• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Abstract of the Disclosure The present disclosure provides a control system of a powered machine. The control system includes a hydraulic motor configured to drive a track system of the machine. The motor is operable with a variable displacement. A control valve is fluidly coupled to the motor. In addition, the control system includes a controller and an electro-hydraulic valve disposed in electrical communication with the controller and fluid communication with the control valve. The electro-hydraulic valve receives a signal from the controller, and based on the signal, the electro-hydraulic valve hydraulically varies the start of control pressure of the motor. 220 202 226 r.--222 204 228 212) 218 224 20620 Fig. 2
    公开号:AU2013203133A1
    申请号:U2013203133
    申请日:2013-04-09
    公开日:2014-08-14
    发明作者:Bryon P. Neumann；Matthew J. Ramler；Calin Raszga
    申请人:Deere and Co；
    IPC主号:F15B13-02
    专利说明:
    1 CONTINUOUSLY ADJUSTABLE CONTROL MANAGEMENT FOR A 2 HYDRAULIC TRACK SYSTEM 3 4 Field of the Disclosure 5 The present disclosure relates to a control system of a variable displacement hydraulic 6 motor, and in particular, to the control management system of a track system on a machine. 7 8 Back2round of the Disclosure 9 Work machines, such as those in the forestry industry, are often required to balance 10 the amount of power distributed to various performance characteristics and operations. For 11 instance, a machine may include a boom and work implement to complete a desired task. 12 The amount of power produced by the engine is shared throughout the machine to move the 13 machine along different terrain and also operate the boom and work implement. In some 14 instances, it is desirable for the machine to travel at a high speed, whereas in other instances 15 the machine may be stationary and work is being done by the boom and work implement. In 16 any event, it is desirable to optimize machine performance. 17 Some machines utilize one or more hydraulic motors to provide torque to drive the 18 machine forward and backward. The machine can include an engine that produces power 19 and drives a hydraulic pump. The pump can provide hydraulic fluid to the one or more 20 hydraulic motors through a control valve. Each hydraulic motor can be a variable 21 displacement motor, such that at a minimum displacement the machine can move at a high 22 speed and at a maximum displacement the machine travels at a lower speed. At a maximum 23 displacement, however, a greater amount of torque can be provided to drive the machine over 24 difficult terrain, an inclined slope, etc. The manner in which motor displacement is 25 controlled on a variable displacement hydraulic motor is through a predefined "start of 26 control" pressure (SOC) that is mechanically fixed and it is difficult to make any adjustments 27 to the displacement setting. The "start of control" pressure is a defined pressure at which the 28 motor displacement begins to increase due to an increased load on the motor. The lack of 29 adjustability prevents the machine from performing at optimal levels of performance in 30 nearly every possible scenario. 1 1 A need therefore exists to provide a means for adjustably controlling the "start of 2 control" pressure of the motor to better optimize machine performance. Moreover, it is 3 desired to be able to make these adjustments continuously and as a function of how a 4 machine operator is controlling the machine in real-time. 5 6 Summary 7 In an exemplary embodiment of the present disclosure, a control system is provided 8 for a powered machine. The machine includes an engine for producing power and a track 9 system for moving along a surface. The control system includes a hydraulic motor 10 configured to drive the track system, where the motor is operable with a variable 11 displacement. The control system also includes a control valve fluidly coupled to the motor, 12 a controller, and an electro-hydraulic valve disposed in electrical communication with the 13 controller and fluid communication with the control valve. The electro-hydraulic valve 14 receives a signal from the controller, and based on the signal, the electro-hydraulic valve 15 hydraulically varies the SOC pressure with an external fluid source. 16 In one aspect of this embodiment, the electro-hydraulic valve is fluidly coupled to a 17 fluid source. In another aspect, the controller electrically urges the electro-hydraulic valve 18 from a closed position to at least a partially open position. In a different aspect, the fluid 19 source is fluidly coupled to the control valve when the electro-hydraulic valve is disposed in 20 at least the partially open position. In a further aspect, the electro-hydraulic valve is biased in 21 a closed position. In an alternative aspect, the control system includes a spring for biasing 22 the control valve to a first position, where in the first position the control valve fluidly 23 controls the motor to minimum displacement. 24 In yet a further aspect of this embodiment, the motor is configured to receive a load 25 from the track system, and based on the load, the motor sends a load pressure signal to the 26 control valve that at least partially compresses the spring. Moreover, the electro-hydraulic 27 valve sends an override fluid signal to the control valve, where the fluid signal and load 28 pressure signal hydraulically applies a pressure force against the control valve to vary the 29 displacement of the motor. In another aspect, the control system can include a motor 2 1 actuator fluidly coupled to the control valve, where a movement of the control valve induces 2 a corresponding movement of the motor actuator to vary the motor displacement. 