LINKAGE ASSEMBLY FOR IMPLEMENTS OF MACHINES

TECHNICAL FIELD

The present disclosure relates to an implement of a machine. More particularly, the present disclosure relates to a linkage assembly to lift and lower the implement.

BACKGROUND

Track type tractors, such as dozers, generally include an implement, such as a blade, to dig through relatively hard ground or compacted earth deposits involving clay and rocky soil. During a digging operation, a relatively large amount of force is often required to push a leading edge of the implement into the deposit so that the deposit may be broken and collected by the implement. This force is commonly referred to as penetration force. In order to begin a subsequent horizontal push, the implement generally shears and lifts the collected material out of the ground in an application commonly known as pryout or breakout. Breakout also occurs while pulling the implement out the ground at an end of the horizontal push, and also while lifting a large bolder or a hard rock surface.

To pull the implement out of the ground, track type tractors generally employ one or more fluid cylinders (or actuators) that facilitate the implement's release. During such a release, associated breakout forces produce a relatively significant (or largest) amount of force on the fluid cylinders. Additionally, on occasions where track type tractors are produced as purpose built machines, such as purpose built autonomous machines, the fluid cylinders may assume a position that may be unable to easily clear spacing constraints of an associated transportation unit.

U.S. Pat. No. 4,078,616 ('616 reference) relates to a frame for a crawler machine. The tractor frame comprises a pair of laterally spaced, rigidly interconnected main frame members, with a pair of lift cylinders that are supported in predetermined positions over the main frame members.

SUMMARY OF THE INVENTION

In one aspect, the disclosure is directed towards a linkage assembly for an implement of a machine. The machine includes a frame. The linkage assembly includes a bell crank assembly and a pair of fluid cylinders. The bell crank assembly is pivotally connected to the frame and coupled to the implement. Each of the pair of fluid cylinders are connected to the frame at one end and connected to the bell crank assembly at an opposite end. Moreover, the pair of fluid cylinders are positioned generally parallel to a length of the machine. The pair of fluid cylinders are extended to raise the implement.

In another aspect, the disclosure relates to a track type tractor. The track type tractor includes a frame, an implement, and a linkage assembly. The linkage assembly is configured for raising and lowering the implement relative to the frame. The linkage assembly includes a bell crank assembly and a pair of fluid cylinders. The bell crank assembly is pivotally connected to the frame and coupled to the implement. The pair of fluid cylinders are positioned generally parallel to a length of the machine, with each of the pair of fluid cylinders being connected to the frame at one end and connected to the bell crank assembly at an opposite end. The pair of fluid cylinders are extended to raise the implement.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is an exemplary machine with an implement, in accordance with the concepts of the present disclosure;

FIG. 2 is an undercarriage of the machine of FIG. 1, depicted in conjunction with a linkage assembly of the machine, in accordance with the concepts of the present disclosure;

FIG. 3 is a view of the linkage assembly with the surrounding components removed, in accordance with the concepts of the present disclosure;

FIG. 4 is a kinematic representation of the linkage assembly, in accordance to the concepts of the present disclosure; and

FIGS. 5 and 6 are different states of the implement, in accordance to the concepts of the present disclosure.

DETAILED DESCRIPTION

Referring to FIG. 1, a machine 100 is disclosed. The machine 100 is a construction machine, such as a track type tractor. The machine 100 includes a forward end 102 and a rearward end 104. The machine 100 may embody a dozer, although it is contemplated that the machine 100 is a purpose built machine that is customized to suit various operational parameters and requirements. In an example, the machine 100 is a purpose built autonomous machine. As shown, the machine 100 possesses a generally partial dozer configuration and is stripped of an operator cab. However, other variations in the machine's structure and rearrangement of various components and sections may be contemplated. For example, a position of the machine's engine (not shown) and associated components, such as an engine radiator portion 106, may also differ from conventional arrangements. In the depicted embodiment, the engine radiator portion 106 is positioned atop the engine, which may perhaps help attain a shorter machine length. Other similar re-arrangements are possible, and which help make the machine 100 more compact. Nevertheless, as aspects of the present disclosure will be divulged, it will become apparent that concepts presented herein may be applied to a variety of machines and applications. Reference will now be made in detail to specific embodiments or features, examples of which are illustrated in the accompanying drawings. Wherever possible, the same reference numbers will be used throughout the drawings to refer to the same or the like parts.

