Patent Application
20150308469
The present disclosure relates generally to a machine control system, and more particularly, to a machine control system having a hydraulic warmup procedure.
Hydraulic machines such as, for example, dozers, loaders, excavators, motor graders, and other types of heavy equipment use one or more hydraulic actuators to accomplish a variety of tasks. These actuators are fluidly connected to a pump on the machine that provides pressurized fluid to chambers within the actuators. As the pressurized fluid moves into or through the chambers, the pressure of the fluid acts on hydraulic surfaces of the chambers to affect movement of the actuator and a connected work tool. When the pressurized fluid is drained from the chambers it is returned to a low pressure sump on the machine.
One problem associated with this type of hydraulic arrangement involves starting or operation of the machine when temperatures are low. Specifically, if the fluid used to move the actuators and/or associated valves is too cold, operation of the machine can become unpredictable and sluggish. In addition, cold operation or improper warming of the machine's components could result in damage to the machine. Thus, a warmup procedure may be useful prior to operation of the machine and the work tool.
One such warmup procedure is described in U.S. Pat. No. 5,410,878 (the '878 patent) issued to Lee et al. on May 2, 1995. Specifically, the '878 patent describes a hydraulic system equipped with an engine and a hydraulic pump driven by the engine and controlled by a microcomputer. The hydraulic system also includes a hydraulic actuator operated by pressurized oil discharged from the hydraulic pump, a valve disposed between the hydraulic pump and the hydraulic actuator, a first temperature sensor configured to detect a temperature of a lubricant oil within the engine, a second temperature sensor configured to detect a temperature of a cooling water within the engine, and a third temperature sensor configured to detect a temperature of the oil pressurized by the hydraulic pump.
During operation of the hydraulic system of the '878 patent, the microcomputer monitors the temperatures of the lubricant oil, the cooling water, and the pressurized oil to determine if warmup is necessary. When warmup is necessary, the microcomputer increases a rotational speed of the engine to a predetermined rotational speed, and then slowly adjusts a discharge oil amount and a pressure of the hydraulic pump and the valve until a load on the engine reaches a predetermined amount. The microcomputer continues to monitor the lubricant oil, cooling water, and pressurized oil temperatures and, after these temperatures reach predetermined values, operation of the engine, the pump, and the valve is returned to a low-idling operation.
Although the hydraulic system and method disclosed within the '878 patent may be helpful in warming a hydraulic system, the benefit thereof may be minimal. Specifically, although the fluid within the hydraulic system may be sufficiently warmed, the associated valves may remain too cold for proper operator or be heated at a rate that results in sticking or damage of the valves.
The disclosed machine control system is directed to overcoming one or more of the problems set forth above and/or other problems of the prior art.
In one example, a machine control system is provided. A pump is driven to pressurize fluid. A low pressure reservoir is provided, and at least one actuator connected to receive fluid pressurized by the pump and discharge fluid to the low pressure reservoir. A bypass passage is situated to allow fluid pressurized by the pump to bypass the at least one actuator and flow to the low pressure reservoir. A warmup valve is disposed within the bypass passage and movable between a flow-passing position and a flow-blocking position. A hydraulic temperature sensor is configured to generate a signal indicative of a temperature of the fluid. A pressure sensor is associated with the at least one actuator and configured to generate a signal indicative of a pressure of the fluid. A controller is in communication with the pump, the warmup valve, the hydraulic temperature sensor, and the pressure sensor. The controller is configured to move the warmup valve to the flow-passing position, fix a displacement position of the pump, and compare the pressure of the fluid of the at least one actuator with a pressure threshold, and move the warmup valve to a flow-blocking position and reduce a pump outlet pressure when the pressure of the fluid is greater than the pressure threshold.
In another example, a method of warming a machine control system is disclosed. The steps can include one or more of the following, including pressurizing a fluid with a pump; directing pressurized fluid to an actuator; determining a temperature of the fluid; and determining a pressure of the fluid. In response to the sensed temperature, the steps can include selectively directing pressurized fluid to bypass the actuator, fixing the displacement amount, and comparing the pressure of the fluid of the actuator with a pressure threshold, moving the warmup valve to a flow-blocking position and reducing an outlet pressure of the pump when the pressure of the fluid is greater than the pressure threshold.