3 In another embodiment of the present disclosure, a method is provided for varying the 4 start of control pressure of a variable displacement hydraulic motor adapted to drive a track 5 system of a machine. The machine includes user controls for controlling the functionality of 6 the machine, a controller in electrical communication with the user controls, a control valve 7 biased in a first position by a spring having a fixed spring force, and a proportional electro 8 hydraulic valve electrically coupled to the controller and fluidly coupled to the control valve. 9 The method includes sending an electrical signal to the electro-hydraulic valve, moving the 10 electro-hydraulic valve from a substantially closed position to at least a partially open 11 position, fluidly coupling the electro-hydraulic valve and control valve to one another, 12 controllably moving the control valve from the first position to a second position, and 13 varying the start of control pressure of the motor. 14 In one aspect of this embodiment, the varying step comprises fluidly controlling a 15 motor actuator. In another aspect, the method includes receiving an input from the user 16 controls, the input being related to a desired function of the machine, and operably 17 controlling the control valve based on the input. In a different aspect, the controllably 18 moving step comprises applying a hydraulic force to the control valve, the hydraulic force 19 including a fluid pressure from the electro-hydraulic valve and a load pressure from the 20 motor, compressing the spring, and moving the control valve to induce a change in motor 21 displacement. In an alternative aspect, the method includes providing the motor with a fixed 22 setting for controlling motor displacement and a plurality of displacement profiles, each of 23 the displacement profiles being a function of load on the motor and machine speed, 24 controlling the motor according to one of the plurality of displacement profiles, sending a 25 signal to override the fixed setting of the motor, and variably adjusting the motor to operate 26 according to a second of the plurality of displacement profiles. 27 In a different embodiment of the present disclosure, a method is provided for varying 28 a start of control pressure of a variable displacement hydraulic motor for driving a machine. 29 The machine includes operator controls for controlling the operation of the machine, a 30 controller in electrical communication with the operator controls, a control valve biased in a 3 1 first position and disposed in fluid communication with the motor, and an electro-hydraulic 2 valve electrically coupled to the controller and fluidly coupled to the control valve. The 3 method includes receiving an input signal from the operator controls, where the input signal 4 corresponds to a desired machine operation. An electrical signal is sent to the electro 5 hydraulic valve based on the input signal. The method also includes fluidly coupling the 6 electro-hydraulic valve and control valve to one another, controllably moving the control 7 valve from the first position to a second position based on the electrical signal, and varying 8 the start of control pressure of the motor in accordance with the desired machine operation. 9 In one aspect of this embodiment, the method includes increasing the start of control 10 pressure in accordance with an input signal corresponding to a desired increase in machine 11 speed. In another aspect, the method includes decreasing the start of control pressure in 12 accordance with an input signal corresponding to a desired increase in machine multi 13 functionality. In a different aspect, the method includes varying the start of control pressure 14 from a first pressure to a second pressure and controlling the machine at a maximum speed 15 and the motor at a minimum displacement. Here, the first pressure is less than the second 16 pressure. 17 In a further aspect, the method includes providing the motor with a plurality of 18 displacement profiles, where the plurality of displacement profiles includes a first 19 displacement profile having a first start of control pressure and a second displacement profile 20 having a second start of control pressure, the first start of control pressure corresponding to a 21 first machine performance profile and the second start of control pressure corresponding to a 22 second machine performance profile. This aspect also includes receiving the input signal 23 from the operator controls to adjust machine performance to correspond to either the first 24 machine performance or the second machine performance and varying the start of control 25 pressure to the first start of control pressure or the second start of control pressure. In a 26 related aspect, the method includes varying the start of control pressure to the first start of 27 control pressure to achieve greater machine functionality or to the second start of control 28 pressure to achieve greater machine speed as load pressure on the motor increases, wherein 29 the first start of control pressure is less than the second start of control pressure. 30 4 1 Brief Description of the Drawin2s 2 The above-mentioned aspects of the present disclosure and the manner of obtaining 3 them will become more apparent and the disclosure itself will be better understood by 4 reference to the following description of the embodiments of the disclosure, taken in 5 conjunction with the accompanying drawings, wherein: 6 Figure 1 is a side perspective view of a tracked feller buncher; 7 Figure 2 is a control schematic for a work machine; 8 Figure 3 is another control schematic for controlling a hydraulic motor displacement; 9 Figure 4 is a graphical view of different motor displacement profiles during machine 10 operation; and 11 Figure 5 is a graphical representation of continuously adjustably controlling motor 12 displacement during machine operation. 13 Corresponding reference numerals are used to indicate corresponding parts 14 throughout the several views. 15 16 Detailed Description 17 The embodiments of the present disclosure described below are not intended to be 18 exhaustive or to limit the disclosure to the precise forms in the following detailed description. 