinged attachment of left wing144aand right wing144b(“together, wings144”) to center section142via left hinge joint146aand right hinge joint146b, respectively, may cause the outermost ends of wings144to sag relative to the height of center section142. As will be understood, the amount of downward displacement or sag of the outermost ends of the wings144as measured relative to the center section142increases as the width of the wings144is increased.

As described above, the ability of wings144to pivot substantially relative to center section142may advantageously allow the header104to conform to the terrain during harvesting. However, such substantial pivoting movement of the wings144relative to the center section142may be undesirable when the header104is in an elevated position (e.g., when the harvester100is being turned around on end rows or during non-harvesting transport of the harvester100). In particular, leaving the wings144unsupported and free to pivot relative to center section142while the header104is elevated may cause the outermost ends of wings144to fully lower, thereby decreasing clearance to the ground even when the header104is in a fully raised configuration, which may allow inadvertent contact between the ground and header104that could damage the header104.

Although preventing sagging of the outermost ends of the wings144in order to maintain a substantially flat profile of the header104may be desirable when the header104is in an elevated configuration such as, e.g., illustrated inFIG. 3—for reasons as described with reference to rigid frame, non-articulated headers above—it may be undesirable to lock or otherwise fix the wings144into a substantially rigid configuration in an attempt to prevent the outermost ends of wings144from doing so. In particular, locking or otherwise restricting movement of the wings144relative to the center section142during an elevated configuration of the header104(such as, e.g., during non-harvesting transport of the harvester100) may undesirably increase the dynamic loads that are imparted by the header104onto the combine102.

Instead, as will be described in more detail below, the harvester100is advantageously provided with a suspension system200that allows for some degree of pivoting movement of the wings144of the header104relative to the center section142while also supporting the header104in a substantially flat profile during field transport of the harvester100(i.e. when the header104is lifted entirely off of the ground). In doing so, the suspension system200minimizes the amount of header104inertia that must be accelerated when encountering bumps in terrain, thereby reducing the forces imparted on the combine102during travel of the harvester100with the header104in an elevated configuration.

Accordingly, in various embodiments, the harvester100is provided with a variable spring rate suspension system200configured to prevent the amount of downward displacement of the outermost ends of the wings144relative to the center section142when the header104is in an elevated configuration and to allow the hingedly attached wings144to pivot as needed relative to the center section142while the harvester100is in a harvesting configuration (i.e. when the header104is at least partially supported along the ground), thus minimizing the structural loading of the combine102by the header104. As such, the suspension system200may allow the harvester100to incorporate a wider header104for more efficient harvesting throughput without requiring a reinforced combine102structure to support the wider width header104.

More specifically, according to various embodiments, when the harvester100is in a harvesting configuration (i.e. when the header104is at least partially supported by the ground, such as, e.g., illustrated inFIGS. 1A-1C) the suspension system200of the harvester100is configured to allow for upward and downward pivoting of the wings144by approximately no more than ±15.0°, more specifically by approximately no more than ±10.0°, and more specifically by approximately no more than ±5.0° as measured relative to the lateral axis along which the center section142extends. When the harvester100is an elevated, non-harvesting transport position (i.e. when the header104is elevated such that the mass of the header104is not supported by the ground), the suspension system200is configured such that the upwards or downwards pivoting of the wings144is constrained to between approximately 10% and 30%, more specifically between approximately 15% and 25%, and even more specifically between approximately 20% of the range through which the wings144are allowed to pivot when the harvester100is in the harvesting configuration, such that the upward and downward pivoting of the wings144as measured relative to the lateral axis along which the center section142extends is approximately no more than ±4.5°, more specifically is no more than approximately ±2.5°, and even more specifically no more than approximately ±1.0° when the harvester100is in a non-harvesting transport position (such as, e.g., illustrated inFIG. 3). By constraining the upward or downward pivoting of the wings144during harvesting and non-harvesting transport configurations in such a manner, the suspension system200is configured to allow for between an approximately 10% to approximately 20% reduction in the stress imparted onto the combine102by the articulated header104, as compared to the structural load that would be imparted by a rigid, non-articulated header104having a similar width and mass.

