Hydraulic circuits for actuators

Abstract: A hydraulic control system comprising a pump (10), a hydraulic actuator (17), working lines (15, 16), meter-in valves (13, 14) individual to each working line (15, 16), a controller (C) for supplying pilot pressure to the respective meter-in valves for controlling the direction of movement of the load, and a pair of return lines (22, 23; 26, 27), each controlled by a relief valve (21, 25). When the controller (C) is moved to actuate one of the meter-in valves for supplying fluid through one of the working lines, the variable relief valve of the return line is also actuated. The controller thus simultaneously controls the fluid flow to the actuator and the fluid flow from the actuator. Thereby simultaneously controlling the driving and braking functions of the system.

Description: This invention relates to a hydraulic control system of the preamble to claim 1 and is applicable particularly to hydraulic circuits for actuators such as are found in excavators, backhoe-loaders and forestry equipment, like log loaders and feller-bunchers. A hydraulic control system according to the preamble of claim 1 is known from GB-A 2 044 366 and includes a pair of meter-out valves for controlling the flow out of the actuator to tank in a manner that the respective meter-out valve which is opening its metering area leads the respective meter-in valve which follows with opening its metering area. Thus, in the case of energy generating loads, the velocity of the load can be controlled by using the meter-out valve. Hydraulic control systems for controlling the acceleration, velocity and deceleration of heavy loads and in particular swing drives, have typically made use of some form of pressure control. An excellent example is the closed loop swing drive pump control described in US-A-3,696,836 which provides true pressure control in both driving and braking mode. In neutral, this control provides for free coast, a characteristic very desirable for construction cranes. In other applications, like excavators, backhoe-loaders and forestry equipment, like log loaders and feller-bunchers, the free coast is not acceptable - neutral lever position must give blocked port conditions. In these applications, the most common method of deceleration or braking is to center the valve and utilize either port relief valves or cross port relief valves. Improvements to the above have been made by introducing two relief valve pressure levels (one for acceleration, one for deceleration), or pressure rate sensing relief valves to smooth the action. Nevertheless, the one large performance disadvantage with the above systems is when once the valve is centered, there is no control of where the swing will stop. The stop position depends on load inertia. Another disadvantage is that there is no way to stop the swing motion earlier, if desired. Among the objectives of the present invention are to provide a hydraulic system wherein the swing motion of the device being controlled is controlled throughout the desired movement; wherein both acceleration and deceleration may be controlled by one input signal from the same controller; wherein both acceleration and deceleration of large inertia loads, for example swing drives, can be achieved; wherein control of acceleration and deceleration is achieved by controlling both accelerating pressure and decelerating pressure simultaneously; wherein the system functions on the basis of a difference between acceleration or driving pressure and deceleration or braking pressure; and wherein the pressure controlling the swing motion comprises the only actuator connection to tank. The teaching of claim 1 gives a solution to the problem referred to above. In accordance with the invention, the hydraulic control system comprises a hydraulic actuator having opposed openings adapted to alternately function as inlets and outlets for moving an element of the actuator in opposite directions, a pump for supplying fluid to the actuator. A meter-in valve individual to each opening is provided to which fluid from the pump is supplied and a pair of lines extends from the respective meter-in valves to the respective openings of the actuator. A controller alternately supplies pressure to the respective meter-in valves for controlling the direction of movement of the load. A second pair of lines extends from the first pair of lines to tank and a variable relief valve is positioned in each of the second pair of lines. When the controller is moved to actuate one of the meter-in valves for supplying fluid to one of the openings of the actuator, the controller also actuates the variable operated relief valve associated with the line of the first pair of lines extending from the other of the openings of actuator to control the flow out of the other opening. The controller thus simultaneously controls the fluid flow to the actuator and controls the fluid flow from the actuator thereby simultaneously controlling the driving and braking functions of the system. Description of the drawings: Fig. 1 is a schematic diagram of a hydraulic system embodying the invention, Fig. 2 is a graph of driving and braking functions versus positions of a controller in a hydraulic system embodying the invention. Referring to Fig. 1, the hydraulic system embodying the invention comprises a pump 10 that supplies fluid under pressure though a first pair of lines 11, 12 through meter-in valves 13, 14 to lines 15, 16 and selective openings A and B of an actuator depending upon which of the meter-in valves 13, 14 is actuated, that is line 15 is working line and line 16 is return line or vice versa. A controller C, herein shown as a manual controller, functions