HYDRAULIC CONTROL SYSTEM

Abstract: A hydraulic control system comprising a hydraulic actuator (20), a pump system (22) for supplying fluid, and a directional valve means (27, 34, 35) for controlling flow to and from the actuator through a pair of actuator lines (32, 33). A controller (23) alternately supplies a first fluid pilot pressure (C1, C2) to pressure translating valves (90) which supply a second pilot pressure (C1a, C2a) to the directional valve means for operating same. The second pilot pressure (C1a, C2a) is a reduced pump pressure or obtained from any other source.

Description: This invention relates to a hydraulic control system as described in the preamble to claim 1. In such a known system (US-A-3,927,603) pilot pressure is from a source of pressurized air where a so-called amplifier is used to prepare a reduced pressure of proper level. However, such a mixed system using air and hydraulic fluid is not desirable in many applications. The invention is intended for environments where long hydraulic lines between a controller and a directional valve are found, for example, in aerial work platforms. In such a system, it is not uncommon to provide a pilot operated directional valve for each actuator which is controlled by a manually operated controller through a pilot hydraulic circuit. The directional valve functions to supply hydraulic fluid to the actuator to control the speed and direction of operation of the actuator. In addition, the directional valve for each actuator controls the flow of hydraulic fluid out of the actuator. In aerial work platforms and the like, the manually operated controller is on the elevated platform and long pilot lines extend from the source of pilot pressure to the manually operated controller and from the controller to the directional valve. Each function of the valve includes a manually operated controller and respective pilot lines to and from the directional valves. In addition, a common tank line is provided from all of the controllers. Such long lines result in a sluggish response that makes it difficult to precisely position the aerial work platform. The long lines also add weight and are costly. In some instances, dual pilot lines are provided where a second controller is provided at the base of the aerial work platform. The weight of the pilot lines often necessitates the addition of counter weights to the aerial work platform which adds to the difficulty of moving the platform along the terrain. In such systems where pilot pressure is provided to the directional valve from a remote location, the long pilot pressure hydraulic lines especially at cold temperatures result in a large pilot pressure drop which prevents adequate system response to the hydraulic signal initiated by the controller. It has heretofore been suggested that the directional valves be controlled by electrohydraulic valves on the directional valve with electric wires extending to a manually operated controller on the aerial work platform. Such systems may include solenoid operated pressure reducing valves that provide a pilot pressure to the directional valve. However, it has been found that in the environment in which such systems are used, as in the case of an aerial work platform, the system is more susceptible to malfunction. Furthermore, the owners of such vehicles are usually lessors and find great difficulty in obtaining skilled personnel for maintaining mechanical, hydraulic and electronic systems. The high frequency repair and difficulty in obtaining qualified personnel for maintenance have resulted in the demand for systems which are exclusively hydraulic for various purposes such as aerial work platforms with the aforementioned problems and difficulties of inadequate response, weight and cost. Such problems also exist in the hydraulic systems shown in US-A-4,201,052, 4,407,122, 4,418,612, 4,480,527 and 4,569,272. The hydraulic systems shown therein are intended to accurately control the position and speed of operation of the actuators. In such systems, the directional valves comprise pilot operated meter-in valves and separate pilot operated meter-out valves. A pilot controller supplies pilot pressure selectively to the meter-in valve to apply pressure to one of the lines of the actuator and to open the meter-out valve of the other line of the actuator. provision is made for sensing the maximum load pressure in one of a series of valve systems controlling a plurality of actuators and applying the higher pressure to the load sensing pump system. In addition, load drop check valves are provided preventing return flow to the meter-in valve when it is in neutral. Inherent leakage in the meter-in valve can adversely affect the hydraulic signal especially in cold temperatures by providing substantial back pressure. Among the objectives of the present invention are to provide a system which results in rapid response to a hydraulic signal from a controller for all operating condictions; which overcomes the problem of long pilot lines especially in cold weather; which permits the use of smaller pilot lines and smaller hydraulic controllers thereby reducing the weight and cost; and which in one form provides for smooth starting and stopping of a load and accurate positioning of the load, as in high inertia loads such as swing drives. Solution to this problem can be found in the independent claim 1. In accordance with the invention, a hydraulic control system comprising a hydraulic actuator having opposed openings adapted to alternately function as inlets and outlets for moving the element of the