Referring to FIGS. 1 and 2, the machine 100 includes an engine compartment 108. The engine compartment 108 may house an engine system 110 inclusive of the engine of the machine 100. The engine system 110 powers a movement of the machine 100 over a ground 112. The ground 112 is also representative of a worksite over which the machine 100 is configured to operate. Further, the machine 100 includes a frame 116 (FIG. 2), ground engaging traction devices 118, an implement 120, and a hydraulic mechanism 122 (FIG. 2). The hydraulic mechanism 122 is configured to actuate the implement 120.

The engine system 110 is a power source of the machine 100. The engine system 110 is arranged within the engine compartment 108. The engine incorporated within the engine system 110 may represent one of the commonly applied power generation units in the art. The engine may be an internal combustion engine based on one of a dual-fueled engine system, a diesel-fueled engine system, a dual-fueled electric engine system, etc. The engine may embody a V-type, an in-line, or any configuration, as is conventionally known. The engine may be a multi-cylinder engine, although aspects of the present disclosure are applicable to engines with a single cylinder as well. Further, the engine may be one of a two-stroke engine, a four-stroke engine, or a six-stroke engine. Although not limited, the engine may represent power generation units, such as a compression ignition engines powered by diesel fuel, a stratified charge compression ignition (SCCI) engine, or a homogeneous charge compression ignition (HCCI) engine. Although the configurations disclosed, aspects of the present disclosure need not be limited to a particular engine type.

The frame 116 may be a main frame of the machine 100, generally forming a structural reference relative to which nearly every sub-structure and sub-system of the machine 100 is arranged. The frame 116 accommodates and supports the engine system 110, the ground engaging traction devices 118, the implement 120, and the hydraulic mechanism 122. Multiple other known components and structures may be supported by the frame 116 as well. The frame 116 plays a generally pivotal role in integrating and connecting various co-related structural and functions aspects of the machine 100. The frame 116 is supported relative to the ground 112 (or the worksite) by the ground engaging traction devices 118. The frame 116 includes a pair of rearward brackets 126 and a pair of forward brackets 128 to support a portion of the hydraulic mechanism 122 (discussed later).

The ground engaging traction devices 118 may constitute a transport mechanism of the machine 100, and may include a set of crawler tracks. Crawler tracks may be configured to transport the machine 100 from one location to another. Generally, there are two crawler track units (a first crawler track unit 132 and a second crawler track unit 134) provided for the machine 100, with each crawler track unit 132, 134 being suitably and individually provided on the respective sides of the machine 100, in a known manner. The crawler track units 132, 134 are in contact with a front idler 136, as is customary. In certain implementations, the transport mechanism of the machine 100 may include wheeled units (not shown) as well. Wheeled units may be provided either in combination with the crawler track units 132, 134 or may be present on the machine 100 as stand-alone entities. Ground engaging traction devices 118 are adapted to provide tractive force for the machine 100's movement over the ground 112 (or worksite) when powered by the engine system 110.

The implement 120 may be a ground engaging tool positioned at the forward end 102 of the machine 100. The implement 120 may be a work tool that is configured to alter a geography or terrain of a section of the ground 112 and carry out useful work. To this end, the implement 120 may be moveable in varied degrees of motion so as to be tilted right-left and forward-rearward, relative to a length, L, of the machine 100. Movements also pertain to the lowering and raising of the implement 120 relative to the machine 100 (FIGS. 5 and 6). In certain cases, the implement 120 may also be substantially panned about a plane depending upon a type of work. For this purpose, the hydraulic mechanism 122 includes a set of linkages actuated by hydraulic power for executing the above noted movements of the implement 120. In general, the implement 120 may be controlled by an operator of the machine 100 or by a control system (not shown) to perform work, such as to achieve a final surface contour or a final surface grade over the ground 112.