to supply pilot pressure from a pilot pressure pump P and produce a varying pilot signal through lines 18, 19 selectively to meter-in valves 13, 14. The controller C also functions when moved in one direction to supply pilot pressure to line 18 to meter-in valve 13 to supply also pilot pressure through line 20 to a variable pressure operated relief valve 21 in line 22 connected to line 16 so as to control flow out of opening B permitting fluid to flow through line 23 to tank functioning to brake or decelerate the load. Thus the return line includes the sections 16, 22, 23 in the situation above. Similarly, the controller C is connected so that when pilot pressure is applied through line 19 to meter-in valve 14 for controlling flow of fluid to opening B, pilot pressure is also supplied through line 24 to a pilot variable pressure controlled relief valve 25 in a line 26 connected to line 15 extending to opening A of the actuator 17 for controlling flow through line 27 to tank T. In the situation under consideration, line 16 is the working line and lines 15, 26, 27 are the return line. Thus, the controller C when moved to supply pilot pressure to one meter-in valve for supplying fluid from the pump 10 to one of the openings functions also to supply pilot pressure to the pilot pressure relief valve controlling flow out of the other openings of the actuator. The meter-in valves 13, 14 as shown and described on perferably of the metering flow controlling type shown and described in US-A-4,201,052 or 4,253,157. In such a system, the maximum driving pressure is established by a pressure relief valve or by the pressure compensated pump, as shown in the patent. The meter-in valves 13, 14 may also be of the metering pressure controlling type shown and described in US-A-4,407,122. The meter-in valves 13, 14 may also be of the on-off type and the system will provide a simultaneous control of acceleration and deceleration as presently described. The meter-in valves 13, 14 may be part of a single valve body, as is well known in the art. Referring to Figs. 1 and 2, in operation with the lever in neutral, both valve actuator ports are blocked and the maximum allowable actuator pressure levels are applied to the meter-in valves 13, 14 as set by relief valves 21, 25. Moving the lever of controller C in either direction will initially proportionally lower the setting of one of the variable relief valves 21, 25 in the return line from the load. After an appropriate amount of lever movement (point A in Fig. 2), the meter-in function will be increasingly engaged and supply flow to accelerate the load. Controller C may be a manually operated hydraulic valve or an electrically operated variable valve such as a proportional solenoid valve. Alternatively, the controller C may comprise a mechanical device which functions to control the movement of one or the other of the meter-in valves 13, 14 and simultaneously control one or the other of the variable pressure relief valves 21, 25. The driving pressure level can be determined by either the valve meter-in function or by the maximum system pressure limitation. At another appropriate point (B) in Fig. 2 of the lever movement, the variable relief valve pressure setting has reached its minimum value, while the load driving flow and/or pressure is still increasing with increasing lever movement. Thus the driving torque is determined by the difference between the driving and braking pressure levels of which one or both can be fully controlled by the amount of lever movement (see Fig. 2). During operation at constant speed, the velocity is selected by the amount of lever movement beyond point "A". For deceleration, the lever is moved toward neutral causing the reverse of what is described above, i. e. decreasing driving flow and/or pressure and increasing braking pressure. By movement of the lever, the operator always has full control of either the driving or braking of the load within the maximum design parameters. It should be noted that the meter-in valves 13, 14 and the variable relief valves 21, 25 are preferably so constructed and arranged that, when changing the position of the control, the braking function is initiated before the driving function reaches its full value. By this feature, the moving element of the actuator 17 is always under control and cannot initiate somewhat of an uncontrolled movement under inertial or gravitational forces. After a transition time, the steady-state driving function as depicted in Fig. 2 will be reached. Thus it can be seen that movement of the controller controls simultaneously on the driving side, the flow and/or pressure to the load, and on the outlet or downstream side of the load, the pressure level. It can be seen that this differs from the currently employed pressure regulating systems where either the pressure/flow on the inlet side is controlled for acceleration or pressure on the outlet side for deceleration. It can thus be seen that there has been provided a hydraulic system wherein the swing motion of the device being controlled is controlled throughout the desired movement; wherein both acceleration and deceleration may be controlled by one input signal from the same controller; wherein both acceleration and deceleration of large inertia loads, for example swing drives, can be achieved; wherein control of acceleration and deceleration is achieved by controlling both accelerating pressure and decelerating pressure simultaneously; wherein the system functions on the basis of the difference between acceleration or driving pressure and deceleration or braking pressure; and wherein the pressure controlling the swing motion comprises the only actuator connection to tank.