actuator in opposite directions, a pump system for supplying fluid, and a directional valve provided to which the fluid from the pump is supplied for controlling flow to and from the actuator. A pair of lines extends from the directional valve to the respective openings of the actuator. A controller alternately supplies a first fluid pilot pressure to pressure translating valves associated with the directional valve for reducing the pressure from the pump system or any other source and supplying a second reduced pilot pressure to the directional valve for controlling the flow to and from the actuator. Preferably, the directional valve comprises a meter-in valve and a meter-out valve associated with each line to the actuator for controlling flow out of the actuator. Each meter-in valve and meter-out valve is operated by the second pilot pressure from the pressure translating valve. In a modified form, novel means are provided for achieving smooth starting and stopping and positioning of a load, as in high inertia load such as swing drives. Embodiments of the invention will be described in connection with the drawings, wherein Fig. 1 is a partly schematic sectional view of a hydraulic system in which the invention is to be inserted, Fig. 2 shows how to insert the hydraulic system embodying the invention, Fig. 3 is a fragmentary sectional view on an enlarged scale of a portion of the system shown in Fig. 2, Fig. 4 is a curve of the second pilot pressure versus controlled input (angle), Fig. 5 is a partly schematic sectional view of a portion of a modified form of a hydraulic system embodying the invention, Fig. 6 is a partly schematic sectional view of a further modified form of hydraulic system embodying the invention, Fig. 7 is a partly schematic sectional view of a further modified form of hydraulic system embodying the invention utilized on swing drives. The invention is particularly applicable to hydraulic systems of the type shown in Fig. 1 being utilized with an actuator 20, herein shown as a linear hydraulic actuator. A pump system 22 may comprise a variable displacement pump having load sensing control or a fixed displacement pump including a load sensing relief valve. Fluid from the pump system 22 is directed through a pressure port P to a supply line 25 and to an inlet passage of an inlet passage 26 of a meter-in valve 27 that functions to direct and control the flow of hydraulic fluid to one or the other of the actuator lines 32, 33 and to the ports A or B of the actuator 20. The meter-in valve 27 comprises a bore in which a spool is positioned which can be shifted by pilot pressure or is maintained in a neutral position by springs. The spool normally blocks the flow from the pressure passage 26 to the actuator lines 32, 33. When actuated, a controller 23 delivers pilot pressure C1 through pilot line 28 to the left hand end of meter-in valve 27 or, as the case is, pilot pressure C2 through pilot line 29 to the right-hand end of meter-in valve 27, so that the spool thereof is shifted to the right or left allowing hydraulic fluid to flow through the actuator line 33 and to the port B of the actuator 20 or through line 32 to port A. The hydraulic system further includes a meter-out valve means 34, 35 for returning the fluid from that end of the actuator which is not pressurized. The meter-out valve 34 controls the flow from (returning) actuator line 32 to tank line 36 and meter-out valve 35 from line 33 to line 36. Each meter-out valve 34 or 35 includes a poppet valve 65 which, when unseated, brings the meter-out valve 34 or 35 in its unseated position. Poppet valve 65 has a piston, one side thereof being connected to pilot lines 28 or 29 and the other side to a bleed line 47 which is connected, through orifice 49, to the tank line 36. Pilot pressure supplied to the piston of poppet valve 65 can also be influenced by further poppet valves 41, 42 and therfore also the operating conditions of meter-out valves 34 or 35. When pilot pressure is applied to either pilot line 28 or 29, it is also applied to poppet 65 of either meter-out valves 34 or 35, so that one of the valves is actuated to throttle the returning flow from the associated end of actuator to tank line 36. It can thus be seen that the same pilot pressure which functions to determine the direction of opening of the meter-in valve 27 also functions to determine and control the opening of the appropriate meter-out valve 34, 35 so that the fluid in the actuator can return to the tank line 36. The hydraulic system further includes spring loaded drop check valves 37, 38 in the lines 32, 33 and spring loaded anti-cavitation valves 39, 40 which are adapted to open the lines 32, 33 to the tank passage 36. The system also includes a back pressure valve 44 associated with the tank line T. Back pressure valve 44 functions to minimize cavitation when an overrunning or a lowering load tends to drive the actuator down. A charge pump relief valve 45 is provided to take excess flow above the inlet requirements of the pump 22 and apply it to the back pressure valve 44 to augment the fluid available to the actuator. Provision is made for sensing the maximum load pressure in one of a multiple of valve systems controlling a plurality of actuators and applying that higher pressure to the load sensitive variable displacement pump 22. Each valve system comprises a passage 50 connecting the actuator lines 32, 33 and including a shuttle valve 51 that is shifted by pressure in the adjacent actuator line 32 or 33 and supplies the high pressure to a line 78 that extends to a further shuttle