In yet another example, a machine includes an engine, an engine temperature sensor configured to generate an engine temperature signal indicative of a temperature of the engine, a pump driven by the engine to pressurize fluid, a low pressure reservoir, a work tool, and at least one actuator connected to receive fluid pressurized by the pump and discharge fluid to the low pressure reservoir to move the work tool. A valve stack is provided having a supply passage fluidly connected to the pump, a drain passage fluidly connected to the drain passage, at least one control valve fluidly connected between the supply and the drain passages and being configured to selectively regulate fluid flow to and from the at least one actuator. A bypass passage fluidly connects the supply and drain passages, and a warmup valve is disposed within the bypass passage and movable between a flow-passing position and a flow-blocking position. A hydraulic temperature sensor is configured to generate a hydraulic temperature signal indicative of a temperature of the fluid. A pressure sensor is associated with the at least one actuator and configured to generate a signal indicative of a pressure of the fluid. A controller is in communication with the engine, the engine temperature sensor, the pump, the warmup valve, and the hydraulic temperature sensor. The controller is configured to move the warmup valve to the flow-passing position, fix a displacement position of the pump, compare the pressure of the fluid of the at least one actuator with a pressure threshold, and move the warmup valve to a flow-blocking position when the pressure of the fluid is greater than the pressure threshold.
Implement system 12 may include a linkage structure acted on by fluid actuators to move work tool 14. Specifically, implement system 12 may include a boom member 22 vertically pivotal about a horizontal axis (not shown) relative to a work surface 24 by a pair of adjacent, double-acting, hydraulic cylinders 26 (only one shown in
Each of hydraulic cylinders 26, 32, 34 may include a tube and a piston assembly (not shown) arranged to form two separated pressure chambers. The pressure chambers may be selectively supplied with pressurized fluid and drained of the pressurized fluid to cause the piston assembly to displace within the tube, thereby changing an effective length of hydraulic cylinders 26, 32, 34. The flow rate of fluid into and out of the pressure chambers may relate to a velocity of hydraulic cylinders 26, 32, 34, while a pressure differential between the two pressure chambers may relate to a force imparted by hydraulic cylinders 26, 32, 34 on the associated linkage members. The expansion and retraction of hydraulic cylinders 26, 32, 34 may function to assist in moving work tool 14.
Numerous different work tools 14 may be attachable to a single machine 10 and controllable by an operator of machine 10. Work tool 14 may include any device used to perform a particular task such as, for example, a bucket, a fork arrangement, a blade, a shovel, a ripper, a dump bed, a broom, a snow blower, a propelling device, a cutting device, a grasping device, or any other task-performing device known in the art. Although connected in the embodiment of
Drive system 16 may include one or more traction devices used to propel machine 10. In one example, drive system 16 includes a left track 40L located on one side of machine 10, and a right track 40R located on an opposing side of machine 10. Left track 40L may be driven by a left travel motor 42L, while right track 40R may be driven by a right travel motor 42R. It is contemplated that drive system 16 could alternatively include traction devices other than tracks such as wheels, belts, or other known traction devices, if desired.
Each of left and right travel motors 42L, 42R may be driven by creating a fluid pressure differential. Specifically, each of left and right travel motors 42L, 42R may include first and second chambers (not shown) located to either side of an impeller (not shown). When the first chamber is filled with pressurized fluid and the second chamber is drained of fluid, the impeller may be urged to rotate in a first direction. Conversely, when the first chamber is drained of the fluid and the second chamber is filled with the pressurized fluid, the respective impeller may be urged to rotate in a second direction opposite the first direction. The flow rate of fluid into and out of the first and second chambers may relate to a rotational velocity of left and right travel motors 42L, 42R, while a pressure differential between left and right travel motors 42L, 42R may relate to a torque.