Referring to FIG. 2, the hydraulic mechanism 122 is structured and arranged within the machine 100. The view in FIG. 2 is removed of the engine compartment 108 and certain other surrounding components to solely depict an undercarriage of the machine 100. However, a detailed depiction of the hydraulic mechanism 122, in conjunction with the implement 120, is shown. The hydraulic mechanism 122 includes a number of fluid cylinders. The fluid cylinders are categorized as a pair of hydraulic tilt actuators 138, 138′ and a pair of hydraulic lift actuators 140, 140′. The hydraulic tilt actuators 138, 138′ are configured to facilitate the forward-rearward tilt of the implement 120, while the hydraulic lift actuators 140, 140′ are configured to alternate the implement 120 between a lowered state and a raised state (FIGS. 5 and 6), relative to the machine 100. The lowered state of the implement 120 is attained when the hydraulic lift actuators 140, 140′ are in a retracted position. Conversely, the raised state is attained when the hydraulic lift actuators 140, 140′ are in an extended position. The view depicted in FIG. 2 corresponds to a retracted position of the hydraulic lift actuators 140, 140′, and thus a lowered state of the implement 120. Each of the pair of hydraulic lift actuators 140, 140′ and the pair of hydraulic tilt actuators 138, 138′ is arranged so as to occupy positions that are laterally opposed or are towards either sides of the implement 120. It will be envisioned that more or less number of hydraulic tilt actuators 138, 138′ and hydraulic lift actuators 140, 140′ may be used, and that a number of the actuators used or disclosed in the present disclosure need not be seen as being limiting in any way. In general, an arrangement, configuration, and working, of the pair of hydraulic tilt actuators 138, 138′ are well known and conceivable by someone in the art, and thus, no further description is directed towards the hydraulic tilt actuators 138, 138′. Nonetheless, an arrangement of the hydraulic lift actuators 140, 140′ alongside a set of complementary assembly components, collectively constituting a linkage assembly 148 of the hydraulic mechanism 122, enhances a lifting operation of the implement 120. Therefore, an arrangement of the hydraulic lift actuators 140, 140′ with the associated components (i.e. the linkage assembly 148) is further described below.

Referring to FIGS. 2 and 3, the linkage assembly 148 of the hydraulic mechanism 122 includes a bell crank assembly 142 that works in conjunction with the hydraulic lift actuators 140, 140′ to operate the implement 120. Furthermore, the linkage assembly 148 is inclusive of a cross-linkage 144 and a lift arm 146 that together facilitate a coupling between the bell crank assembly 142 and the implement 120.

In further detail, the hydraulic lift actuators 140, 140′ are categorized into a first hydraulic lift actuator 140 and a second hydraulic lift actuator 140′. The hydraulic lift actuators 140, 140′ may be configured to be actuated synchronously, although the hydraulic lift actuators 140, 140′ may move independently of each other, such as to facilitate a right-left movement of the implement 120. The hydraulic lift actuators 140, 140′ are positioned generally horizontally or substantially along the length, L, of the machine 100 (see FIG. 1). In an instance, a movement of the hydraulic lift actuators 140, 140′ may be controlled by a controller associated with the machine 100. In some embodiments, however, the movement of the hydraulic lift actuators 140, 140′ may be manually controlled by an onsite or a remotely stationed operator. For ease in reference and understanding, further structural details of only the first hydraulic lift actuator 140 is specified, and wherever applicable, only the first hydraulic lift actuator 140 is discussed. Similar details may be envisioned for the second hydraulic lift actuator 140′ as well, as the second hydraulic lift actuator 140′ remains similar in form and function to the first hydraulic lift actuator 140. Moreover, for ease in reference, the first hydraulic lift actuator 140 may be simply referred to as an actuator 140. Wherever required both the first hydraulic lift actuator 140 and the second hydraulic lift actuator 140′ will be collectively referred to as actuators 140, 140′.