valve 80 that receives load pressure from an adjacent valve system through a line 81. Shuttle valve 80 senses which of the pressures is greater and shifts to apply the higher pressure to the pump system 22. Thus, each valve system in succession incorporates shuttle valves 80 which compare the load pressure therein with the load pressure of an adjacent valve system and transmit the higher pressure to the adjacent valve system in succession and finally apply the highest load pressure to pump system 22. The single meter-in valve 27 may be replaced by two meter-in valves. The details of the preferred construction of the elements of the hydraulic circuit are more specifically described in the afore-mentioned US-A-4,201,052, 4,407,122, 4,418,6l2, 4,480,527 and 4,569,722. Fig. 2 is a partly schematic sectional view of a hydraulic system embodying the invention, the elements having corresponding reference numerals where applicable to those of Fig. 1. In accordance with the invention, as shown in Fig. 2, instead of applying pilot pressure through pilot lines 28, 29 directly to each end of the meter-in valve 27, the first pilot pressure C1, C2 as prepared by the pilot controller 23 is amplified in pressure translating valves 90 to become second pilot pressure C1a, C2a. So the pilot lines 28, 29 include in input section (not shown) connected to the pilot controller 23 and an output section 28a, 29a connecting the respective pressure translating valve 90 to the respective end of the meter-in valve 27, as presently described. Energy for each pressure translating valve 90 is taken from supply pressure as delivered by the main pump 22 and such supply pressure is throttled down to provide the second pilot pressure C1a, C2a which therefore is a reduced pressure from supply pressure. The pilot controller 23 supplies the first pilot pressure C1, C2 selectively to the end of one or the other of the pressure translating valves 90 which provides pressure fluid to the respective end of the meter-in valve 27 sufficient to shift the entire spool of the meter-in valve 27 and meter-out valve 34 or 35. As shown in Fig. 3, each pressure translating valve 90 comprises a body 91 having an opening 111 connected to the input section of the pilot pressure line 28 or 29. Opening 111 is registered to a valve bore 95 which intersects a supply pressure passage 96 extending to the supply passage 26. Valve bore 95 also intersects output section 28a, 29a of the pilot line and a tank passage 97. A spool 98 is slidably positioned in the valve bore 95 and has a small metering land 99 which normally intersects and shuts off the supply pressure passage 96. The spool 98 also has a first piston-like end 100 and a second piston-like end 101 to be shifted in one or the other direction by pressure acting on these ends 100, 101. Piston-like end 100 has a control edge which cooperates with the tank passage 97 so that pressure fluid in the valve bore 95 can escape into the tank passage 97 when the valve 90 is not operated, whereas when spool 98 is shifted upwardly in the drawings, such escaping flow is metered and finally shut off. Output section 28a, 29a of the pilot line has an extension passage 103 including an orifice to communicate the second pilot pressure C1a, C2a to a return chamber 102 at second end 101 of spool 98. The first pilot pressure C1, C2 and eventually the force of a valve spring 109 are acting upon the first end 100 of spool 98. Depending on the difference of these forces, land 99 is shifted relatively to supply passage 96 and controls the flow and the level of the second pilot pressure C1a, C2a through output section 29a to that one end of the meter-in valve 27 to which it is assigned. Controller 23 is of conventional construction and comprises a pair of valve control units which are spring loaded to their OFF position wherein they hold the manual control level in neutral position. Movement of the lever in one of two directions opens the valve control units to direct the first pilot pressure selectively to one or the other of the pressure translating valves 90. Body 91 of each pressure translating valve 90 comprises a first section 104 having a reduced portion 105 threaded into the body of the valve system and having a control chamber 106 adjacent the lower end 100 of spool 98. The body 91 includes a second section 107 threaded onto first section 104. A flanged inlet member 108 is provided between body section 107 and body section 104. Inlet member 108 includes an inlet passage 111 which extends from the respective input section of pilot pressure line 28 or 29 to the control chamber 106. The valve spring 109 is interposed between the spool 98 and inlet member 108 and yieldingly urges the spool 98 axially inwardly. A second spring 110 is interposed between the body section 104 and the member 108 to urge the member 108 axially outwardly. As the controller 23 is operated, control chamber 106 takes first pilot pressure C1, C2 and spool 98 is shifted upwardly in Fig. 3 so that land 99 is uncovering the opening of the supply passage 96 into the valve bore 95. Pressure fluid from the pump 22 or other pressure source is entering the valve bore 95 and the output section 28a, 29a of pilot line and propagates through passage 103 into the return chamber 102. As the second pilot pressure is built up in this manner, the spool 98 eventual]y is moved back until a force balance is created at spool 98 between spring force 109 and first pilot pressure force on the one hand and second pilot pressure force on the other hand. Land 99 takes a control position so that fluid