Power source 18 may embody an engine such as, for example, a diesel engine, a gasoline engine, a gaseous fuel-powered engine, or any other type of combustion engine known in the art. It is contemplated that power source 18 may alternatively embody a non-combustion source of power such as a fuel cell, a power storage device, or another source known in the art. Power source 18 may produce a mechanical or electrical power output that may then be converted to hydraulic power for moving hydraulic cylinders 26, 32, 34 and left and right travel motors 42L, 42R.
As illustrated in
First and second sources 51, 53 may draw fluid from one or more tanks 64 and pressurize the fluid to predetermined levels. Specifically, each of first and second sources 51, 53 may embody a pumping mechanism such as, for example, a variable displacement pump. First and second sources 51, 53 may each be separately and drivably connected to an output rotation power source 18 of machine 10 by, for example, a countershaft (not shown), a belt (not shown), an electrical circuit (not shown), or in any other suitable manner Alternatively, each of first and second sources 51, 53 may be indirectly connected to power source 18 via a torque converter, a reduction gear box, or in another suitable manner In this manner, for a fixed displacement amount, an input speed of first and second sources 51, 53 (i.e., an output speed of power source 18) may be controllably varied to adjust a displacement rate (i.e., a discharge flow rate) of first and second sources 51, 53. And, for a given input speed, the displacement amounts of first and second sources 51, 53 may be independently varied to adjust their respective displacement rates. Thus, the first and second streams of pressurized fluids may be produced by first and second sources 51, 53, respectively, to have different pressure levels and/or flow rates. It is contemplated that only a single source may alternatively provide pressurized fluid to both first and second circuits 50, 52, if desired.
Tank 64 may constitute a low-pressure reservoir configured to hold a supply of fluid. The fluid may include, for example, a dedicated hydraulic oil, an engine lubrication oil, a transmission lubrication oil, or any other fluid known in the art. One or more hydraulic systems within machine 10 may draw fluid from and return fluid to tank 64. It is contemplated that machine control system 48 may be connected to multiple separate fluid tanks or to a single tank.
Each of boom, bucket, left travel, right travel, and stick control valves 54, 56, 58, 60, 62 may regulate the motion of their associated fluid actuators. Specifically, boom control valve 54 may have elements movable to control the motion of hydraulic cylinders 26 associated with boom member 22, bucket control valve 56 may have elements movable to control the motion of hydraulic cylinder 34 associated with work tool 14, and stick control valve 62 may have elements movable to control the motion of hydraulic cylinder 32 associated with stick member 28. Likewise, left travel control valve 58 may have valve elements movable to control the motion of left travel motor 42L, while right travel control valve 60 may have elements movable to control the motion of right travel motor 42R.
The control valves of first and second circuits 50, 52 may be connected to regulate flows of pressurized fluid to and from their respective actuators via common passages. Specifically, the control valves of first circuit 50 may be connected to first source 51 by way of a first common supply passage 66 that extends along one side of valve stack 49, and to tank 64 by way of a first common drain passage 68 extending along a side of valve stack 49 opposite first common supply passage 66. Similarly, the control valves of second circuit 52 may be connected to second source 53 by way of a second common supply passage 70 that extends along one side of valve stack 49, and to tank 64 by way of a second common drain passage 72 that extends along a side of valve stack 49 opposite second common supply passage 70. Boom, bucket, and left travel control valves 54, 56, 58 may be connected in parallel to first common supply passage 66 by way of individual fluid passages 74, 76, and 78, respectively, and in parallel to first common drain passage 68 by way of individual fluid passages 84, 86, and 88, respectively. Similarly, right travel and stick control valves 60, 62 may be connected in parallel to second common supply passage 70 by way of individual fluid passages 82 and 80, respectively, and in parallel to second common drain passage 72 by way of individual fluid passages 90 and 92, respectively. A check valve 94 may be disposed within each of fluid passages 74, 76, and 80 to provide for a unidirectional supply of pressurized fluid to control valves 54, 56, and 62, respectively.