As conventional hydraulic actuators, the actuator 140 includes a cylinder 150, with a rod 152 (FIG. 6). The rod 152 is reciprocally movable within the cylinder 150. The cylinder 150 defines a head end portion 154 of the actuator 140, while the rod 152 defines a rod end portion 156 of the actuator 140 (FIG. 6). The rod end portion 156 is extendable from the head end portion 154 of the actuator 140 in a direction depicted by arrow, B (FIG. 4), which is substantially towards the forward end 102 of the machine 100 (see arrow, A, FIG. 1). The actuators 140 are coupled to the pair of rearward brackets 126 of the frame 116 at one end (or at the head end portion 154). In addition, the actuators 140, 140′ are configured to pivot relative to the frame 116 (or the pair of rearward brackets 126) and angularly vary relative to the length, L, of the machine 100.

The bell crank assembly 142 is positioned intermediately between the actuator 140 and the implement 120. More particularly, the bell crank assembly 142 includes a first bell crank lever 160 and a second bell crank lever 160′. The first bell crank lever 160 and the second bell crank lever 160′ are generally laterally laid out relative to the machine 100 and are respectively pivotally coupled to the first hydraulic lift actuator 140 and the second hydraulic lift actuator 140′. Also, the first bell crank lever 160 and the second bell crank lever 160′ are pivotally coupled to the pair of forward brackets 128 of the frame 116. Both the first bell crank lever 160 and the second bell crank lever 160′ are similar in construction and working, and thus, wherever applicable, details and working of only the first bell crank lever 160 is provided. It will be understood that the details discussed for the first bell crank lever 160 are equivalently applicable for the second bell crank lever 160′ as well. For ease and simplicity, the first bell crank lever 160 may be interchangeably referred to as bell crank lever 160.

In detail, the bell crank lever 160 includes a first end 166 and a second end 168. The first end 166 of the bell crank lever 160 is pivotally coupled to the rod end portion 156 by an end fork 172. The second end 168 is coupled to the implement 120 through the cross-linkage 144 and a lift arm 146 (discussed later). Further, the bell crank lever 160 includes a fulcrum 170 structured and arranged between the first end 166 and the second end 168. The bell crank lever 160 (i.e. both the first bell crank lever 160 and the second bell crank lever 160′) is pivotally coupled to the pair of forward brackets 128 of the frame 116 at the fulcrum 170. The bell crank lever 160 is defined such that a first axis 174 is defined between (or through) the first end 166 and the fulcrum 170, and a second axis 176 is defined between the second end 168 and the fulcrum 170 (FIGS. 5 and 6). The first axis 174 is defined at an angular offset Θ to the second axis 176. A portion of the bell crank lever 160 between the first end 166 and the fulcrum 170 and passing through the first axis 174 is termed as a first arm portion 178. Similarly, a portion of the bell crank lever 160 between the second end 168 and the fulcrum 170 and passing through the second axis 176 is termed as a second arm portion 180. Since the first axis 174 is at an angular offset Θ to the second axis 176, a structural bend 182 exists between the first arm portion 178 and the second arm portion 180. To this end, the structural bend 182 imparts a boomerang (or triangular) shaped profile to the bell crank lever 160. Both the first arm portion 178 and the second arm portion 180 meet at the structural bend 182, which is formed at the fulcrum 170 of the bell crank lever 160, and are envisioned to extend radially away from the fulcrum 170 at the angular offset Θ to each other. Moreover, the structural bend 182 is defined such that the second arm portion 180 attains an inclined position towards the implement 120 in the lowered state of the implement 120 (FIG. 5). Similarly, the first arm portion 178 attains an inclined positioned towards the implement 120 in the raised state of the implement 120 (FIG. 6).

The cross-linkage 144 is a cross-linking member connected between second ends 168, 168′ of first bell crank lever 160 and the second bell crank lever 160′, respectively. Given the lateral arrangement of the first bell crank lever 160 and the second bell crank lever 160′ relative to the machine 100, the cross-linkage 144 assumes a position that is substantially lateral relative to the machine 100, as well.

The lift arm 146 is an arm is pivotally coupled to the cross-linkage 144 substantially at one end 184, and is also pivotally coupled to the implement 120 at another end 186 by a coupler bracket 188 (FIG. 2). In that manner, the lift arm 146 is coupled and occupies a position between the cross-linkage 144 and the implement 120. In general, the lift arm 146 may take a position substantially midway to a length of the cross-linkage 144, although variations may be sought and contemplated. For example, it is possible for the cross-linkage 144 to be coupled to the implement 120 by means of more than one lift arms (such as lift arm 146). Therefore, a number of lift arms provided between the cross-linkage 144 and the implement 120 may vary from application to application.