flow on supply pressure is throttled down to the pressure level of the second pilot pressure. The required second pilot pressure C1a, C2a to move the meter-in valve 27 is thus made up by the first pilot pressure plus the opposing force created by spring 109. This is shown schematically in Fig. 4 which is a curve of second pilot pressure versus controller input or movement which is usually an angular movement of the manual controller. The threshold point is determined by the sum of the force necessary to overcome the preload spring force of the meter-in valve 27 and the dead band of the meter-in valve 27. As the controller 23 is moved (with increasing α; Fig. 4) to app]y (increasing) pilot pressure, the amount of fluid required is only thath to pressurize the input section of the pilot line and to shift the spool 98 of the pressure translating valve 90, i. e. with a miniscule amount of fluid. Energy to be applied to one or the other end of the meter-in valve 27 and to one of the meter-out valves 34, 35 is taken from fluid supplied by the main pump 22. So the input sections of the pilot lines may be of light-weight construction. A feature of the pressure translating valve shown in Figs. 2 and 3 is the arrangement wherein the threshold point can be adjusted. This is achieved by threading the portion 107 on the portion 104 to change the force of the spring 109. This permits adjustment of the pressure translating valve in the field in order to change the threshold of each part of the system which is controlled by each of the pressure translating valves independently of the other part of the system. Thus, the adjustment of the spring force makes it possible to adjust for tolerances in the pilot controller and the directional valve in order to adjust the threshold to minimize dead band. Such adjustment is achieved at low cost thereby providing a more efficient hydraulic system. In accordance with the invention, it is possible to utilize a controller positioned remotely from the valves being controlled and at the same time obviating the problems heretofore inherent, namely, slow response at cold temperatures. ln addition, it is possible to provide a hydraulic system which requires long connecting hoses of much lesser diameter which are less costly and occupy less space. Moreover, the system provides for individual adjustment of the system when it is in place thereby enlarging flexibility of the system. Referring to Fig. 5, where an adjustment is not needed, the body 91b of pressure reducing valve 90a can be provided in one section with an inlet 111a extending to control chamber 106a. Referring to Fig. 6, pilot pressure need not be obtained from the main supply passages 26, but can be obtained from any other source P P providing fluid to each pressure translating valve 90. In the modified form of system shown in Fig. 7, provision is made for providing a smooth stopping and starting of the load and accurate positioning of the load in high intertia load situations such as swing drives on an excavator. This is achieved by providing a pin-like piston 113, which is interposed between the end 101 of the spool 98 and a feedback line 114a extending from the return chamber 102 to the actuator passage 33. A similar passage 114b extends from the other return chamber to actuator passage 32. In operation, when, for example, the pilot controller is operated to deliver pilot pressure C1 and to shift the spool of meter-in valve 27 in a direction such that pressure is applied to port B of the actuator and the meter-out valve 34 associated with port A is opened, the pressure of fluid from port B is applied through feedback line 114a onto piston 113 of the left-hand valve 90 tending to move the spool 98 in a direction to reduce the second pilot pressure C1a through line 28a and causing the meter-in spool 27 to be moved in a more centering direction compared with the case without pressure feedback. This tends to center the spool of the meter-in valve 27. By this arrangement, the function of the meter-in valve 27 is changed from load flow control to load pressure control. Thus, it is possible to obtain smooth starting and stopping and accurate loading under high inertia loads. By this arrangement, it is possible to achieve a similar control as in US-A-4,407,122. The arrangement of Fig. 7 thus permits improved control of the swing drive. By changing the rate of the spring and the pressure translating valve, it is possible to modify the swing drive to obtain a more steep or less steep characteristic of pressure versus flow. It can be appreciated where load pressure control is required in only one direction, the pressure tending to oppose the centering of the meter-in valve spool can be applied to one side only of the hydraulic system. Although the invention has been particularly described in connection with systems utilizing separate meter-in valves and meter-out valves, it is also applicable to directional valves that incorporate a single spool that functions to control meter-in flow and meter-out flow and is pilot pressure operated. It can thus be seen that there has been provided a system which overcomes the problems of long pilot lines especially in cold weather; which permits the use of smaller pilot lines and smaller hydraulic controllers thereby reducing the weight and cost; which results in rapid response to a hydraulic signal from a controller for all operating conditions; and which in one form provides for smooth starting and stopping of a load and accurate positioning of the load, as in high inertia loads such as swing drives on an excavator.