Because the elements of boom, bucket, left travel, right travel, and stick control valves 54, 56, 58, 60, 62 may be similar and function in a related manner, only the operation of boom control valve 54 will be discussed in this disclosure. In one example, boom control valve 54 may include a first chamber supply element (not shown), a first chamber drain element (not shown), a second chamber supply element (not shown), and a second chamber drain element (not shown). The first and second chamber supply elements may be connected in parallel with fluid passage 74 to fill their respective chambers with fluid from first source 51, while the first and second chamber drain elements may be connected in parallel with fluid passage 84 to drain the respective chambers of fluid. To extend hydraulic cylinders 26, the first chamber supply element may be moved to allow the pressurized fluid from first source 51 to fill the first chambers, e.g, the head end chambers, of hydraulic cylinders 26 with pressurized fluid via fluid passage 74, while the second chamber drain element may be moved to drain fluid from the second chambers, e.g., the rod end chambers, of hydraulic cylinders 26 to tank 64 via fluid passage 84. To move hydraulic cylinders 26 in the opposite direction, the second chamber supply element may be moved to fill the second chambers of hydraulic cylinders 26 with pressurized fluid, while the first chamber drain element may be moved to drain fluid from the first chambers of hydraulic cylinders 26. It is contemplated that both the supply and drain functions may alternatively be performed by a single element associated with the first chamber and a single element associated with the second chamber, or by a single valve that controls all filling and draining functions.
A pressure sensor 83a or 83b may be associated with at least one of the hydraulic cylinders 26, 32, 34 (shown as cylinder 26) and configured to generate signals indicative of a pressure of fluid within the associated cylinder, if desired. In the disclosed embodiment, the pressure sensors 83a and/or 83b may be disposed along the fluid lines extending from and/or to the respective control valve. It is contemplated, however, that the pressure sensor 83a,b may alternatively be disposed along a bypass passage 109 and/or 113, if desired. Signals from the pressure sensor 83a and/or 83b may be directed to controller 112 for use in regulating operation of the warmup function, as will be further described. Additionally, the pressure sensor may be associated with the cylinder in a variety of manners, such that any of the chambers of each cylinder has its own pressure sensor(s). In one example, a first pressure sensor 83a may be associated with a head end chamber of the hydraulic cylinder, and a second pressure sensor 83b may be associated with a rod end chamber of the hydraulic cylinder. A pump pressure sensor 87 may be associated with at least one of the first and second sources 51, 53 (shown at first source 51) and configured to generate signals indicative of a pump discharge pressure of fluid pressurized by the corresponding source. Signals from the pressure sensor 87 may be directed to controller 112 for use in regulating operation of the warmup function, as will be further described.
A bypass valve 85 may be configured to regulate a flow of pressurized fluid to tank 64. The bypass valve can be configured to facilitate in the provision of a desired feedback to an operator. The bypass valve 85 may be disposed downstream of first source 51 and/or, in another example (not shown), a second bypass valve may be disposed downstream of second source 53. The bypass valve 85 may include a spring biased valve stem supported in a valve bore. The valve stem may be solenoid actuated and configured to proportionally move between a first position at which a maximum fluid flow may be allowed to flow to tank 64 and a second position at which fluid flow may be substantially blocked from flowing to tank 64. Proportional movement of the valve stem between the first position and the second position may allow a varying flow of pressurized fluid to flow to tank 64. It is contemplated that the proportional valve stem may vary the flow of pressurized fluid in any manner known in the art, such as, for example, non-linearly or linearly. It is also contemplated that the bypass valve 85 may alternatively be hydraulically actuated, mechanically actuated, pneumatically actuated, or actuated in any other suitable manner. It is also contemplated that the bypass valve 85 may alternatively be spring biased to a position at which a flow of pressurized fluid is substantially blocked from flowing to tank 64. It is further contemplated that the quantity of bypass valves may be equal to the quantity of sources of pressurized fluid. It is noted that the amount of the flow of pressurized fluid directed to tank 64 by the bypass valve 85 may functionally reduce the pressure supplied to first and/or second circuits 50, 52 by first and second sources 51, 53. When bypass valve is electronically controlled, signals from the controller 112 may be directed to the solenoid for use in regulating operation of the warmup function, as will be further described.
