Patent Application
20120152575
The present disclosure relates generally to a hydraulic system, and more particularly, to a hydraulic system having dual tilt blade control.
Some earth moving machine, for example dozers, motor graders, and snow plows, have a front-mounted work tool such as a blade, bucket, or plow for pushing or carrying material. These work tools can be tilted about a horizontal axis generally perpendicular to the work tool by one or more tilt cylinders, and pitched about a horizontal axis parallel to the work tool by dual cylinders located to either side of the work tool. Tilting may be accomplished by extending and retracting a single cylinder or extending one paired cylinder while retracting the other paired cylinder. Pitching can be separately accomplished by extending or retracting both paired cylinders in the same direction at the same time. Existing hydraulic systems utilize different combinations of manual and/or pilot control valves to regulate the tilting and pitching operations.
An exemplary hydraulic system having tilt control is disclosed in U.S. Pat. No. 6,481,506 (the '506 patent) issued to Okada et al. on Nov. 19, 2002. Specifically, the '506 patent discloses a hydraulic system having a left tilt cylinder and a right tilt cylinder connected between straight side frames of a machine and outer edges of a blade. The hydraulic system also includes a left cylinder actuation switching valve (LCASV), a right cylinder actuation switching valve (RCASV), a left post-pressure compensating valve associated with the LCASV, a right post-pressure compensating valve associated with the RCASV, and a pilot switching valve. Each of the LCASV and RCASV are pilot-operated valves configured to move between first positions at which pressurized fluid from a pump is directed into head-ends of the associated tilt cylinders, and second positions at which pressurized fluid is directed into rod-ends of the associated tilt cylinders. The pilot switching valve is a solenoid-operated valve movable between a first position at which the head-ends of both the LCASV and RCASV receive the same pilot pressure, and a second position at which the head-end of the LCASV and the rod-end of the RCASV receive the same pilot pressure. In this configuration, the hydraulic system may be capable of separately implementing a pitch operation utilizing both LCASV and RCASV, a single-tilt operation using only LCASV, or a dual-tilt operation using LCASV and RCASV.
Although the system of the '506 patent may be capable of separately implementing both tilt and pitch operations, it may still be limited. That is, the system of the '506 patent may not be capable of simultaneously tilting and pitching, or of accomplishing single-tilt operations using only the RCASV. These limitations may reduce functionality of the associated machine.
The hydraulic system of the present disclosure addresses one or more of the needs set forth above and/or other problems of the prior art.
In one aspect, the present disclosure is directed to a hydraulic system. The hydraulic system may include a tank configured to hold a supply of fluid, a pump configured to draw fluid from the tank and pressurize the fluid, a first cylinder operatively connected between a first side of a work tool and an undercarriage of the machine, and a second cylinder operatively connected between a second side of the work tool and the undercarriage of the machine. The hydraulic system may also include a first electro-hydraulic valve associated with the first cylinder and configured to selectively regulate a flow of pressurized fluid to the first cylinder independently of the second cylinder, and a second electro-hydraulic valve associated with the second cylinder and configured to selectively regulate a flow of pressurized fluid to the second cylinder independently of the first cylinder.
In another aspect, the present disclosure is directed to a method of moving a work tool. The method may include receiving a first signal indicative of desired work tool tilting, receiving a second signal indicative of desired work tool pitching, and determining a valve position command based on the first and second signals. The method may also include simultaneously tilting and pitching the work tool based on the valve position command.
Implement system 12 may include a linkage structure acted on by fluid actuators to move work tool 14. Specifically, implement system 12 may include left and right push arms 20, 22 that are pivotally connected at proximal ends 24 to drive system 16 and at opposing distal ends 26 to left and right base edges of work tool 14, respectively. A pair of opposing left and right hydraulic cylinders 34, 36 may be operatively connected between left and right upper edges of work tool 14 and center portions of left and right push arms 20, 22, respectively, to tilt and pitch work tool 14 relative to a frame 30. As will be described in more detail below, the extension or retraction of hydraulic cylinders 34, 36 by differing amounts and/or in differing directions may function to tilt work tool 14 in a vertical plane about a horizontal axis 38. In contrast, the extension or retraction of both hydraulic cylinders 34, 36 by an equal amount in the same direction may function to pitch work tool 14 in a vertical plane about a horizontal axis 40 that is substantially perpendicular to axis 38.
