TECHNICAL FIELD
The present disclosure relates generally to a hydraulic actuator, and more particularly, to a high response hydraulic actuator for controlling a variable displacement pump.
BACKGROUND
Variable displacement hydraulic pumps are widely used in hydraulic systems to provide pressurized hydraulic fluid for various applications. Many types of machines such as dozers, loaders, and the like, rely heavily on hydraulic systems to operate, and utilize variable displacement pumps to provide a greater degree of control over fixed displacement pumps.
Various control schemes have been utilized to control the swashplate angle of such variable displacement hydraulic pumps. One such control scheme is disclosed in U.S. Pat. No. 6,553,891, filed Jul. 9, 2001, to Carsten Fiebing, which is hereby incorporated by reference. However, it may be beneficial to provide a control scheme offering greater responsiveness and stability.
SUMMARY OF THE INVENTION
In one aspect of the disclosure, a hydraulic system includes a source of pressurized fluid; a hydraulic actuator; and first and second hydraulically isolated chambers configured to expand and contract, wherein expansion of the first and second chamber actuates the actuator in a first direction. The hydraulic system further includes third and fourth hydraulically isolated chambers configured to expand and contract, wherein expansion of the third and fourth chamber actuates the actuator in a second direction opposite the first direction. Each of the chambers has an associated pressure reducing valve that selectively communicates the respective chamber with either a source of pressurized fluid or a tank.
In another aspect, a variable displacement hydraulic device is disclosed having a swashplate; a hydraulic actuator operable to selectively increase and decrease an inclination of the swashplate; a first chamber configured to expand and contract, wherein expansion of the first chamber actuates the actuator in a first direction; a first valve fluidly connected to the first chamber, wherein the first valve selectively communicates pressurized fluid with the first chamber; and a second chamber configured to expand and contract, wherein expansion of the second chamber actuates the actuator in the first direct. According to this aspect, the first chamber and the second chamber are substantially hydraulically isolated.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a side-view diagrammatic illustration of an exemplary disclosed machine;
FIG. 2 is a schematic illustration of an exemplary disclosed transmission; and
FIG. 3 is a schematic illustration of an exemplary disclosed hydraulic pump and associated control hardware.
DETAILED DESCRIPTION
FIG. 1 illustrates an exemplary machine 10. Machine 10 may be a fixed or mobile machine that performs operations associated with an industry such as mining, construction, farming, or any other industry known in the art. For example, machine 10 may be an earth moving machine such as a dozer, a loader, a backhoe, an excavator, a motor grader, a dump truck, or any other earth moving machine. Machine 10 may also embody a generator set, a pump, a marine vessel, or any other suitable machine. Referring to FIGS. 1 and 2, machine 10 may include a frame 12, an implement 14, a hydraulic actuator, an engine 16, fraction devices 18 such as wheels or tracks, and a transmission 20 to transfer power from the engine 16 to the traction devices 18.
As illustrated in FIG. 2, the transmission 20 may be a hydrostatic transmission and may include a primary pump 22, a motor 24 and a bypass relief valve 26. In practice, transmission may be a continuously variable transmission (CVT), parallel path variable transmission (PPV), or other transmission known in the art. According to the present disclosure, the main pump 22 may be a variable displacement pump such as a variable displacement axial piston pump, and the motor 24 may be a fixed displacement hydraulic motor. However, the motor 24 may alternatively be a variable displacement motor. The transmission 20 may further include a charge pump 28 providing pressurized fluid to swashplate control hardware 30, which is illustrated in greater detail in FIG. 3.
FIG. 3 illustrates the primary pump 22, which includes pistons 50 disposed in a cylinder block 52. The pistons 50 are slidably supported by swashplate 54, and swashplate 54 has a variable angle of inclination that affects the displacement of the pistons 50 for each revolution of the pump 22. In the illustrated embodiment, swashplate 54 is connected to an actuation arm 56 that is, in turn, connected to an actuation member 58. Movement of actuation arm 56 may effect a change in the inclination of swashplate 54. For example, moving actuation arm 56 to the left, with respect to FIG. 3, may increase the inclination of swashplate 56, whereas moving actuation arm 56 to the right, with respect to FIG. 3, may decrease the inclination of swashplate 54. Actuation member 58 is slidable about a shaft 60, which is fixed with respect to the pump housing 62.