Claims: A hydraulic control system comprising a hydraulic actuator (17) having opposed openings (A, B) adapted to alternately function as inlets and outlets for moving an element of the actuator in opposite direction, a pump (10) for supplying fluid to the actuator (17), meter-in valves (13, 14) to which fluid from the pump (10) is supplied, a pair of lines (15, 16) extending from the respective meter-in valves (13, 14) to the respective openings (A, B) of the actuator (17), a controller (C) for alternately actuating a respective meter-in valve (13, 14) for controlling the direction of movement of the load, characterized by a second pair (22, 23; 26, 27) of lines extending from the first pair of lines (15, 16) to tank (T) and a variable pressure relief valve (21; 25) positioned in each line (22, 23; 26, 27) of the second pair of lines, said controller (C) being constructed and arranged such that when it is actuated to supply pressure to one (13) of the meter-in valves for supplying fluid to one (A) of the openings of the actuator (17), the controller (C) also actuates the variable relief valve (21) positioned in the other line (22, 23) of the second pair of lines extending from the other of the openings of actuator (17) to control the flow out of the other opening (B) so that the controller (C) substantially simultaneously controls the flow to the actuator and the flow from the actuator thereby simultaneously controlling the driving and braking functions of the system. The hydraulic system set forth in claim 1 wherein each said meter-in valve (13, 14) and the associated pilot operated relief valve (21, 25) are so constructed and arranged that the control of the braking function is initiated before the control of the driving function. The hydraulic system set forth in claim 1 or 2 wherein each meter-in valve (13, 14) and its associated pilot operated relief valve (21, 25) are constructed and arranged such that the braking function reaches a minimum value while the driving function continues to increase as the pilot signal increases. The hydraulic system set forth in any of claims 1-3 wherein said meter-in valves (13, 14) are of the metering type. The hydraulic system set forth in any of claims 1-4 wherein said controller (C) is of the pilot pressure type for supplying pilot pressure for actuating said meter-in valves (13, 14). The hydraulic system set forth in any of claims 1-5 wherein said controller (C) is of the manual type. The hydraulic system set forth in any of claims 1-6 wherein said controller (C) is of the electrohydraulic type. The hydraulic system set forth in any of claims 1-7 wherein each said meter-in valve (13, 14) is of the pressure controlling type. The hydraulic system set forth in any of claims 1-8 wherein each said meter-in valve (13, 14) is of the flow controlling type. The hydraulic system set forth in any of claims 1-9 wherein each said meter-in valve (13, 14) is of the on-off type. The hydraulic system set forth in claim 1 wherein said controller (C) is of the mechanical type and is adapted to move the meter-in valve directly and to actuate the variable pressure relief valve directly. A method of controlling the hydraulic control system of any of claims 1-11 comprising the steps of : controlling the movement of one or the other of the meter-in valves (13; 14) to control the flow of pressure of fluid to one opening (A) of the actuator (17), and simultaneously controlling the pressure of fluid out of the actuator (17) from the other opening (B) of the actuator, such that the driving and braking functions are substantially simultaneously controlled. The method of controlling a hydraulic system set forth in claim 12 wherein said step of controlling the pressure of fluid out of the actuator comprises utilizing a controller to variably control the pressure of the fluid and simultaneously control the movement of the meter-in valves. The method of controlling a hydraulic system set forth in claim 13 wherein the braking function is initiated before the driving function. The method of controlling a hydraulic system set forth in claim 15 wherein the braking function reaches a minimum value while the driving function continues to increase as the controller is moved.

Inventors: LONNEMO KURT ROLAND, LONNEMO, KURT ROLAND
Applicants: VICKERS INC, VICKERS INCORPORATED
Application year: 1990
Main classification: F15B13
IPC codes: F15B13, E02F9, F15B11