Numerous different work tools 14 may be attachable to a single machine 10 and operator controllable. Work tool 14 may include any device used to perform a particular task such as, for example, a blade, a bucket, a plow, or another task-performing device known in the art. Although connected in the embodiment of
Drive system 16 may include opposing undercarriage assemblies 42 (only one shown in
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 known source. Power source 18 may produce a mechanical or electrical power output that is used to propel machine 10 via drive system 16 and can be converted to hydraulic power for moving hydraulic cylinders 34, 36.
Operator station 19 may include devices that receive input from a machine operator indicative of desired machine maneuvering. Specifically, operator station 19 may include one or more interface devices 50 located proximate a seat 52. Interface devices 50 may be manipulated by an operator to initiate movement of machine 10 by producing proportional displacement signals that are indicative of desired maneuvering. In one embodiment, interface device 50 may include a joystick associated with control of tilting and pitching movements of work tool 14. It is contemplated that an interface device 50 other than a joystick such as, for example, a pedal, a lever, a wheel, and other devices known in the art, may additionally or alternatively be provided within operator station 19 for movement control of machine 10, if desired.
As shown in
As shown in
Machine 10 may include a hydraulic system 76 having a plurality of fluid components that cooperate to cause the extending and retracting movements of hydraulic cylinders 34, 36 described above. Specifically, hydraulic system 76 may include a tank 78 holding a supply of fluid, and a primary source 80 configured to pressurize the fluid and selectively direct the pressurized fluid to each of hydraulic cylinders 34, 36. Primary source 80 may be connected to tank 78 via a tank passage 82, and to each hydraulic cylinder 34, 36 via a common supply passage 84 and separate head- and rod-end passages 86, 88. Tank 78 may be connected to each hydraulic cylinder 34, 36 via a common drain passage 90 and head- and rod-end passages 86, 88. Hydraulic system 76 may also include a plurality of valves located between hydraulic cylinders 34, 36 and tank 78 and primary source 80 to regulate flows of fluid through passages 84-90.
Primary source 80 may be configured to draw fluid from one or more tanks 78 and pressurize the fluid to predetermined levels. Specifically, primary source 80 may embody a pumping mechanism such as, for example, a variable displacement pump having a displacement actuator 92 that adjusts a displacement of primary source 80 based on a pressure of fluid within a load sense passage 94, a fixed displacement pump (not shown) having an unloader valve (not shown) that selectively reduces a load on primary source 80, or any other type of source known in the art. Primary source 80 may be connected to power source 18 of machine 10 by, for example, a countershaft, a belt (not shown), an electrical circuit (not shown), a reduction gear box (not shown), or in any other suitable manner.
Tank 78 may constitute a reservoir configured to hold a low-pressure 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 78. It is contemplated that hydraulic system 76 may be connected to multiple separate fluid tanks 78 or to a single tank 78, as desired.
The valves of hydraulic system 76 may be disposed within a common or separate valve blocks (not shown) and include, for example, a first electro-hydraulic valve 96 associated with hydraulic cylinder 34, and a second substantially identical electro-hydraulic valve 98 associated with hydraulic cylinder 36. First electro-hydraulic valve 96 may be disposed between head- and rod-end passages 86, 88 of hydraulic cylinder 34 and common supply and drain passages 84, 90. Second electro-hydraulic valve 98 may be disposed between head- and rod-end passages 86, 88 of hydraulic cylinder 36 and common supply and drain passages 84, 90
Each of first and second electro-hydraulic valves 96, 98 may include a pilot-operated main spool 100 and first and second paired solenoid-operated valve elements 102, 104. Main spool 100 may be movable between a first position at which a main flow of pressurized fluid from common supply passage 84 is allowed to pass to head-end pressure chamber 70 of its associated hydraulic cylinder 34 or 36 and waste fluid from rod-end pressure chamber 72 is allowed to pass to common drain passage 90, a second position at which the main flow of pressurized fluid from common supply passage 84 is allowed to pass to rod-end pressure chamber 72 and waste fluid from head-end pressure chamber 70 is allowed to pass to common drain passage 90, and a third position (shown in
In the disclosed embodiment, a pre-pressure compensating valve 106 and/or a check valve 108 may be disposed within a supply passage 110 that extends between common supply passage 84 and main spool 100 to provide a unidirectional supply of fluid having a substantially constant flow from primary source 80 into main spool 100. It is contemplated that, in some applications, pre-pressure compensating valve 106 and/or check valve 108 may be omitted or moved to another location within hydraulic system 76, as desired.