The first arm portion 178 of the bell crank lever 160 is shorter in length than the second arm portion 180, as may be seen from FIGS. 4, 5, and 6. This feature of the bell crank lever 160 helps the actuator 140 attain a shorter length. In detail, a shorter first arm portion 178 length results in a shorter range of motion at the first end 166 of the bell crank lever 160, around the fulcrum 170, thus requiring a shorter rod (rod 152) or a shorter cylinder (cylinder 150). In co-relation, as the second arm portion 180 is longer than the first arm portion 178, a larger range of motion at the second end 168 is attained about fulcrum 170. Accordingly, since the second end 168 is coupled to the implement 120 via the cross-linkage 144 and the lift arm 146, shorter extensions of the rod 152 proportionally corresponds to a greater range of implement movement. In that way, it may be unrequited for the actuator 140 to attain a length equivalent to a stroke of the implement 120, thus leading to a more compact actuator design and a more compact machine configuration. Although a hydraulic effort required by the actuator 140 working with the shorter first arm portion 178 may be relatively significant, the head end portion 154 of the cylinder 150 provides more surface area for pressurized oil to contact and thus pressurize the cylinder 150, during operations. In that way, for the same pressure, the head end portion 154 of the cylinder 150 may generate more force than when, for example, the rod end portion 156 is pressurized. Therefore, in the extended position of the actuators 140, 140′, the implement 120 is configured to be raised relative to the machine 100 (or the frame 116).

In certain implementations, lengths of the first arm portion 178 and the second arm portion 180 may be reversed, i.e. the first arm portion 178 may be rendered longer than the second arm portion 180. This may be contemplated when lower energy producing fluid cylinders (actuators 140, 140′) are used, or when it is required to save hydraulic effort or it is required to produce larger degrees of torque (as attained by the larger range of motion of the longer first arm portion 178). Although an implement motion attained may remain similar, as attained by the relatively higher energy producing fluid cylinders (actuators 140, 140′) of the above embodiment, it will be understood that that longer first arm portions (such as first arm portion 178) may correspond to an increased rod (rod 152) length, which may inevitably lead to an increased machine length and size. Effectively, a lesser actuator length corresponds to an increased hydraulic effort, while a greater actuator length may correspond to a decreased hydraulic effort. Therefore, a length of the actuator 140 may vary or be based upon a hydraulic effort of the fluid cylinders (i.e. hydraulic lift actuators 140, 140′).

Referring to FIG. 4, a kinematic depiction 192 of the linkage assembly 148 is shown. The kinematic depiction 192 is shown inclusive of multiple links that are connected at their vertices. In particular, the kinematic depiction 192 presents a schematic assemblage between the various components of the linkage assembly 148 in the form of a line diagram to better understand a mechanism and a load path of the linkage assembly 148 to the ground 112. A first link 194 represents the actuator 140 (i.e. both the first hydraulic lift actuator 140 and the second hydraulic lift actuator 140′), a second link 196 represents the bell crank lever 160 (i.e. both the first bell crank lever 160 and the second bell crank lever 160′), while a third link 198 denotes the lift arm 146 that is coupled to the implement 120.

INDUSTRIAL APPLICABILITY

Referring to FIGS. 5 and 6, operative configurations of the linkage assembly 148 that pertain to the raising and the lowering of the implement 120 is shown. FIG. 5 represents the lowered state of the implement 120, while FIG. 6 depicts the raised state of the implement 120. The different states follow different configurations of the linkage assembly 148 as well, as the linkage assembly 148 is altered while shifting the implement 120 between the lowered state and the raised state. FIGS. 5 and 6 may also be sequentially viewed as to envision and understand an execution of a sequential shift of the implement 120 from the lowered state to the raised state. In the lowered state, the implement 120 may substantially contact the ground 112 (or worksite).