As will be understood, the suspension system200may be defined by any number of and combination of different components that are arranged in a manner to allow for the selective constraint of the movement of the wings144relative to the center section142according to first and second variable states. In particular, in the first variable state, the suspension system200is configured such that movement of the wings144is constrained to a first range (such as, e.g., described with reference to the harvesting configuration above). Meanwhile, in the second variable state, the suspension system200is configured such that movement of the wings144is constrained to a second range that is less than the first range (such as, e.g., described with reference to the non-harvesting transport configuration above).

For example, according to some embodiments (not shown), suspension system200may comprise a first set of coiled springs positioned about the left wing144aand a second set of coils positioned about right wing144b. Each of the first set and second set of coils comprise a first spring and a second spring. One or both of the length of the first spring and/or spring constant of the first spring differs from the second spring, such that the spring force of the first spring is greater than the spring force of the second spring. The first and second springs are configured to be independently engageable, such that, when the first spring is engaged, the pivoting movement of the wings144about center section142of the header104is constrained to a smaller range of motion than when the first spring is disengaged, and the second spring is engaged.

Accordingly, in such embodiments, by selectively engaging the second springs, the suspension system200may provide the wings144with sufficient ability to pivot about center section142so as to allow the wings144to adapt to the contours of changing terrain when the harvester100is in harvesting position. Meanwhile, by selectively engaging the first springs, the suspension system200may be configured to allow for more constrained movement of the wings144relative to the center section142, thereby minimizing the degree of displacement of the outermost ends of the wings144relative to the center section142(and thereby minimizing the risk of the outermost ends inadvertently contacting the ground when the header104is in an elevated, transport position) while also providing the wings144with sufficient flexibility to pivot so as to minimize the dynamic loads on the combine102during non-harvesting transport of the harvester100(such as, e.g., illustrated inFIG. 3).

Alternatively, in other coiled spring embodiments of suspension system200, a single coiled spring may be positioned about each of the left wing144aand the right wing144b. The suspension system200may further comprise a length adjusting mechanism associated with each of the left wing144aand right wing144b, which is selectively actuatable to increase or decrease the effective length of the coiled spring. During non-harvesting transport with the header104in an elevated transport position, the length adjusting mechanisms may be actuated to effectively shorten the lengths of the springs, thereby increasing the spring force of the springs and minimizing the freedom of the wings144to pivot relative to center section142. Meanwhile, when in the harvesting position, the length adjusting mechanisms may be actuated to effectively lengthen the springs, thereby decreasing the spring forces of the springs and increasing the degree to which the wings144may pivot. As will be understood, according to various embodiments, the length adjusting mechanisms may be configured to allow the effective lengths of the springs to vary between first and second fixed lengths, while in other embodiments, the length adjusting mechanisms may be configured to allow the effective lengths of the springs to be varied as desired, thus allowing for greater or lesser degrees of constraint of the movement of the wings144relative to the center section142of the header104during different non-harvesting transport and/or harvesting uses of the harvester100. Additionally, while in some such embodiments the length adjusting mechanisms of the wings144may be actuated by the suspension system200in tandem with one another, in other embodiments, the length adjusting mechanisms may be actuated independent of one another, such that the degree to which movement of the left wing144ais constrained may vary from the degree to which movement of the right wing144bis constrained, and vice versa.

In yet other embodiments, the suspension system200may comprise a hydraulic system configured to provide for first and second variable states which selectively allow for differing degrees of pivoting of the wings144relative to the center section142. For example, in some embodiments (not shown), the suspension system200may comprise a pair a hydraulic circuits that are operably provided for each of the left wing144aand right wing144b, with a first circuit having a different volume and/or pressure of fluid than a second, distinct circuit defining the pair of hydraulic circuits.

Referring toFIG. 4, a simplified schematic of a hydraulic based spring suspension system200comprising a blocker valve300which is configured to provide for first and second variable states according to one embodiment is illustrated. The suspension system200illustrated inFIG. 4corresponds to one of the left wing144aor right wing144bof the header104, with the other of the left wing144aor right wing144bbeing provided with a substantially similar, albeit mirrored, suspension system200as shown in and described with reference toFIG. 4.