The common supply and drain passages 66,70, 68, 72 of first and second circuits 50, 52 may be interconnected for relief functions. In particular, first and second common drain passages 68, 72 may relieve fluid from first and second circuits 50, 52 to tank 64 during normal operation. However, as fluid within first or second circuits 50, 52 exceeds a maximum acceptable pressure level, fluid from the circuit having the excessive pressure may also drain to tank 64 by way of supply passages 66, 70, a shuttle valve 102, and a common main relief element 104. It is contemplated that common supply passages 66, 70 of first and second circuits 50, 52 may similarly be interconnected for makeup functions, if desired.
Machine control system 48 may also include a warm-up circuit for use during startup and cold operations of machine 10. That is, common supply and drain passages 66, 68 and 70, 72 of first and second circuits 50, 52, respectively, may be selectively communicated via first and second bypass passages 109, 113 for warm-up and/or other bypass functions. A warmup valve 105 may be located in each of bypass passages 109, 113 and configured to direct fluid from common supply passages 66 and 70 to bypass control valves 54-62 and flow to tank 64 by way of common drain passages 68 and 72. Each warmup valve 105 may include a valve element movable from a closed or flow-blocking position to an open or flow-passing position. In this configuration, when warmup valve 105 is in the open position, such as during start up of machine 10, fluid pressurized by first and second sources 51, 53 may be allowed to circulate through first and second circuits 50, 52 without passing through control valves 54, 56, 58, 60, 62. Warmup valves 105 may be configured to provide a restriction on the flow of fluid passing therethrough to warm the fluid. In some embodiments, the restriction provided by warmup valves 105 may be variable. After the fluid has been sufficiently warmed, the valve elements of warmup valves 105 may be moved to the closed positions so that the pressure of the fluid within first and second circuits 50, 52 may build and be available for use by control valves 54, 56, 58, 60, 62, as described above
Machine control system 48 may further include a controller 112 configured to regulate operations of machine 10 during startup and cold conditions based on sensed parameters of power source 18 and machine control system 48. Controller 112 may be in communication with power source 18, first source 51, second source 53, and warmup valves 105. Controller 112 may also be in communication with an engine temperature sensor 96, a hydraulic temperature sensor 98, and a timer 100. Based on signals provided by engine and hydraulic temperature sensors 96, 98 and timer 100, controller 112 may affect at least one of an output of power source 18, a displacement of first and/or second sources 51, 53, and a position of warmup valves 105 to implement a warmup procedure.
Controller 112 may embody a single microprocessor or multiple microprocessors that include a means for controlling an operation of machine control system 48. Numerous commercially available microprocessors can be configured to perform the functions of controller 112. It should be appreciated that controller 112 could readily be embodied in a general machine microprocessor capable of controlling numerous machine functions. Controller 112 may include a memory, a secondary storage device, a processor, and any other components for running an application. Various other circuits may be associated with controller 112 such as power supply circuitry, signal conditioning circuitry, solenoid driver circuitry, and other types of circuitry.
Engine temperature sensor 96 may embody any type of sensor configured to monitor a temperature of power source 18. In one example, engine temperature sensors 96 may be a fluid sensor associated with a flow of air or exhaust, a coolant, or a lubricant of power source 18. As such, engine temperature sensor 96 may generate a signal indicative of the temperature of power source 18, and direct this signal to controller 112. When the engine temperature signal indicates a temperature lower than a threshold value, for example about 25° C., machine 10 may be considered to be operating in a cold condition.