A pressure regulating valve 112 may be disposed within common drain passage 90 to provide a desired backpressure within hydraulic system 76. Pressure regulating valve 112 may be movable between flow-passing and flow-restricting positions based on a pressure differential between the fluid from load-sense passage 94 (or from hydraulic cylinders 34, 36, depending on which is higher) and the fluid draining into tank 78 via common drain passage 90. A pressure relief valve 114 may be disposed within a bypass passage 116 that connects common supply passage 84 to an inlet of pressure regulating valve 112. Pressure relief valve 114 may be movable between flow-passing and flow-blocking positions based on a pressure differential between the fluid from common supply passage 84 and the fluid from common drain passage 90.
Load sense passage 94 may be configured to direct a portion of the main flow of fluid (i.e., the fluid pressurized by primary source 80) from the one of main spools 100 that is exposed to higher pressures. In particular, load sense passage 94 may be connected to a supply port of each main spool 100 via a resolver 115 and individual load sense passages 117, 119 associated with each main spool 100. Resolver 115 may be configured to move based on a pressure differential between load sense passages 117, 119 to allow the higher pressure fluid to affect the displacement of primary source 80.
The flow of pilot fluid regulated by solenoid-operated valve elements 102, 104 to move main spool 100 may be provided by way of a pilot source 121, a common pilot passage 118, and individual pilot supply passages 120, 122. Similar to primary source 80, pilot source 121 may be configured to draw fluid from one or more tanks 78 and pressurize the fluid to predetermined levels. Pilot source 121 may embody a variable or fixed (shown in
A controller 124 may be in communication with the different components of hydraulic system 76 to regulate operations of machine 10. For example, controller 124 may be in communication with each of solenoid-operated valve elements 102, 104 and with interface device 50 (referring to
The disclosed hydraulic system may be used with any machine having a work tool that is capable of both tilting and pitching. The disclosed hydraulic system may be particularly useful when applied to a dozer having a blade where variable control over blade tilting and combined blade tilt/pitch maneuvers are beneficial. Variable control over blade tilting and combined blade tilt/pitch maneuvers may be possible through separate regulation of independent hydraulic cylinders. Operation of hydraulic system 76 will now be described in detail.
As shown in
For example, if a retraction of hydraulic cylinder 34 is requested, solenoid-operated valve element 102 may be energized by controller 124 to move toward its first position and direct pressurized fluid from primary source 80 to its associated end of main spool 100. Substantially simultaneously, the solenoid-operated valve element 104 may be de-energized by controller 124 and spring-biased toward its second position to allow fluid from its associated end of mail spool 100 to drain to tank 78. By directing pressurized fluid to the valve 102-end of main spool 100 and draining fluid from the valve 104-end of main spool 100, a pressure differential across main spool 100 may be created that causes main spool 100 to move away from solenoid-operated valve element 102 and toward solenoid-operated valve element 104 (i.e., to move toward its second position). When main spool 100 is in the second position, as described above, pressurized fluid from primary source 80 may be directed into rod-end pressure chamber 72 while fluid from head-end pressure chamber 70 may be drained of fluid, thereby creating a pressure differential across piston assembly 68 that causes hydraulic cylinder 34 to retract. An extension of hydraulic cylinder 34 may be performed in a similar manner and, therefore, will not be described in detail in this disclosure. Extensions and retractions of hydraulic cylinder 36 may also be performed in a similar manner and will therefore also not be described in further detail in this disclosure.