Suspension system200generally comprises a fluid cylinder202that is fluidly connected to one or more accumulators206via an attenuation hose208. The accumulators206are configured to store a volume of pressurized fluid (such as, e.g., incompressible hydraulic fluid) that is supplied to the fluid cylinder202via the attenuation hose208. As fluid flows into or out from the fluid cylinder202, the fluid cylinder202is configured to extend or retract. As the fluid cylinder202is configured to suspend the wing144(i.e., one of left wing144aand/or right wing144b), the retraction and extension of the fluid cylinder202in response to changes in the amount of fluid within fluid cylinder202causes the wing144to move pivotably about the center section142, resulting in the upward or downward movement of the wing144relative to the center section142.

A blocker valve300is fluidly disposed between the fluid cylinder202and the accumulators206. As will be described with more detail with reference toFIGS. 6A-9Bbelow, the blocker valve300is configured to allow for selective flow of fluid between the fluid cylinder202and the accumulators206, allowing the fluid cylinder202to provide varying degrees of suspension of the wing144, which in turn allows the suspension system200to provide for first and second variable states that selectively allow for differing degrees of pivoting of the wings144relative to the center section142.

As shown inFIG. 4, the accumulators206are additionally fluidly connected to a hydraulic block210, which serves as a source of fluid for the accumulators206. Fluid from the hydraulic block210is supplied to the accumulators206in response to the selective activation of a valve212to permit flow between the hydraulic block210and accumulators206. Once sufficient fluid has been allowed to fill the accumulators206to a desired pressure, the valve212may be activated to a closed configuration. As will be understood, according to some embodiments, a single hydraulic block210may be common to the suspension systems200of both the left wing144aand the right wing144b, while in other embodiments, the suspension systems200of each of the left wing144aand the right wing144bmay comprise distinct, individual hydraulic blocks210.

Referring toFIGS. 5A-5C, a blocker valve300according to various embodiments is illustrated. In general, the blocker valve300is selectively activatable between a flow position, defined by a flow structure302and a restricted flow position defined by a flow-restriction structure304. As will be understood, blocker valve300may be biased to either the flow position or restricted-flow position, and may be selectively energized or otherwise activated between the flow and restricted flow positions according to any number of different arrangements, including mechanical and/or electromechanical arrangements.

Additionally, while in some embodiments the activation of the blocker valve300between the flow position and the restricted-flow position may be controlled directly by the operator as desired, according to other embodiments, the activation of the blocker valve300may be controlled by a control system of the harvester100. For example, according to some embodiments, the harvester100may comprise a control system, which, in addition to controlling other aspects of the operation of the harvester100, may additionally be configured to control the activation of the blocker valve300. According to some such embodiments, the control system may be configured to automatically activate the blocker valve300to the restricted-flow position upon the control system exiting out of an auto-header height mode of the control system and/or in response to the feederhouse108(and attached header104) being lifted up and elevated with respect to the ground. In yet other embodiments, the control system may be configured such that, when the harvester100is operated in a manual mode, the blocker valve300is automatically activated to a restricted-flow position upon the control system receiving a signal from ground detection sensors that the header104has been elevated off of the ground.

When the blocker valve300is in the restricted-flow position, fluid present within the fluid cylinder202and attenuation hose208is prevented from flowing into the accumulators206. However, as will be described in more detail below with reference toFIGS. 10A-12B, according to some embodiments, it may be advantageous to allow for a limited degree of fluid flow from the accumulators206into the attenuation hose208and fluid cylinder202. Accordingly, as shown inFIG. 5A, according to some embodiments, the flow-restriction structure304of blocker valve300may comprise an orificed check valve structure400, which is configured to restrict flow from the attenuation hose208and fluid cylinder202into the accumulators206, but which allows for flow from the accumulators206into the attenuation hose208, even when the blocker valve300is in the restricted flow position.

In other embodiments, it may be desired that there be no flow in either direction (i.e. no flow of fluid into or out of the accumulators206) when the blocker valve300is in the restricted flow position. According to some such embodiments, the flow-restriction structure304of blocker valve300may comprise a double-checked valve structure (such as, e.g., illustrated inFIG. 5B) or other structure configured to prevent flow in either direction through the blocker valve300.