19 Rather, the embodiments are chosen and described so that others skilled in the art may 20 appreciate and understand the principles and practices of the present disclosure. 21 Referring to Figure 1, an exemplary embodiment of a machine, such as a feller 22 buncher 100, is shown. The machine 100 can include an upper frame assembly 102 which is 23 supported by an undercarriage assembly 104. A boom assembly 112 has a first end which is 24 pivotally coupled to the upper frame assembly 102 and a second end which has a work 25 implement secured thereto such as a cutting head 116 for sawing and bunching trees. The 26 upper frame assembly 102 can include a cab 106 in which an operator utilizes a plurality of 27 controls (e.g., joysticks, pedals, buttons, screens, etc.) for controlling the machine 100 during 28 operation thereof. The upper frame assembly 102 can also include an engine compartment 29 114 that houses an engine such as a diesel engine which provides the motive power for 30 operating the components associated with the machine 100. Both the cab 106 and the engine 5 1 compartment 114 can be supported by various frame members that form the upper frame 2 assembly 102. 3 The undercarriage assembly 104 can include a first track 108 and a second track 110 4 that engage and move along the ground during operation. The first track 108 and second 5 track 110 can be driven by a drive sprocket (not shown) and a front idler wheel (not shown) 6 about which a track chain (not shown) is entrained. As will be described, a hydraulic motor 7 can operably drive the drive sprocket (which may form part of a high reduction gearset) so as 8 to drive the track chain (not shown) thereby providing motive power for moving the machine 9 100. 10 The upper frame assembly 102 can be mechanically coupled to the undercarriage 11 assembly 104 by a tilt mechanism and turntable assembly 118. The tilt mechanism and 12 turntable assembly 118 can operably control the machine 100 to be rotated and tilted about 13 one or more axes. 14 With reference to Figure 2, an embodiment of a control scheme for a tracked machine 15 200 (e.g., a feller buncher or harvester) is shown. The machine 200 includes an engine 202 16 that can be hydraulically coupled to a hydraulic pump 204. The hydraulic pump 204 can 17 deliver fluid to a main valve 230 for hydraulically controlling different machine elements. 18 The machine 200 also includes both a first side and a second side. On the first side, the 19 machine 200 can include a first hydraulic drive motor 214 that is operably coupled to a high 20 reduction planetary gearbox 218. The gearbox 218 may include a drive sprocket (not shown) 21 or similar mechanism that is coupled to a chain 222 or belt for rotatably driving an idler 22 wheel or disc 220. The chain 222 can be operably coupled to a track upon which the 23 machine can move forward and backward. 24 Similarly, on the second or opposite side, the machine 200 can include a second 25 hydraulic drive motor 216 that is operably coupled to a high-reduction planetary gearbox 26 224. The gearbox 224 may include a drive sprocket (not shown) or similar mechanism that is 27 coupled to a chain 228 or belt for rotatably driving an idler wheel or disc 226. In conjunction 28 with the first hydraulic drive motor 214, the second hydraulic drive motor 216 can move the 29 machine 200 in a forward or reverse direction. 30 In Figure 2, the drive motors 214, 216 can be supplied with hydraulic fluid from the 6 1 hydraulic pump 204 via the main valve 230. The main valve 230 can include different 2 channels or flow paths for directing fluid to both drive motors. Moreover, the main valve 3 230 can direct fluid to one or more hydraulic cylinders (not shown) for operating a boom 4 assembly, work implement, swing the upper frame assembly 102 relative to the undercarriage 5 assembly 104 (Figure 1), and perform other functions of the machine. In other words, 6 hydraulic fluid supplied by the hydraulic pump 204 can be distributed throughout the 7 machine for performing the different functions of the machine. 8 As also shown in Figure 2, the machine 200 can include operator controls 208 for 9 operating the machine 200. An operator can maneuver a joystick, press a pedal, push a 10 button, or utilize other controls for achieving desired functionality of the machine 200. In 11 doing so, the operator controls 208 can be in electrical communication or coupled to a 12 machine controller 210. The machine controller 210 can operably control the functionality of 13 the machine 200. For instance, different software algorithms or programs can be 14 downloaded to and readable by the controller 210 for controlling the machine 200. Some of 15 the steps taken by the controller 210 to control the machine 200 may be as a result of 16 different inputs by the machine operator to the operator controls 208, which in turn provides 17 a signal to the controller 210. The controller 210 can interpret the type of control being made 18 by the operator, and different actions can be taken by the controller 210 as a result of this 19 control. As will be described in further detail, an electro-hydraulic valve 212 can be 20 disposed in communication with the controller 210 and further in hydraulic communication 21 with the hydraulic motors 214, 216. 