Claims: A hydraulic control system comprising a hydraulic actuator (20) having opposed openings adapted to alternately function as inlets and outlets for moving the element of the actuator in opposite directions; a pump (22) for supplying fluid to said actuator (20); a directional valve means (27, 34, 35) to which the fluid from the pump (22) is supplied, said directional valve means (27, 34, 35) being pilot pressure controlled; a pair of actuator lines (32, 33) extending from said directional valve means (27, 34, 35) to said respective openings of said actuator (20); a pilot controller (23) for alternately supplying fluid at a first pilot pressure (C1, C2) through pilot lines (28, 29) to said directional valve means (27, 34, 35) for controlling the direction of movement thereof, each said pilot line (28, 29) includes a pressure translating valve (90) which is operable by said first pilot pressure (C1, C2) and outputs a second pilot pressure (C1a, C2a) into an output section (28a, 29a) of said control line (28, 29); characterized in that said fluid at first pilot pressure is hydraulic fluid, and said fluid at second pilot pressure is hydraulic fluid which is supplied from said pump (22) or any other hydraulic pressure source to produce said second pilot pressure (C1, C2a) as a reduced pressure from said pump pressure (P) or from said other hydraulic pressure source, that said pressure translating valve (90) comprises a spool (98) having a land (99) which controls hydraulic fluid flow through a supply pressure passage (96) to said output section (28a, 29a) of said pilot line (28, 29) that said spool (98) has one end (100) subjected to said first pilot pressure (C1, C2) thus being acted upon in opening direction of the valve, and that said spool (98) has the other end (101) subjected to said second pilot pressure (C1a, C2a) thus being acted upon in shutting direction of the valve. The hydraulic control system set forth in claim 1 wherein said pressure translating valve (90) includes adjustable spring means (109) for adjusting the second pilot pressure (C1a, C2a) for tolerances in the pilot controller (23) as well as in the directional valve means (27, 34, 35) to adjust the threshold and minimize the dead band. The hydraulic control system set forth in claim 2 wherein said pressure translating valve (90) includes a first body section (104) having a control chamber (106) adjacent to one end (100) of the spool (98), a second body section (107) threaded on said first body section (104), an inlet member (108) having an opening (111) therethrough communicating with said control chamber (106) in the first body section (104) , said spring means (109) being interposed between said one end (100) of the spool (98) and said inlet member (108) such that rotation of the second body section (107) relative to the first body section (104) adjusts the spring force which acts on the end (100) of the spool (98). The hydraulic control system set forth in claim 3 including second spring means (110) yieldingly urging the inlet member (108) axially outwardly relative to said first body section (104) into engagement with said second body section (107). The hydraulic control system set forth in any of claims 1 through 4 wherein at least one of said pressure translating valves (90) is connected through a feedback line (114a, 114b) to that one of said actuator lines (32, 33) which is connected to pump pressure when said at least one pressure translating valve (90) is operated, said feedback line (114a, 114b) developing a force which acts onto said one pressure translating valve (90) in shutting direction. The hydraulic control system set forth in claims 5 wherein said feedback line (114a, 114b) contains a piston (113) which develops said force and is connected to said pressure translating device (90). The hydraulic control system set forth in claims 5 or 6 wherein a pair of feedback lines (114a, 114b) is provided, each being assigned to a respective pressure translating valve (90). The hydraulic control system set forth in any of claims 1 through 7 wherein said directional valve (27, 34, 35) includes a meter-in valve (27) to which the fluid of the pump (22) is supplied, and a pair of meter-out valve means (34, 35), each being associated with one of the actuator lines (32, 33).

Inventors: LONNEMO, KURT ROLAND
Applicants: VICKERS INCORPORATED
Application year: 1988
Main classification: F15B13
IPC codes: F15B13, F15B11