As shown inFIG. 5C, in some embodiments in which the blocker valve300comprises a flow-restriction structure304configured to prevent flow in either direction through the blocker valve300(such as, e.g., a double-checked valve flow-restriction structure304), the suspension system200may include an orificed check valve structure400arranged fluidly in parallel with the blocker valve300. By providing an alternate fluid path through which fluid from the accumulators206may flow into the attenuation hose208, the orificed check valve structure400may allow for restricted flow of fluid from the accumulators206into the attenuation hose208even when the blocker valve300is in the restricted-flow position.

The ability of the suspension system200to provide for first and second variable states which selectively allow for differing degrees of pivoting of the wings144relative to the center section142will now be described with reference toFIGS. 6A-9B.

Referring toFIGS. 6A and 6B, a simplified block diagram of the suspension system200and the header104configuration is shown during harvesting operation of the harvester100according to some embodiments. As described above, during harvesting, the articulated configuration of header104(in which left wing144ais hingedly attached to center section142via a left hinge joint146aand in which right wing144bis hingedly attached to center section142via a right hinge joint146b) allows the wings144of the header104to pivot upward and/or downward relative to the center section142to allow the header104to more closely follow the contours of the terrain.

As shown inFIG. 6A, to facilitate the ability of the wings144to travel over and follow contours in terrain during harvesting operation, the blocker valve300is in a flow configuration in which the flow structure302of the blocker valve300is aligned between the accumulators206and the attenuation hose208so as to allow fluid to freely flow between the accumulators206and fluid cylinder202. As described above, by allowing fluid to flow into and out from the fluid cylinder202, the fluid cylinder202is able to extend and retract as needed in response to changes in terrain. As will be understood, according to various embodiments, a float system configured to assist the header104in adapting to changes in terrain (such as, e.g., by monitoring changes in pressure imparted onto the header104and assisting in the flow of fluid into and out from the fluid cylinder202so as to maintain a desired target pressure) may be incorporated into harvester100.

Because fluid is allowed to flow freely between the accumulators206and fluid cylinder202during harvesting operation of the device, the pressure within the attenuation hose208will be substantially the same as the pressure within the accumulators206. Additionally, because the mass of the header104is supported by the ground during harvesting, as shown byFIG. 6B, the wings144extending substantially parallel to ground. The simplified block diagram ofFIG. 6Billustrates the header104when the header104is positioned on substantially flat terrain, and as such, the entire header104is shown inFIG. 6Bas extending in a generally planar manner. However, as will be understood, if the simplified block diagram ofFIG. 6Bwere to represent the header104along uneven terrain, the wings144of header104would be shown as extending substantially parallel to the terrain above which the wings144extended, such that the wings144would extend at non-zero degree angles relative to the center section142.

Referring toFIG. 7A, a simplified diagram of the suspension system200according to one embodiment is illustrated representative of a transition configuration of the harvester100, in which the header104is still supported by the ground (i.e. the header104has not been elevated to a point where the combine102supports the entirety of the weight of the header104) and in which the blocker valve300has been deenergized or otherwise deactivated from the flow position to the restricted-flow position.

In the transition configuration, the switching of the blocker valve300into the restricted-flow position prevents any fluid from flowing into or out from the accumulators206. Upon entering into the transition configuration, the amount of fluid within the fluid cylinder202and attenuation hose208corresponds to the amount of fluid that had been present within the fluid cylinder202and attenuation hose208immediately prior to the blocker valve300being switched to the restricted-flow position. Accordingly, upon entering the transition configuration, the wings144are ‘locked’ in their last position prior to the harvester100being put into the transition configuration. The ‘locked’ configuration of the wings144may correspond to a configuration of the wings144in which one or both of the wings144extend angled upward relative to center section142, extend angled downward relative to center section142, and/or extend substantially parallel to center section142. As will be understood, the configuration of the wings144in the ‘locked’ position will depend on whether the fluid cylinder202was in a retracted, expanded, or neutral state immediately prior to switching the blocker valve300into the restricted-flow configuration.