22 The drive motors in Figure 2 can be a variable displacement hydraulic motor, such 23 that variable speeds can be achieved based on a given amount of flow. The motor 24 displacement can be controlled between a minimum or low displacement and a maximum or 25 high displacement. The minimum displacement of the motor can correspond to an actual 26 minimum motor displacement or to a desired displacement value mechanically set by an 27 operator, for example. At minimum displacement, the motor can operate so that the machine 28 achieves maximum or high speed. On the other hand, at maximum displacement, greater 29 torque can be achieved but at a lower machine speed. In one method of operation, the motor 30 control can be set to maintain the motor at or near minimum displacement so that the 7 1 machine can operate at a higher speed. This, however, can change as the machine encounters 2 difficult terrain, contacts a tree stump, ascends an elevation or other similar event that causes 3 a load pressure induced on the motor to increase. This increased load pressure is a function 4 of an increased load applied to the tracks of the machine. As the load pressure increases, a 5 threshold or predetermined load pressure, or a "start of control" pressure, can be reached to 6 change or modify the motor displacement. An example of this is shown in Figure 4. 7 Referring to Figure 4, a graphical illustration 400 of a plurality of motor displacement 8 profiles are shown plotted as a function of travel slope and machine speed. As shown, on the 9 far left portion of the graph is minimum displacement 402 and maximum speed of the 10 machine, whereas on the far right portion of the graph is maximum displacement 404 and 11 minimum speed of the machine. As described, the motor control can be set so that the motor 12 operates at or near minimum displacement so that the machine can travel at high speed. The 13 start of control pressure or threshold at which the motor displacement begins to vary, 14 however, is mechanically set (or fixed). 15 In Figure 4, for example, a first profile 406 can have a first start of control pressure or 16 threshold 414. As the machine travels along an increased slope, the load on the tracks 17 increases thereby inducing a greater load pressure on the motor. Once the load pressure 18 reaches the first start of control pressure or threshold 414, the motor control begins to swivel 19 the motor from minimum displacement to increase torque to ascend the slope albeit at a 20 reduced machine speed. Motor displacement continues to vary until it reaches maximum 21 displacement 422 along the first profile 406. As noted, this corresponds to the minimum 22 speed 404 of the machine. 23 The same can be held for a second profile 408 having a second start of control 24 pressure 416 or threshold, a third profile 410 having a third start of control pressure 418 or 25 threshold, and a fourth profile 412 having a fourth start of control pressure 420 or threshold. 26 With respect to the second profile 408, for example, the motor operates at minimum 27 displacement until the load pressure overcomes the start of control pressure 416 point on the 28 profile and then the motor displacement begins to vary between minimum displacement 402 29 and maximum displacement 404. The motor reaches maximum displacement at point 424 30 along the second profile 408. Likewise, the motor reaches maximum displacement at point 8 1 426 along the third profile 410 and at point 428 along the fourth profile 428. At each of 2 points 424, 426, and 428, the machine is operating at its minimum speed. 3 As shown in Figure 4, the first profile 406 reaches its start of control pressure 414 at a 4 smaller slope compared to the second profile 408, third profile 410, and fourth profile 412. 5 Moreover, the first profile 406 also reaches maximum displacement 422, and hence 6 minimum machine speed, at a smaller slope than the second profile 408, third profile 410, 7 and fourth profile 412. 8 A given slope is defined by vertical line 430 in Figure 4. As shown, the first profile 9 406 crosses the vertical line 430 and reaches the defined slope at point 432. The second 10 profile 408 crosses the vertical line 430 and reaches the defined slope at point 434. Here, if a 11 motor is operating in accordance with the first displacement profile 406, the machine will be 12 travelling at a slower speed at the defined slope compared to the instance in which the motor 13 operates in accordance with the second displacement profile 408. Although individual points 14 are not specifically labelled in Figure 4, it is shown that a motor operating in accordance with 15 the third displacement profile 410 and fourth displacement profile 412 will allow the 16 machine to travel at higher speeds than if the motor were operating according to the first or 17 second profiles. Hence, if a machine operator desires to travel at the highest speed possible, 18 it is desirable for the motor to operate in accordance with the third or fourth displacement 19 profiles. Moreover, to do so, the start of control pressure must be set in accordance with 20 either profile. 21 As the machine ascends the slope, i.e., slope increases, additional torque is required to 22 drive the tracks along the ground and move the machine up the slope. To operate the 23 hydraulic motors and operably drive the tracks, hydraulic pressure is supplied to the motor. 24 With the machine have multi-functionality (e.g., boom control, swing control, work 25 implement control, etc.), and at least one function requiring hydraulic fluid from the pump, it 26 is desired to maintain a substantially constant difference of pressure over the hydraulic motor 27 so that the machine can maintain its multi-functionality. To maintain a substantially constant 28 difference of pressure, however, the motor displacement increases thereby causing machine 29 speed to be reduced as its torque is increased. 30 For travel purposes, and as previously described, operating along the fourth profile 9 1 412 is optimal because the machine can achieve the highest speed for a given slope. This, 2 however, may not be optimal for a machine to achieve multiple functions because the tracks 3 require the greatest amount of power from the engine and hydraulic pump, thereby reducing 4 or preventing the use of other machine functions. Similarly and as previously described, 5 operating along the first profile 406 may allow for additional machine functionality, but the 6 machine operates at the slowest speed for a given slope. Therefore, in many conventional 7 applications, the motor start of control pressure is mechanically fixed to one of the profiles 8 between the first profile 406 and fourth profile 412. With it being mechanically fixed, 9 however, it is difficult to change or modify the start of control pressure of the motor in most 10 conventional applications. 