In operation, such as when it is required to grade the ground 112 and pile up a quantity of earth at a location, an operator shifts the implement 120 to the lowered state such that the implement 120 is in substantial contact with the ground 112. Thereafter, the operator initiates a machine movement. As the machine 100 moves, the implement 120 breaks into the ground 112 and begins to push the quantity of earth (for example, rubble as disintegrated ground particles) from a point distinct from the location. As machine movement progresses, the implement 120 pushes and grades an underlying surface of the ground 112 to finally collect the disintegrated ground particles at said location. A breaking of the surface of the ground 112 may in turn cause the implement 120 to sustain a proportional reactive force. After pushing through the ground 112, at some point the implement 120 may find itself under a relatively hard rock or a heavy surface. At this point, it may be required to pull the implement 120 out from the ground 112 (which has not yet been fractured or sheared). Pulling the implement 120 out from such a surface may produce the largest amount of force on the implement 120 and the associated linkage assembly 148. This is because during breakout, a maximum amount of machine weight is available, and the machine 100 may end up pivoting about the front idler 136. While pivoting about the front idler 136, the distance of the machine 100's centre of gravity versus the implement's tip to the front idler 136 are relatively similar. Therefore, a useful weight of the machine 100 for reacting against the cylinder forces (of the linkage assembly 148) is maximized.

Referring to FIGS. 4, 5 and 6, as the implement 120 is to be raised from the lowered state (i.e. from the surface of the ground 112), the operator actuates the actuators 140, 140′. In an example, the actuators 140, 140′ may be actuated manually. In another example, the actuators 140, 140′ may be actuated by a controller that is either integrated within the machine 100 or is configured as a stand-alone entity, and which is stationed perhaps at a remote location from the machine 100. Once the actuators 140, 140′ are actuated, a suitable fluid (such as a conventionally applied hydraulic fluid) enters the cylinder 150, such as in a head chamber of the cylinder 150. As a result, the cylinder 150 is pressurized and pushes the rod 152 (first link 194) of the actuator 140 to the extended position along a direction denoted by arrow, B (FIG. 4). As the rod 152 (first link 194) is extended, the rod end portion 156 pushes the first end 166 of the bell crank lever 160 (second link 196) in a rotational direction denoted by arrow, C (FIG. 4). In consequence, the bell crank lever 160 (second link 196) pivots (or rotates in counter clockwise direction identified by arrow, C, FIG. 4) about the fulcrum 170, moving the second end 168 of the bell crank lever 160 also in a counter clock-wise direction, but towards the rearward end 104 of the machine 100, in a direction identified by arrow, D (FIG. 4). Therefore, as the second end 168 of the bell crank lever 160 is pushed in reverse (arrow, D), the cross-linkage 144 also shifts rearwards pulling the lift arm 146 (third link 198, FIG. 4) in the same direction as well, in turn raising the implement 120 (arrow, E, FIG. 4) from the ground 112, and thus releasing the implement 120 from the surface of the ground 112.

Given the placement of the actuators 140, 140′ in a direction generally parallel to the length of the machine 100, a need to support the actuators 140, 140′ over frames of auxiliary components of the machine 100, as is practiced conventionally, is avoided. Moreover, as the actuators 140, 140′ are mounted to the frame 116, a considerable degree of load resulting from a raising of the implement 120 during breakout, is transferred to the frame 116. Therefore, the linkage assembly 148 has a more direct path to the ground 112, making the implement 120 well connected with the ground 112, to better alter the ground 112. Further, the frame 116 being generally more robust and rigid than frames of other sub-components of the machine 100, well bear the load received from the linkage assembly 148. Additionally, as the linkage assembly 148 is structured generally within the confines of the machine 100, components of the linkage assembly 148 are well veiled from being projected outwards of the machine 100, thus making the machine 100 more compact and compatible with restrictions associated with machine 100's shipping requirements.

It should be understood that the above description is intended for illustrative purposes only and is not intended to limit the scope of the present disclosure in any way. Thus, one skilled in the art will appreciate that other aspects of the disclosure may be obtained from a study of the drawings, the disclosure, and the appended claim.

LINKAGE ASSEMBLY FOR IMPLEMENTS OF MACHINES

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CPC

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