As illustrated inFIG. 7B, because the header104remains partially supported by the ground in the transition configuration, the wings144of the header104remain extending in a direction substantially parallel to the terrain above which the wings144are supported. As similarly described with reference toFIG. 6B, the header104that is represented by the simplified block diagram ofFIG. 7Bis shown in a configuration in which the header104is positioned atop substantially horizontal terrain. However, as will be understood, if the simplified block diagram ofFIG. 7Bwere to represent the header104positioned along uneven terrain, the wings144of header104would be shown as extending substantially parallel to the surface above which the wings144extend, such that the wings144would extend at non-zero degree angles relative to the center section142.

Referring toFIG. 8A, a simplified block diagram representative of the suspension system200during non-harvesting transport of the harvester100with the header104in an elevated position in which the weight of the header104is entirely supported by the combine102is shown according to one embodiment. As shown inFIG. 8A, in such an elevated, non-harvesting configuration of the header104, the blocker valve300remains closed in a restricted-flow configuration, in which flow of fluid from the fluid cylinder202and attenuation hose208into the accumulators206is prevented.

According to various embodiments, the attenuation hose208is constructed with a desired degree of elasticity and resilience, which allows the attenuation hose208to expand to hold increased volumes of fluids as compared to an initial, neutral configuration of the attenuation hose208. Although the flow of fluid into the accumulators206is prevented by the blocker valve300, fluid is free to flow between the fluid cylinder202and attenuation hose208during the elevated, non-harvesting transport configuration of the header104. As such, when the header104is elevated, causing the wing144to no longer be supported the ground, the elastic nature of the attenuation hose208is configured to allow some, or all, of the fluid that was ‘locked’ in the fluid cylinder202during the transition configuration (as described with reference toFIGS. 7A and 7Babove) to flow into the attenuation hose208, thereby increasing the volume of ‘locked’ fluid already present within the attenuation hose208(as also described with reference toFIGS. 7A and 7Babove).

As representatively illustrated by the simplified block diagram ofFIG. 8A, the displacement of some or all of the fluid from the fluid cylinder202into the attenuation hose208increases the pressure of the fluid within the attenuation hose208to a pressure that is greater than the pressure of the fluid stored within the accumulators206. Meanwhile, as representatively illustrated by the simplified block diagram ofFIG. 8B, the decrease in the volume of fluid within the fluid cylinder202resulting from the displacement of fluid from the fluid cylinder202into the attenuation hose208decreases the ability of the fluid cylinder202to suspend the wing144, which in turn causes the wing144to pivot downward relative to the center section142by an angle of al from an initial wing144position defined by the position of the wing144in the transition configuration (which in turn, corresponds to last position of the wing144during the last harvesting configuration of the header104prior to the blocker valve300being switched to a restricted-flow position).

According to various embodiments, the angle α1may range from approximately 0.05° to 1.5°, more specifically between approximately 0.5° and 1.0°, and even more specifically between approximately 0.6° and 0.8°. As will be understood, the angle α1by which the left wing144ais pivoted downwards relative to the center section142during the elevated, non-harvesting transport configuration may be the same or may be different than the angle α1by which the right wing144bis pivoted downwards relative to the center section142during the elevated, non-harvesting transport configuration.

Although, as shown inFIG. 8B, the wings144of the header104will exhibit some degree of sagging (i.e. pivoting of the wings144downwards relative to the center section142), with respect to the initial position of the wings144as defined by the position of the wings144during the transition configuration, the position of the wings144during the elevated, non-harvesting transport configuration may extend at an upwards angle relative to the center section142, generally planar with the center section142, or at a downwards angle relative to the center section142. As will be understood, the angle(s) relative to the center section142at which the wings144extend during the elevated, non-harvesting transport configuration will depend on factors including the angle(s) of the wings144relative to the center section142during the last harvesting configuration of the header104prior to the blocker valve300being switched to a restricted-flow position as well as the angle(s) α1by which the wings144are pivoted downwards during the elevated, non-harvesting transport configuration.