11 To further describe this aspect, in one non-limiting embodiment each hydraulic motor 12 of the machine can be set to operate along the second profile 408. Here, the profile 408 has a 13 start of control pressure 416 and a maximum displacement point 424 at which the machine 14 operates at minimum speed. For purposes of understanding the motor control, the motor can 15 operate at minimum displacement as the machine climbs the slope. However, assuming the 16 machine continues to climb and the load pressure on the motor continues to increase, the start 17 of control pressure is reached at point 416 in Figure 4. In other words, the load pressure hits 18 this start of control pressure threshold 416 and motor displacement begins to be regulated. 19 The motor control continues to regulate motor displacement as the machine climbs 20 the slope until maximum displacement is reached at point 424. Once point 424 is reached, 21 the machine can continue to climb but at its slowest speed. The machine can continue to 22 climb until another threshold point is reached at which the motor may require additional fluid 23 pressure to move any further. In some instances, i.e., when higher machine speed is desired, 24 it may be more beneficial to operate at a different profile. However, as previously described, 25 it can be difficult to adjust this mechanical setting on the motor. For example, a technician 26 may have to remove various covers and access the top portion of the machine to make any 27 adjustment. Therefore, the mechanical setting on the machine (i.e., to follow the second 28 profile 408 of Figure 4) can be set at a desired profile having a fixed start of control pressure 29 so that hydraulic pressures for other functions are not affected by machine operation. 30 The present disclosure, however, provides an alternative embodiment or aspect to the 10 1 control scheme previously described. More specifically, the present disclosure provides a 2 means for adjusting the start of control pressure or threshold in real-time so that optimal 3 machine performance can be achieved. Whereas in conventional applications this setting is 4 fixed and is difficult to change, the embodiments of the present disclosure can continuously 5 vary or adjust the start of control pressure so that the machine can operate at higher speeds 6 when desired and achieve greater machine functionality when desired. 7 Referring to Figures 2 and 3, a control system 300 is shown for controlling the start of 8 control pressure of a variable displacement hydraulic motor 302. The motor 302 can be the 9 same as the first hydraulic drive motor 214 and the second hydraulic drive motor 216 of 10 Figure 2. The motor 302 can transfer output torque to a gearbox 304 for driving a machine 11 forward and backward. The gearbox 304 in Figure 3 can be similar to the first gearbox 218 12 and second gearbox 224 of Figure 2. During machine travel, the motor 302 can operate at 13 minimum displacement. As the machine encounters a slope, stump, difficult terrain, etc., a 14 load 312 can be applied to the gearbox 304 which in turn is received by the motor 302. In 15 response to the load 312, a motor load pressure signal 314 can be transferred from the motor 16 (e.g., one of two fluid ports on the motor) to a control or servo valve 206 in the form of a 17 pressure load or force 316. The control or servo valve 206 can be internal to the motor 302, 18 or in other embodiments it can be disposed entirely or partially outside of the motor 302. 19 The motor load pressure signal 314 can be the pressure at which the motor works, and this 20 pressure varies based on different loads transferred to the motor 302. 21 The control valve 206 is in communication with the motor 302, as described with 22 reference to Figure 2. Moreover, the control valve 206 can be fluidly coupled to the motor 23 302 and transfer fluid to an actuator 306 internally disposed within the motor 302. The 24 actuator 306 can be in the form of a piston that is movably disposed within a cylinder. The 25 cylinder can have a first end 308 and a second end 310, where the piston moves 26 therebetween. When the piston is disposed at the first end 308, the motor is configured at 27 minimum displacement. When the piston is disposed at the second end 310, the motor is 28 configured at maximum displacement. To regulate the actuator 306 between minimum 29 displacement and maximum displacement, the control valve 206 can transfer fluid through a 30 first flow path 320 and a second flow path 322. In the arrangement shown in Figure 3, fluid 11 1 can pass through the first flow path 320 and fill the cylinder to urge the piston towards the 2 second end 310 (i.e., towards maximum displacement). Alternatively, fluid can flow through 3 the second flow path 322 and fill the cylinder to urge the piston towards the first end 308 4 (i.e., towards minimum displacement). 5 The manner in which the control valve 206 hydraulically controls the actuator 306, 6 and thereby regulates the displacement of the motor 302, is further shown in Figure 3. Here, 7 a spring 318 having a fixed spring constant is disposed in contact with one side of the control 8 valve 206. In this manner, the spring 318 can exert a spring force, Fsi, against the control 9 valve 206. The spring force, Fsi, can be opposed by the motor load pressure signal 314 10 which exerts a force 316 against a second side of the control valve 206. The first side and 11 second side of the control valve 206 can be defined as opposite sides of the valve. When the 12 spring force, Fsi, is greater than the motor load pressure signal force 316, the motor 302 can 13 be disposed at minimum displacement. However, as the load pressure signal force 316 14 overcomes or exceeds the spring force, Fsi, the control valve 206 can vary the motor 15 displacement. Here, the start of control point can be defined at the point in which the spring 16 force, FsI, is overcome by the motor load pressure signal force 316. Thus, motor 17 displacement can be controlled according to the type of spring and its corresponding spring 18 force. 