As seen in FIG. 3, many components of the swashplate control hardware 30 may be similar on both the left and right sides of the pump 22; such similar components may be denoted with common reference numbers. Disposed within actuation member are proximal spring retainers 64a and distal spring retainers 64b, which together enclose springs 65. Proximal spring retainer members 64a may be slidable about shaft 60, but may be constrained from sliding toward the center of the shaft 60 by a lip 68 on the shaft 60. Distal spring retainers 64b may be slidable about shaft 60, but constrained from movement away from the center of actuation member 58 by a restraining ring 70, and constrained from movement away from the center of shaft 60 by another restraining ring 72. Both proximal spring retainers 64a and distal spring retainers 64b may include fluid passageways 74 to allow fluid to pass through the spring retainers 64a, 64b.
A cap member 77 may further be partially disposed in actuation member 58. In the illustrated embodiment, cap member 77 is constrained from movement with respect to actuation member 58 by restraining ring 70 and restraining ring 78. Cap member 77 also passes through a restrictive portion 80 of pump housing 62, and is surrounded by a seal 82 at the restrictive portion 80.
In the illustrated embodiment, with respect to the left side of the pump 22 in FIG. 3, seal 82 defines a boundary between interior chamber 100a and anterior chamber 102a. With respect to the right side of the pump 22 in FIG. 3 seal 82 defines a boundary between interior chamber 100b and anterior chamber 102b. In the illustrated embodiment, each chamber 100a, 100b, 102a, 102b is selectively connected to charge pump 28 by a pressure reducing valves 110a, 110b, 112a, 112b, respectively. The use of pressure reducing valves to control the displacement of a variable displacement pump is discussed in U.S. patent application Ser. No. 11/269,392 to Michael Cronin (Pub. No. 2007/0101709), which is hereby incorporated by reference. As illustrated, pressure reducing valves 110a, 110b, 112a, 112b may be infinitely variable, three way valves that selectively communicate their respective chamber 100a, 100b, 102a, 102b with either the charge pump 28 or tank 115. Furthermore, pressure reducing valves 110a, 110b, 112a, 112b may be electronic pressure reducing valves and may be selectively actuated by solenoids.
INDUSTRIAL APPLICABILITY
In operation, swashplate 54 inclination can be changed by moving actuation member 58, and hence actuation arm 56. Actuation member 58 can be moved by selectively directing pressurized fluid in and out of chambers 100a, 100b, 102a, 102b. For example, with reference to FIG. 3, to move actuation member 58 to the left, the solenoids corresponding to pressure reducing valve 110b and pressure reducing valve 112b may be energized such that pressurized fluid from charge pump 28 is passed to both interior chamber 100b and anterior chamber 102b, thereby causing both chambers to expand. The expansion of chambers 100b, 102b actuates actuation member 58 to the left. While some leakage may pass between the anterior chamber 102b and interior chamber 100b, seal 82 causes interior chamber 100b to be substantially hydraulically isolated from anterior chamber 102b. As flow is passed through two valves 110b, 112b, actuation member 58 can be actuated more quickly because pressurized fluid can be provided through the two valves 110b, 112b at a higher combined rate than a similar system having only a single valve of similar size that must effectively provide fluid to both chambers. Furthermore, as the two chambers 100b, 102b are substantially hydraulically isolated, interference and cross-talking between the two valves 110b, 112b may be reduced or avoided.
To further the example discussed above, to move actuation member 58 to the left, the solenoids corresponding to pressure reducing valve 110a and pressure reducing valve 112a may be de-energized such that fluid in interior chamber 100a and anterior chamber 102a can flow to tank 115, causing these chambers 100a, 102a to contract, which permits actuation member 58 to move left. In a similar manner, actuation member 58 may be moved to the right by energizing solenoids associated with pressure reducing valve 110a and pressure reducing valve 112a, and de-energizing solenoids associated with pressure reducing valve 110b and pressure reducing valve 112b.
It will be apparent to those skilled in the art that various modifications and variations can be made to the disclosed hydraulic system. Other embodiments will be apparent to those skilled in the art from consideration of the specification and practice of the disclosed hydraulic system. 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.
Patent Application
20110094214