According to various embodiments, as the harvester100is in the elevated, non-harvesting transport configuration (such as, e.g., represented inFIGS. 8A and 8B), the harvester100may transition to a downward flex configuration in response to the mass of the header104being subject to a downwards acceleration force (such as, e.g., in response to the harvester100travelling over uneven terrain). As such, the harvester100is subject to additional instantaneous loading in the downward flex configuration in addition to the sustained loading that the harvester100is subject to during the non-harvesting transport configuration. As illustrated inFIG. 9A, during such additional loading of the header104in the downward flex configuration, additional fluid flows out of the fluid cylinder202and into the attenuation hose208. This additional fluid causes the volume of fluid within the attenuation hose208to further increase from the increased volume that the attenuation hose208was subject to during the elevated, non-harvesting transport configuration. As shown inFIG. 9A, as a result of this additional fluid now held within the attenuation hose208, the pressure within the attenuation hose208is further increased.

Meanwhile, as representatively illustrated by the simplified block diagram ofFIG. 9B, the additional decrease in the volume of fluid within the fluid cylinder202as fluid is displaced from the fluid cylinder202and into the attenuation hose208during the downward flex configuration causes the wing144to pivot further downwards relative to the center section142by an angle of α2. According to various embodiments, the angle α2may range from approximately 0.05° to approximately 2.0°, more specifically between approximately 0.5° and approximately 1.5°, and even more specifically by approximately 1.0°. As will be understood, the angle α2by which the left wing144ais pivoted downwards relative to the center section142during the downward flex configuration may be the same or may be different than the angle α2by which the right wing144bis pivoted downwards relative to the center section142during the downward flex configuration.

As explained with reference toFIG. 8B, although, as shown inFIG. 9B, the wings144of the header104will exhibit some degree of sagging (i.e. pivoting of the wings144downwards relative to the center section142), with respect to the position of the wings144in the configuration immediately prior to the downward flex configuration of the header104(such as, e.g., the elevated, non-harvesting transport configuration ofFIGS. 8A and 8B), the position of the wings144during the downward flex configuration may extend at an upwards angle relative to the center section142, generally planar with the center section142, or downwards relative to the center section142. As will be understood, the angle(s) relative to the center section142at which the wings144extend during the downward flex configuration will depend on factors such as, e.g., the angle(s) of the wings144relative to the center section142during the last harvesting configuration of the header104prior to the blocker valve300being switched to a restricted-flow position; the angle(s) al by which the wings144are pivoted downwards during the elevated, non-harvesting transport configuration; the angle(s) α2by which the wings144are pivoted downwards during the downward flex configuration; etc.

As illustrated byFIGS. 6A-9B, the ability of the blocker valve300to isolate flow into the accumulators206during a restricted-flow position and to allow flow to and from the accumulators206during a flow position provides the suspension system200with first and second variable states which selectively allow for differing degrees of pivoting of the wings144relative to the center section142. As discussed with reference toFIGS. 6A and 6B, when the blocker valve300is in the flow position, the first variable state is defined by the hydraulic circuit defined between the fluid cylinder202, the accumulators206, and the attenuation hose208. In this first variable state, the ability of fluid to flow freely between the fluid cylinder202and the accumulators206, allows the wings144to pivot about the center section142by an amount that defines a first range of motion. By allowing the wings144to pivot about the center section142, the suspension system200enables the wings144to dynamically adapt to and follow terrain, which, in addition to increasing crop yield efficiency, also reduces the dynamic loads on the harvester100during harvesting operation.

As discussed with reference toFIGS. 7A-9B, when the blocker is in the restricted-flow position, the second variable state is defined by the hydraulic circuit defined between the fluid cylinder202and the attenuation hose208. In the second variable state, the expandable nature of the attenuation hose208allows the attenuation hose208to hold fluid that may flow out of the fluid cylinder202. This ability of the attenuation hose208to hold an increased capacity of fluid provides the suspension system200with a manner by which the wings144are provided with a second range of motion by which the wings144may pivot relative to the center section142.

Because the second range of motion is smaller than the first range of motion (such as, e.g., by between approximately 10% and approximately 30%), the ability of the wings144to pivot about the center section142is more limited when the suspension system200is in the second variable state than when the suspension system200is in the first variable state. As such, when the header104is elevated from the ground with the suspension system200in the second variable state (such as, e.g., discussed with reference to the elevated, non-harvesting transport configuration shown inFIGS. 8A and 8B) the suspension system200is configured to maintain the header104in a relatively level configuration in which the header104only exhibits a minimum amount of sagging, thus minimizing the risk of the outermost ends of the wings144inadvertently coming into contact with the ground during non-harvesting transport of the harvester100.