19 The motor 302 can also include an external port 330 (port H) that is fluidly coupled to 20 a hydraulic tank in most applications, and therefore no fluid pressure is received at this port 21 330. However, in Figure 3, the external port 330 can be fluidly coupled to a proportional 22 reducing relieving valve 322, or the PRV valve. The PRV valve 322 can be fluidly coupled 23 to both a fluid source 326 (e.g., pressure source "P") and tank pressure 328 (e.g., tank "T"). 24 In this disclosure, the PRV valve 322 can also be referred to as an electro-hydraulic valve 25 similar to that of the valve 212 in Figure 2. The fluid source 326 can provide a constant 26 pressure signal from another portion of the hydraulic system of the machine. The PRV valve 27 322 can be mechanically disposed or biased in a closed position by a spring 324 that exerts a 28 spring force, Fs 2 , against the valve 322. In this case, the spring 324 substantially prevents or 29 blocks the PRV valve 322 from fluidly coupling the fluid source 326 and external port 330 to 30 one another. 12 1 The PRV valve 322 can also be disposed in electrical communication with the 2 machine controller 210. The machine controller 210 can send an electrical signal (e.g., 3 current) to induce a force against the PRV valve 322, thereby causing the PRV valve 322 to 4 at least partially open and releasing fluid to the external port 330. In turn, the fluid can pass 5 through the external port 330 and be directed to the control valve 206 along flow path 332. 6 As such, the control valve 206 is fluidly coupled to the external port 330 and the PRV valve 7 322. The fluid pressure passing through flow path 332 can exert a force against the control 8 valve 206 in the same direction as the motor load pressure signal force 316. As such, two 9 pressure signals exert a combined force against the control valve 206, which is opposed by 10 the fixed spring force, Fsi, as described above. In this manner, the equilibrium set between 11 the spring force, Fs 1 , and the motor load pressure signal 314 can be overridden or varied by 12 fluid pressure from the PRV valve 322. This, in turn, can require a lower pressure from the 13 motor load pressure signal 314 to cause the control valve 206 to vary or regulate the start of 14 control pressure of the motor. 15 As previously described, movement of the control valve 206 can hydraulically induce 16 movement of the actuator 306 to thereby vary motor displacement between its minimum and 17 maximum. In effect, this can modify or controllably adjust the speed and torque capability of 18 the motor. Moreover, the machine can be more adaptable under different and varying 19 operating conditions. In other words, the control system of the machine can induce a 20 proportional, hydraulic load via the controller 210 and the PRV valve 322 so that the 21 equilibrium or start of control pressure threshold can be varied to more easily override or 22 offset the fixed spring force. 23 In a related aspect, the controller 210 can be in electrical communication with the 24 operator controls 208 of the machine. Thus, as an operator manipulates a joystick, lever, or 25 other control button to operably control the machine, the controller 210 can interpret this 26 input from the operator and respond accordingly. Moreover, this response from the 27 controller 210 can be in the form of varying the start of control pressure of the motor (i.e., by 28 communicating a control signal to the PRV valve 322 to vary the amount of fluid pressure 29 transferred from the fluid source 326 to the control valve 206 via flow path 332). 30 Referring to Figure 5, a different graphical representation 500 is shown which 13 1 characterizes how continuously varying start of control pressure can affect motor 2 displacement as a function of travel slope and machine speed. Here, the hydraulic motor can 3 operate at a predetermined minimum displacement 502 as the machine begins to ascend a 4 slope. As previously described, the predetermined minimum displacement 502 may 5 correspond to the motor's actual minimum displacement setting, or alternatively it may 6 correspond to a setting that is defined by an operator which is greater than the motor's actual 7 minimum displacement. The motor can also operate at maximum displacement 504 as 8 shown in Figure 5. At minimum motor displacement 502, the machine can operate at or near 9 a maximum speed, whereas at maximum motor displacement 504 the machine tends to 10 operate at its slowest speed. 11 In Figure 5, the graphical representation 500 includes a first motor displacement 12 profile 506 and a second motor displacement profile 508 that is disposed offset to the right of 13 the first profile 506. A motor that operates according to the first profile 506 is one in which 14 the machine can travel at slow speeds at a given slope but achieve high multi-functionality, 15 whereas the second profile 508 represents a profile upon which the machine can travel at 16 higher speeds for a given slope but with limited multi-functionality capabilities. 17 The first profile 506 includes a first start of control pressure 510 and a first maximum 18 displacement point 514. Likewise, the second profile 508 includes a second start of control 19 pressure 512 and a second maximum displacement point 516, both of which are disposed to 20 the right of the first start of control pressure 510 and first maximum displacement point 514. 