Hydraulic temperature sensor 98 may embody any type of sensor configured to monitor a temperature of machine control system 48. In one example, hydraulic temperature sensors 98 may be a fluid sensor associated with the fluid of first and/or second circuits 50, 52. As such, hydraulic temperature sensor 98 may generate a signal indicative of the temperature of machine control system 48, and direct this signal to controller 112. When the hydraulic temperature signal indicates a temperature lower than a threshold value, for example about a temperature selected from the range of about 25° C. or lower to about 60° C., machine control system 48 may be considered to be operating in a cold condition.
Timer 100 may be separate from or form a part of controller 112. In response to a command from controller 112, timer 100 may track an elapsed time. Signals indicative of this elapsed time may be directed from timer 100 to controller 112.
The disclosed machine control system may be applicable to any machine that includes multiple fluid actuators where operation during startup or cold conditions can be damaging or result in undesired performance. The disclosed machine control system may provide a warmup procedure that helps minimize damage and improves performance of the machine. Operation of machine control system 48 will now be explained.
As shown in
During the engine warmup procedure, controller 112 may monitor and compare the tracked time to a threshold time period, for example about five minutes, to determine if power source 18 has been operating in a warming mode for a sufficient amount of time (Step 230). If the tracked time is less than the threshold time period, control may return to step 210 and cycle through steps 210-230 until either the operational time of power source 18 exceeds the threshold time period for warming or the temperature of power source 18 increases to the desired engine temperature. When either of these conditions is met, controller 112 may then monitor a signal from hydraulic temperature sensor 98 to determine if the indicated hydraulic temperature is suitable for full operation of work tool 14 (i.e., to determine if the indicated hydraulic temperature is greater than a desired hydraulic temperature of about 40° C. in one example or 55° C. in another example) (Step 240). It is understood that the desired hydraulic temperature can be any temperature selected from the range of about 25° C. to about 60° C.
If, at step 240, the temperature indicated by the signal from hydraulic temperature sensor 98 is less than the desired hydraulic temperature, warmup of machine control system 48 may commence. It is contemplated that warmup of machine control system 48 may be delayed by, for example, about 30-60 seconds after engine warmup, if desired. Controller 112 may initiate warmup of machine control system 48 one or more of the following: by setting operation of power source 18 to a warmup start level, by way of example that can be greater than a low-idle level, by fixing the displacement of first and/or second sources 51, 53 at a desired displacement, which can be in one example, a maximum displacement position, by moving one or both of warmup valves 105 to the flow-passing position to cause fluid pressurized by first and/or second sources 51, 53 to bypass control valves 54-62 and their associated actuators (Step 250).
After warmup initiation, controller 112 may monitor the cylinder pressure of one or more hydraulic cylinders, for example, the boom hydraulic cylinder 26 (Step 260). The cylinder pressure can be measured or sensed by the pressure sensors 83a or 83b, or may be determined by a calculation based on one or more of the following, the cylinder displacement, valve position, pump discharge pressure, and other known hydraulic system parameters. Controller 112 may compare the current cylinder pressure to a maximum allowable or threshold operational level (Step 270). In one example, the maximum allowable or threshold operational level may be about, e.g., 18,000 kPa. In one example, the cylinder pressure may exceed a pressure threshold, which can be modified in some instances for a particular system application, for a period of time (t) to permit quicker temperature rise.
If, at step 270, the comparison reveals that the cylinder pressure is less than the threshold operational level, controller 112 may check to see if the hydraulic temperature of machine control system 48 is still less than the desired hydraulic temperature (Step 280). Controller 112 may continue to cycle through steps 260, 270 and 280 until the hydraulic temperature becomes equal to or greater than the desired hydraulic temperature.
When the warmup procedure is complete, operation of power source 18 may be returned to a low-idle level if warmup level for engine speed is greater than low-idle, the displacement of first and/or second sources 51, 53 may be returned to a minimum displacement setting if warmup setting for pump displacement is greater than minimum displacement setting, and one or both of warmup valves 105 may be moved to the flow-blocking positions and the procedure may be terminated (Step 300).