Hydraulic cylinders 34, 36 may be cooperatively extended or retracted to generate a dual-action tilt to the left, a dual-action tilt to the right, a forward pitch, a rearward pitch, and a combination tilt/pitch to the left or right and forward or rearward. For example, to generate the dual-action tilt to the left, hydraulic cylinder 34 may be retracted while hydraulic cylinder 36 may be extended. Retraction of hydraulic cylinder 34 may result in the left edge of work tool 14 being pulled downward relative to machine 10, while extension of hydraulic cylinder 36 may result in the right edge of work tool 14 being pushed upward relative from machine 10. The combined downward movement of the left edge of work tool 14 and upward movement of the right edge of work tool 14 may function to tilt work tool 14 to the left, as viewed from an operator's perspective. A simultaneous retraction of hydraulic cylinder 36 at the right edge of work tool 14 and extension of hydraulic cylinder 34 at the left edge of work tool 14 may function to tilt work tool 14 to the right. Simultaneous movements of hydraulic cylinders 34 and 36 may result in a large range of work tool tilting with high force. Work tool 14 may be caused to pitch forward by the simultaneous equal extension of both hydraulic cylinders 34, 36, and rearward by the simultaneous equal retraction of both hydraulic cylinders 34, 36. The combination tilt/pitch motion to the left or right may be achieved by simultaneously extending or retracting both hydraulic cylinders 34, 36, but by differing amounts. For example, to tilt work tool 14 to the left while pitching work tool 14 forward, both hydraulic cylinders 34, 36 may be extended, but with hydraulic cylinder 36 extending at a greater rate. Similarly, to tilt work tool 14 to the right while pitching work tool 14 rearward, both hydraulic cylinders 34, 36 may be retracted, but with hydraulic cylinder 34 retracting at a slower rate.
Hydraulic cylinders 34, 36 may each be independently extended or retracted to generate a single-action tilt of work tool 14 to the left or to the right. The single-action tilting of work tool 14 may be beneficial when a failure of one of hydraulic cylinders 34, 36 or associated valving has occurred that makes dual-action tilting impractical. For example, when a communication failure between first and/or second solenoid-operated valve elements 102, 104 of hydraulic cylinder 34 has occurred, controller 124 may detect the failure and responsively command only hydraulic cylinder 36 to extend or retract and thereby tilt work tool 14 in the desired manner, and vice versa. Although the resulting tilting may have a smaller range of motion and/or a smaller associated force, this functionality may still provide a “limp home” capability.
Controller 124 may implement one or more algorithms and/or maps stored in memory to regulate movements of each solenoid-operated valve element 102, 104 based on input received from interface device 50 to control the corresponding movements of work tool 14 in a manner desired by the machine operator. For example, when an operator only pivots handle 54 to the left to a position about half way through its range from its centered position, a proportional first signal requesting a left tilt of work tool 14 at about 50% of a maximum speed may be generated by interface device 50 and directed to controller 124. Upon receiving the first signal, controller 124 may normalize the signal (i.e., convert the signal to a standard value between −1000 and zero or between zero and +1000 for each hydraulic cylinder 34, 36 depending on the pivot direction) according to one or more preprogrammed algorithms. In this example, pivoting handle 54 leftward to the 50% position may result in a normalized value for hydraulic cylinder 34 of about −500 and a normalized value for hydraulic cylinder 36 of about +500. Controller 124 may then reference the normalized values with one or more modulation maps stored in memory to determine corresponding valve position commands directed to solenoid-operated valve elements 102, 104 causing hydraulic cylinder 34 to retract and hydraulic cylinder 36 to extend in opposing directions at substantially equal speeds.