21 In addition, a given slope is identified by a vertical line 518 in Figure 5. The first profile 506 22 crosses this given slope 518 at a first point 520. The second profile 508 crosses this given 23 slope 518 at a second point 522. As shown, the machine operates at a slower speed for the 24 given slope 518 if the motor operates according to the first profile 506, whereas the machine 25 operates at a greater speed if the motor operates according to the second profile 508 (i.e., 26 point 520 of the first profile 506 corresponds to a slower speed than point 522 of the second 27 profile 508). 28 In accordance with the present disclosure, the additional variable override signal (i.e., 29 pilot signal) provided by the PRV or electro-hydraulic valve 322 allows the controller 210 to 30 continuously operate in real-time in a variable start of control region 524. The variable start 14 1 of control region 524 is defined between the first profile 506 and the second profile 508 of 2 Figure 5 based on desired machine functionality. In other words, the controller 210 can 3 continuously adjust or vary the start of control pressure based on a desired need so that the 4 motor can operate within the defined region 524. For instance, if the machine operator wants 5 to operate at a higher speed and the controller 210 interprets this desire via the operator 6 controls 208, the controller can send an electrical signal to the PRV valve 322 to induce a 7 pressure load to the control valve 206 to vary or offset the start of control pressure of the 8 motor towards the second start of control pressure 512, thereby allowing the machine to 9 operate at or near its maximum speed as it continues to ascend a slope. In other words, the 10 motor may operate within the region 524 in a manner corresponding to the second profile 11 512 of Figure 5. 12 If the operator desires to cut down a tree or needs greater functionality from the 13 machine, the controller can receive this input from the operator controls 208 and induce a 14 similar signal to the PRV valve 322. Here, the motor may operate within the region 524 15 closer to the first profile 506. Based on the control and functionality desired from the 16 machine, the controller 210 can continuously vary the pressure signal sent to the control 17 valve 206, which in turn can override or adjust the start of control pressure of the motor as 18 necessary. 19 Various embodiments of the present disclosure allows for the implementation of a 20 variable start of control for the variable displacement hydraulic motors used for the track 21 system on a forestry machine. This can provide for better machine performance under 22 different terrain and machine operations, and the machine is better able to adapt to changing 23 conditions in the terrain and machine functionality. Moreover, the control system of the 24 machine is better able to increase machine productivity, meet operator demands, optimize 25 fuel consumption, and reduce operator fatigue by adapting the track characteristics to the 26 machine working cycle. 27 While exemplary embodiments incorporating the principles of the present disclosure 28 have been described hereinabove, the present disclosure is not limited to the described 29 embodiments. Instead, this application is intended to cover any variations, uses, or 30 adaptations of the disclosure using its general principles. Further, this application is intended 15 1 to cover such departures from the present disclosure as come within known or customary 2 practice in the art to which this disclosure pertains and which fall within the limits of the 3 appended claims. 4 Throughout this specification and the claims which follow, unless the context requires 5 otherwise, the word "comprise", and variations such as "comprises" or "comprising", will be 6 understood to imply the inclusion of a stated integer or step or group of integers or steps but 7 not the exclusion of any other integer or step or group of integers or steps. 8 The reference in this specification to any prior publication (or information derived 9 from it), or to any matter which is known, is not, and should not be taken as, an 10 acknowledgement or admission or any form of suggestion that that prior publication (or 11 information derived from it) or known matter forms part of the common general knowledge 12 in the field of endeavour to which this specification relates. 13 14 16
    权利要求:
    Claims (22)
    [1] 1. A control system of a powered machine, the machine having an engine for producing power and a track system for moving along a surface, comprising: a hydraulic motor configured to drive the track system, the motor being operable with a variable displacement; a control valve fluidly coupled to the motor; a controller; and an electro-hydraulic valve disposed in electrical communication with the controller and fluid communication with the control valve; wherein, the electro-hydraulic valve receives a signal from the controller, and based on the signal, the electro-hydraulic valve hydraulically varies the start of control pressure of the motor.
    [2] 2. The control system of claim 1, wherein the electro-hydraulic valve is fluidly coupled to a fluid source.
    [3] 3. The control system of claim 2, wherein the controller electrically urges the electro hydraulic valve from a closed position to at least a partially open position.
    [4] 4. The control system of claim 3, wherein the fluid source is fluidly coupled to the control valve when the electro-hydraulic valve is disposed in at least the partially open position.
    [5] 5. The control system of claim 1, wherein the electro-hydraulic valve is biased in a closed position. 17
    [6] 6. The control system of claim 1, further comprising a spring for biasing the control valve to a first position, where in the first position the control valve fluidly controls the motor to minimum displacement.
    [7] 7. The control system of claim 6, wherein the motor is configured to receive a load from the track system, and based on the load, the motor sends a load pressure signal to the control valve that at least partially compresses the spring.
