HYDRAULIC CIRCUIT

Abstract: A hydraulic circuit for cushioning shock when feeding discharged pressure oil from one hydraulic pump to a plurality of actuators while gradually reducing the flow quantity fed to the actuator under a high load whereas increasing the flow quantity to the other actuators under a low load for increasing the operating speed of said actuators. The hydraulic circuit is provided with a throttle (R) in the load pressure introducing passage of a pressure compensation valve (18) provided in one of a plurality of operating valves (2). The circuit is further provided with relief valves (22,22) adapted to perform relief action by load pressure in an actuator (3) operated by the operating valve (2), and with throttle (24) arranged so that pressure may be generated at the drain side of each of these relief valves.

Description: FIELD OF THE INVENTION The present invention relates to a hydraulic circuit system for supplying pressurized oil to plurality of hydraulic actuators. DESCRIPTION OF THE PRIOR ART From Japanese Unexamined Patent Publication No. 58-117140 it is known that a plurality of closed-center type directional control valves are provided in a pressurized oil discharge line or passage of single hydraulic pump employed in hydraulic circuit system so as to supply pressurized oil (which is discharged from the single hydraulic pump) to a plurality of hydraulic actuators through the directional control valves. In the hydraulic circuit system having the above construction, when the plurality of the directional control valves are simultaneously operated, the pressurized oil discharged from the single pump is supplied only to lightly-loaded ones of the actuators. In the conventional hydraulic circuit system, this problem is resolved as follows: Namely, in the conventional hydraulic circuit system, a pressure-compensated flow control valve is provided in a connecting circuit interposed between each of the directional control valves and each of the actuators. In operation, the pressure set point of each of the pressure-compensated flow control valves substantially corresponds to the highest one of load pressures of each of the actuators to enable the single hydraulic pump to supply its discharged pressurized oil to the plurality of the actuators (which are different in load pressure with each other) even when the plurality of the directional control valves are simultaneously operated. Namely, in the conventional hydraulic circuit system having the above construction, when the plurality of the directional control valves are simultaneously operated, each of the pressure-compensated flow control valves is set at the highest one of the load pressures of each of the actuators, thereby permitting the single hydraulic pump to supply or deliver its discharged pressurized oil to each of the actuators at a flow rate depending on a valve-opening ratio of each of the directional control valves. However, in the above conventional hydraulic circuit system, in a condition in which the pressurized oil discharged from the pump is supplied to only one (hereafter referred to as the first actuator) of the actuators through one of the directional control valve. when the pressurized oil is supplied to the remaining actuators through the remaining directional control valves, each of the pressure-compensated flow control valves is immediately set at a load pressure of each of the actuators to have the pump deliver its discharged pressurized oil to each of the actuators at a flow ratio depending on a valve-opening ratio of each of the directional control valves. As a result, the flow rate of the pressurized oil delivered to the first actuator suddenly decreases so that a working speed of the first actuator is also suddenly lowered to administer a shock to a load. For example, in a hydraulic circuit system employed in a power shovel machine having a single hydraulic pump for supplying pressurized oil to: a hydraulic motor used for traveling in the machine; a boom hydraulic cylinder: and an arm hydraulic cylinder, the pressurized oil discharged from the pump is supplied to the motor used for traveling in the machine by operating one of directional control valves employed in the hydraulic circuit system. Under such circumstances, when the pressurized oil discharged from the pump is supplied to the boom cylinder and the arm cylinder too by operating the remaining directional control valves, a flow rate of the pressurized oil supplied to the motor used for traveling is suddenly reduced to administer a shock to the machine in traveling. As is in the above, in case that the directional control valves are simultaneously shifted from their neutral positions to their operating positions by means of pilot pressures, each of the directional control valves has the same changeover stroke, and, therefore has the same valve opening area. Consequently, each of the actuators receives the pressurized oil at the same flow rate. Namely, for example, in case that one of two actuators only supports its load, and, therefore does not move it in a condition in which the other of the actuators moves its load, the pressurized oil supplied to the one of the actuators is merely wasted, whereas the pressurized oil supplied to the other of the actuators lacks in flow rate to lower the working speed of the other of the actuators. Namely, for example, in the power shovel machine in which the one of the actuators forms a swing motor of the machine, and the other of the actuators forms a boom hydraulic cylinder of the machine, in case that the power shovel machine swingably moves its bucket up and down to cut a side wall of a trench in a condition in which the bucket is pressed against the side wall of the trench, the swing motor swingably drives an upper vehicle body of the shovel machine in a horizontal plane so as to press the bucket against the side wall of the trench. In operation under such circumstances, the boom hydraulic cylinder of the shovel machine swingably moves its boom up and down in a vertical plane, thereby permitting the bucket to cut the side wall of the trench. In such cutting operation, since