Although the range of motion through which the wings144are able to pivot in the second variable state is limited, by providing even a limited range of motion by which the wings144are able to pivot about the center section142, (such as, e.g., by a range of between approximately ±0.05° and approximately ±2.0°) the suspension system200is able to reduce the mass of the header104that is accelerated during transport of the harvester100(such as, e.g., during when the harvester is an the elevated, non-harvesting transport configuration), thereby reducing the stress on the structure of the combine102(such as, e.g., by at least approximately 5%).

As noted above, the ability of the suspension system200to provide the wings144with a limited ability flex to while the suspension system200is in the second variable state is provided by the ability of the attenuation hose208to hold fluid that flows out from the fluid cylinder202when the wings144are subject to downward forces (such as, e.g., when the header104is elevated entirely off of the ground in the elevated, non-harvesting transport configuration or during the downward flex configuration in which the harvester100travelling with an elevated header104encounters uneven terrain). Accordingly, as will be understood, in various embodiments, the range of motion through which the wings144are able to pivot while the suspension system200is in the second variable state may be varied by, e.g., changing the length of the attenuation hose208, changing the selection of materials and/or structure of the attenuation hose208(to either make the attenuation hose208more or less compressible), etc. Additionally, according to some embodiments, the suspension system200may optionally be provided with an additional structure via which fluid may be added to and/or removed from the circuit defined by the fluid cylinder202and the attenuation hose208when the suspension system200is in the second variable state.

As will be understood, although the harvesting configuration ofFIGS. 6A and 6B, the transition configuration ofFIGS. 7A and 7B, the elevated, non-harvesting transport configuration ofFIGS. 8A and 8B, and the downward flex configuration ofFIGS. 9A and 9Bhave been described as occurring in a sequential manner, the various configurations illustrated and described with reference toFIGS. 6A-9Bmay occur according to any other number of sequences, in which any of the configurations may be repeated any number of different times. Additionally, the header104may be subject to the configurations ofFIGS. 6A-9Bfor varied durations of time. For example, according to various embodiments, the downward flex configuration ofFIGS. 9A and 9Bmay directly follow the transition configuration ofFIGS. 7A and 7B. In some embodiments, the transition configuration ofFIGS. 7A and 7Bmay directly follow the elevated, non-harvesting transport configuration ofFIGS. 8A and 8B.

Referring now toFIGS. 10A-10B, a simplified block diagram of the suspension system200and the header104configuration is shown during an upward flex configuration of the harvester100. In some embodiments,FIGS. 10A-10Brepresent an upward flex configuration caused by the header104encountering uneven terrain. For example, header104may experience transient negative loading (i.e., negative as in the opposite of the load caused by gravity) when riding over a divot or when returning to level ground after riding over a bump. In some embodiments, the upward flex configuration occurs subsequent a downward flex configuration, described above with reference toFIGS. 8A-9B. In other embodiments,FIGS. 10A-10Brepresent an upward flex configuration caused by transient negative loading due to flexure of a trailer upon which the header104is supported during a transport operation.

As representatively illustrated by the simplified block diagram ofFIG. 10A, negatively loading the header104results in the displacement of some fluid from the attenuation hose208into the fluid cylinder202. This displacement decreases the pressure of the fluid within the attenuation hose208to a pressure is that is less than the pressure of the fluid stored within the accumulators206. Because the blocker valve300is in the restricted-flow position, the orificed check valve structure400prevents flow in the direction from the fluid cylinder202through the attenuation hose208and into the accumulators206while permitting some limited/metered flow of fluid from the accumulators206to the attenuation hose208and into the fluid cylinder202. For example, the limited/metered flow rate of fluid through the orificed check valve structure400may be substantially less than the flow rate of fluid when the blocker valve300is in the flow configuration (i.e., the configuration depicted inFIG. 6A).