    [8] 8. The control system of claim 7, wherein the electro-hydraulic valve sends an override fluid signal to the control valve, the fluid signal and load pressure signal hydraulically applying a pressure force against the control valve to vary the displacement of the motor.
    [9] 9. The control system of claim 7, further comprising a motor actuator fluidly coupled to the control valve, where a movement of the control valve induces a corresponding movement of the motor actuator to vary the motor displacement.
    [10] 10. A method for varying the start of control pressure of a variable displacement hydraulic motor adapted to drive a track system of a machine, the machine including user controls for controlling the functionality of the machine, a controller in electrical communication with the user controls, a control valve biased in a first position by a spring having a fixed spring force, and a proportional electro-hydraulic valve electrically coupled to the controller and fluidly coupled to the control valve, the method comprising: sending an electrical signal to the electro-hydraulic valve; moving the electro-hydraulic valve from a substantially closed position to at least a partially open position; fluidly coupling the electro-hydraulic valve and control valve to one another; controllably moving the control valve from the first position to a second position; and varying the start of control pressure of the motor. 18
    [11] 11. The method of claim 10, wherein the varying step comprises fluidly controlling a motor actuator.
    [12] 12. The method of claim 10, further comprising: receiving an input from the user controls, the input related to a desired function of the machine; and operably controlling the control valve based on the input.
    [13] 13. The method of claim 10, wherein the controllably moving step comprises: applying a hydraulic force to the control valve, the hydraulic force including a fluid pressure from the electro-hydraulic valve and a load pressure from the motor; and compressing the spring; and moving the control valve to induce a change in motor displacement.
    [14] 14. The method of claim 10, further comprising: providing the motor with a fixed setting for controlling motor displacement and a plurality of displacement profiles, each of the displacement profiles being a function of load on the motor and machine speed; controlling the motor according to one of the plurality of displacement profiles; sending a signal to override the fixed setting of the motor; and variably adjusting the motor to operate according to a second of the plurality of displacement profiles.
    [15] 15. A method for varying a start of control pressure of a variable displacement hydraulic motor for driving a machine, the machine including operator controls for controlling the operation of the machine, a controller in electrical communication with the operator controls, a control valve biased in a first position and disposed in fluid communication with the motor, and an electro-hydraulic valve electrically coupled to the controller and fluidly coupled to the control valve, the method comprising: 19 receiving an input signal from the operator controls, where the input signal corresponds to a desired machine operation; sending an electrical signal to the electro-hydraulic valve based on the input signal; fluidly coupling the electro-hydraulic valve and control valve to one another; controllably moving the control valve from the first position to a second position based on the electrical signal; and varying the start of control pressure of the motor in accordance with the desired machine operation.
    [16] 16. The method of claim 15, further comprising increasing the start of control pressure in accordance with an input signal corresponding to a desired increase in machine speed.
    [17] 17. The method of claim 15, further comprising decreasing the start of control pressure in accordance with an input signal corresponding to a desired increase in machine multi functionality.
    [18] 18. The method of claim 15, further comprising: varying the start of control pressure from a first pressure to a second pressure; and controlling the machine at a maximum speed and the motor at a minimum displacement; wherein, the first pressure is less than the second pressure.
    [19] 19. The method of claim 15, further comprising: providing the motor with a plurality of displacement profiles, where the plurality of displacement profiles includes a first displacement profile having a first start of control pressure and a second displacement profile having a second start of control pressure, the first start of control pressure corresponding to a first machine performance characteristic and the second start of control pressure corresponding to a second machine performance characteristic; 20 receiving the input signal from the operator controls to adjust machine performance to correspond to either the first machine performance characteristic or the second machine performance characteristic; and varying the start of control pressure to the first start of control pressure or the second start of control pressure.
    [20] 20. The method of claim 19, further comprising: varying the start of control pressure to the first start of control pressure to achieve greater machine functionality or to the second start of control pressure to achieve greater machine speed as load pressure on the motor increases; wherein, the first start of control pressure is less than the second start of control pressure.
    [21] 21. A control system of a powered machine, substantially as hereinbefore described with reference to the accompanying figures.
    [22] 22. A method for varying the start of control pressure of a variable displacement hydraulic motor, substantially as hereinbefore described with reference to the accompanying figures. 21
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    同族专利:
    公开号 | 公开日
    US20140208934A1|2014-07-31|
    CA2809481A1|2014-07-29|
    BR102013007709A2|2015-07-28|
    CA2809481C|2018-10-16|
    US9518655B2|2016-12-13|
    CN103963635A|2014-08-06|
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    法律状态:
    2016-07-28| MK5| Application lapsed section 142(2)(e) - patent request and compl. specification not accepted|
    优先权:
    申请号 | 申请日 | 专利标题
    US13/752,752||2013-01-29||
    US13/752,752|US9518655B2|2013-01-29|2013-01-29|Continuously adjustable control management for a hydraulic track system|
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