Manipulation of only thumb roller 60 may be treated in the same general manner by controller 124. For example, when an operator only rotates thumb roller 60 to the right to a position about one-quarter through its range from its centered position, a proportional second signal requesting a forward pitch of work tool 14 at about 25% of a maximum speed may be generated by interface device 50 and directed to controller 124. Upon receiving the second signal, controller 124 may again normalize the signal. In this example, rotating thumb roller 60 to the right to the 25% position may result in a normalized value for both hydraulic cylinder 34, 36 of about +250. Controller 124 may then reference the normalized values with one or more modulation maps stored in memory to determine corresponding valve position commands directed to solenoid-operated valve elements 102, 104 causing both hydraulic cylinders 34, 36 to extend at substantially equal speeds.
When handle 54 is tilted and thumb roller 60 is also simultaneously moved away from its centered position, controller 124 may generate combined valve position commands that are functions of both the first and second signals. For example, when handle 54 is tilted to the left 50% position and thumb roller 60 is simultaneously rotated to the right 25% position, controller 124 may generate normalized values of −500 (tilt value) and +250 (pitch value) for hydraulic cylinder 34, and +500 (tilt value) and +250 (pitch value) for hydraulic cylinder 36. Before referencing the modulation maps stored in memory, as normally performed by controller 124 when only tilting or only pitching is requested, controller 124 may instead first sum the normalized values. In the disclosed example, the normalized values would sum to −250 for hydraulic cylinder 34 and +750 for hydraulic cylinder 36. These sums may then be referenced by controller 124 with the modulation maps to determine corresponding valve position commands directed to solenoid-operated valve elements 102, 104 causing hydraulic cylinder 34 to retract at a first slower speed and hydraulic cylinder 36 to extend at a second faster speed. The unequal retraction/extension of hydraulic cylinders 34, 36 may result in a combined left tilting/forward pitching motion of work tool 14.
In some applications, it may be desirable to scale the valve position commands before they are directed to solenoid-operated valve elements 102, 104. Scaling the valve position commands may increase control over work tool 14 and allow modulation of hydraulic cylinders 34, 36 to be tuned for different machines in different applications. In the disclosed embodiment, the scaling may be different when the first or second signal is received alone, versus when the two signals are received at the same time. For example, when only one of the first and second signals requesting only tilting or only pitching of work tool 14 is received, controller 124 may scale down the valve position commands by about 50% before directing the valve position commands to solenoid-operated valve elements 102, 104. In contrast, when the first and second signals are simultaneously received, controller 124 may scale down the valve position commands by only about 20%. The different levels of scaling may improve responsiveness during the combined tilt/pitch movements of work tool 14.
Because hydraulic system 76 may be capable of simultaneously tilting and pitching work tool 14, efficiency, productivity, and ease of use of machine 10 may be increased. For example, when both a tilt and pitch operation of work tool 14 are required, the operator may no longer be required to wait until work tool 14 has finished tilting to the desired angle before initiating pitching of work tool 14. By eliminating the wait time of the operator, the operator may be able to more quickly initiate and complete the task at hand, thereby improving the efficiency and productivity of machine 10. In addition, it may be easier for the operator to position work tool 14 exactly where desired with a single input action when both tilting and pitching movements are performed simultaneously, as opposed to tilting work tool 14, then pitching work tool 14, then adjusting the tilt, and so forth.
The ability to separately and independently control hydraulic cylinder 34 and hydraulic cylinder 36 to tilt work tool 14, may provide some functionality even during failure of one of the cylinders. This functionality may allow the operator to complete the task at hand before bringing machine 10 in for service and/or at least allow the operator to move the malfunctioning work tool 14 to a desired position for safe and efficient travel to a service area.
It will be apparent to those skilled in the art that various modifications and variations can be made to the hydraulic system of the present disclosure without departing from the scope of the disclosure. Other embodiments will be apparent to those skilled in the art from consideration of the specification and practice of the hydraulic system disclosed herein. It is intended that the specification and examples be considered as exemplary only, with a true scope of the disclosure being indicated by the following claims and their equivalent.
This application is based on and claims the benefit of priority from U.S. Provisional Application No. 61/424,250 by Timothy L. HAND et al., filed Dec. 17, 2010, the contents of which are expressly incorporated herein by reference.
| Number | Date | Country | |
|---|---|---|---|
| 61424250 | Dec 2010 | US |