Returning back to step 270, if the cylinder pressure is determined to be not less than the threshold (i.e., greater than), the pump discharge or outlet pressure may be reduced such that the cylinder pressure is at or below the threshold operational level. In some instances, the pump outlet pressure may be reduced such that the cylinder pressure is at a certain percentage level below the threshold operational level, e.g., about 10%. The pump outlet pressure may also be determined with the pump pressure sensor 87 and be reduced and monitored. Once the cylinder pressure is at a desired level, reducing the pump outlet pressure is no longer necessary, and the hydraulic temperature may be compared such as in Step 280.
In one example, the pump outlet pressure may be reduced by destroking the sources 51 and/or 53. Controller 112 may be configured to selectively begin decreasing the displacement of first and/or second sources 51, 53 (depending on which source is currently supplying the high pressure fluid moving work tool). In some embodiments, the de-stroking of first and/or second sources 51, 53 may be limited. That is, controller 112 may be configured to destroke first and/or second sources 51, 53 only to a minimum amount that still allows some flow to be discharged by first and/or second sources 51, 53. For example, the minimum amount may still allow for about 10% of a maximum flow to be discharged from first and/or second sources 51, 53.
In another example, instead or in addition to destroking the sources 51 and/or 53, the pump outlet pressure may be reduced by modulating the bypass valve 85. For example, based on the cylinder pressure being above the threshold, controller 112 can command the bypass valve to move to the flow passing first position, via the solenoid actuated valve stem, to allow flow to flow to tank 64. The position of the bypass valve can be tuned in order to achieve a desired varying flow rate. The bypass valve 85 can be open to allow flow to tank 64. The bypass valve 85 can be configured to unload the corresponding source 51 instead of using main relief element 104. Once the cylinder pressure is at a desired level, the bypass valve can be commanded to move to its flow blocking second position at which fluid flow may be substantially blocked from flowing to tank 64.
Returning back to step 280, if the temperature indicated by the signal from hydraulic temperature sensor 98 is about equal to or greater than the desired hydraulic temperature (i.e., if the indicated temperature is not less the desired temperature), control may advance to step 300. In this situation, the warmup procedure may be complete regardless of the operational level attained by power source 18.
Several benefits may be associated with the hardware and warming procedure of machine 10. Specifically, because of the arrangement of common supply and drain passages 66, 70, 68, 72 within valve stack 49, when the fluid therein is warmed and caused to circulate through valve stack 49, the entire valve stack 49, including control valves 54, 56, 58, 60, 62, may be warmed. Further, the disclosed warming procedure may help ensure that the components of machine 10 are warmed in a sequence and at a rate that minimize damage to machine 10 and quickly readies machine 10 for operation. Also, by controlling cylinder pressure to a desired value, leakage of oil can be reduced and/or inhibited through the cylinder and/or system. In the case where a first pressure sensor is associated with a head end chamber of the hydraulic cylinder, and a second pressure sensor is associated with a rod end chamber of the hydraulic cylinder, a system pressure increase on the head end chamber may have a greater impact on hydraulic cylinder during warming procedure, than compared to the rod end chamber, due to the cylinder ratio.
It will be apparent to those skilled in the art that various modifications and variations can be made to the disclosed machine control system. Other embodiments will be apparent to those skilled in the art from consideration of the specification and practice of the disclosed machine control system. For example, it is contemplated that the above warming procedure may additionally or alternatively commence at any time during operation of machine 10 based on temperatures of power source 18 and or machine control system 48, regardless of operator input (i.e., the warming procedure may be triggered in ways other than by the operator turning the key on). And, it is contemplated that an operator input may override the warming procedure such that full operation of machine 10 may be utilized regardless of the temperatures of power source 18 and machine control system 48, if desired. It is intended that the specification and examples be considered as exemplary only, with a true scope being indicated by the following claims and their equivalents.
This application claims the benefit of priority from U.S. Provisional Application No. 61/954,855 by Matthew J. Beschorner et al., filed Mar. 18, 2014.
| Number | Date | Country | |
|---|---|---|---|
| 61954855 | Mar 2014 | US |