Meanwhile, as representatively illustrated by the simplified block diagram ofFIG. 10B, the increase in the volume of fluid within the fluid cylinder202resulting from the displacement of fluid from the attenuation hose208into the fluid cylinder202increases the ability of the fluid cylinder202to lift the wing144, which in turn causes the wing144to pivot upward relative to the center section142by an angle of α3from an initial wing144position. However, the presence of the orificed check valve structure400in the blocker valve300constrains the angle α3by which the wing144is permitted to pivot relative to the center section142. By contrast, unmetered flow from the accumulators206to the attenuation hose208may result in unconstrained and permanent ratcheting of the wings144into an upward configuration. Permanent ratcheting of the wings144into the upward configuration is undesirable, as it may degrade the harvesting efficiency of the header104and may overload the center section142of the header104, resulting in damage to the center section142or decoupling of the header104from the trailer during a transport operation.

According to various embodiments, the angle α3may range from approximately 0.05° to 1.0°, and more specifically between approximately 0.1° and 0.5°. The angle α3may be constrained by the restricted flow through the orificed check valve structure400and the compliance of the attenuation hose208. As will be understood, the angle α3by which the left wing144ais pivoted upwards relative to the center section142during the upward flex configuration may be the same or may be different than the angle α3by which the right wing144bis pivoted upwards relative to the center section142during the upward flex configuration.

Referring now toFIG. 11, an agricultural harvesting header104in an integrated transport configuration is depicted, according to some embodiments. As shown, the integrated transport configuration of the header104includes integrated transport structural members502and a plurality of ground engaging wheels504that support the header104and apply a sustained negative load to the left wing144aand the right wing144bsuch that the left wing144aand the right wing144bare forced into an upward flex configuration. Turning now toFIGS. 12A-12B, a simplified block diagram of the suspension system200and the header104configuration is shown during an integrated transport configuration of the harvester100. In some embodiments, the integrated transport configuration of the harvester100is identical or substantially similar to the integrated transport configuration depicted inFIG. 11.

As depicted in the simplified block diagram ofFIG. 12A, the upward force on the wings due to the integrated transport structure results in the displacement of some fluid from the attenuation hose208into the fluid cylinder202. This displacement decreases the pressure of the fluid within the attenuation hose208to a pressure that is less than the pressure of the fluid stored within the accumulators206. Because the blocker valve300is in the restricted-flow position, the orificed check valve structure400prevents flow in the direction from the fluid cylinder202through the attenuation hose208and into the accumulators206while permitting some limited/metered flow of fluid from the accumulators206to the attenuation hose208and into the fluid cylinder202until the pressure in the accumulators206and the attenuation hose208is equalized. As described above, the limited/metered flow rate of fluid through the orificed check valve structure400may be substantially less than the flow rate of fluid when the blocker valve300is in the flow configuration (i.e., the configuration depicted inFIG. 6A).

Meanwhile, as representatively illustrated by the simplified block diagram ofFIG. 12B, the increase in the volume of fluid within the fluid cylinder202resulting from the displacement of fluid from the attenuation hose208into the fluid cylinder202increases the ability of the fluid cylinder202to lift the wing144, which in turn causes the wing144to pivot upward relative to the center section142by an angle of α4from an initial wing144position. However, the presence of the orificed check valve structure400in the blocker valve300constrains the angle α4by which the wing144is permitted to pivot relative to the center section142and prevents the fluid cylinder202from pulling a vacuum on the attenuation hose208, which may result in decreased durability of the header104.

According to various embodiments, the angle α4may range from approximately 1.0° to 10.0°, and more specifically between approximately 3.0° and 7.0°. The angle α4may be constrained by a physical limitation of the fluid cylinder202. For example, in some embodiments, the fluid cylinder202includes a cylinder rod slidably coupled to a cylinder barrel, with the wing144coupled to the cylinder rod. Thus, the angle α4is limited by an amount the cylinder rod is permitted to protrude from the cylinder barrel. As will be understood, the angle α4by which the left wing144ais pivoted upwards relative to the center section142during the upward flex configuration during integrated transport may be the same or may be different than the angle α4by which the right wing144bis pivoted upwards relative to the center section142during the integrated transport configuration.

As will be understood, although the articulated header104illustrated herein has been shown as comprising three sections: a center section142, a left wing144a, and a right wing144b, according to other embodiments, the articulated header104may comprise any number of different sections, including, e.g., a two section arrangement defined by only the left wing144aand the right wings144b.