the swing motor of the shovel machine is not turned after the bucket is brought into contact with the side wall of the trench, the pressurized oil is substantailly not supplied to the swing motor in a condition in which the swing motor only has the bucket press against the side wall of the trench. In contrast with this, during the above cutting operation, since it is necessary for the boom hydraulic cylinder of the shovel machine to swiftly move the bucket up and down, the pressurized oil must be supplied to the boom hydraulic cylinder at a considerable flow rate. However, since there is no difference in valve opening area of the directional control valves, the pressurized oil is supplied to each of the swing motor and the boom hydraulic cylinder at the same flow rate. As a result, the pressurized oil supplied to the swing motor is wasted thereon, whereas the pressurized oil supplied to the boom hydraulic cylinder lacks in flow rate. DE-C-3605312 discloscs a pressure-compensated valve function which comprises an auxiliary spool and a spool or slide for balancing, when one of a number of actuators is operated, the operate pressure or load pressure of an A port communicated with the actuator and the pressure of a LS port and for compensating, when the actuator and another actuator are operated and the load pressure of the A port of another actuator is higher than the load pressure of the A port of the actuator, the load pressure of the A port of the actuator so as to divide the amount of pressurised oil into the actuator and another actuator. That means, when the actuator is only operated, the slide is operated so as to decrease the load pressure of the A port and to lead the load pressure in to the LS port so that-the load pressures of these two ports are balanced. When both of the actuators and another actuator are operated and the load pressure of the A port of another actuator is higher than that of the actuator, LS pressure of the actuator makes the auxiliary spool move towards the right side so as to restrict the hydraulic circuit between a P port and the A port of the actuator. As a result of this restriction, the opening area of the port of the actuator is controlled so as to correspond to the opening area of the port of another actuator so that the load pressure of the A port of the actuator is compensated whereby the load pressure of the A port of the actuator corresponds to that of another actuator. Summarising, according to DE-C-3605312 when the actuator and another actuator are operated and the load pressure of the A port of another actuator is higher than that of the actuator, the load pressure of the A port of the actuator is compensated by moving the auxiliary spool. However, according to this known device, when the actuator and another actuator are operated, since each of the load pressures of the actuator and the other actuator are not detected and the slide is not moved, it is impossible to control the amount of the pressurised oil supplied to the actuator. With respect to DE-C-3605312 it is an object of the invention to control the stroke of the spool and therewith the amount of pressurised oil supplied to one of the actuators by detecting the load pressure of the one of the actuators. This object is solved by the features of the claim. In accordance with the present invention, it is possible to advantageously reduce a shock in operation: namely, in a condition in which a hydraulic pump supplies pressurized fluid or oil to only a first one of the actuators by operating a first one of the directional control valves, when another one of the directional control valves is operated, another one of the actuators gradually leads its load pressure into a pressure-compensated flow control valve provided in the first one of the directional control valves to cause the setting pressure of the pressure-compensated flow control valve to gradually increase. As a result, the flow rate of the pressurized oil supplied to the first one of the actuators gradually decreases to gradually lower a working speed of the first one of the actuators so that the shock is substantially removed. On the other hand, when the load pressure of the first one of the actuators to which the pressurized oil is supplied through the first one of the directional control valves increases, the relief valves of the first one of the directional control valves relieve the pressurized oil to produce a pressure in the drain sides of the relief valves. Under the influence of such pressure produced in the drain sides of the relief valves, the valve opening area of the first one of the directional control valve is reduced. Consequently, when the plurality of the directional control valves are simultaneously operated, the first one of the directional control valves which is connected with the highly-loaded first one of the actuators is smaller in valve opening area than any other ones of the directional control valves connected with other ones of the actuators. As a result, the flow rate of the pressurized oil supplied from the first one of the directional control valves to the first one of the actuators reduces, whereas the flow rate of the pressurized oil supplied from the other ones of the directional control valves to the other ones of the actuators increases. Consequently, in a condition in which the first one of the actuators merely supports its load not to move it while the other ones of the actuators move their loads, the flow rate of the pressurized oil supplied to the first one of one actuators reduces and the flow rate of the pressurized oil supplied to the other ones of the actuators increase to advantageously increase the working speeds of the other ones of the actuators. The above object, additional objects, additional aspects and advantages of the present invention will be clarified to those skilled in the art hereinbelow with reference to the following description and accompanying drawings illustrating a preferred embodiment of the present invention according to principles of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic diagram of a hydraulic circuit; Fig. 2 is an embodiment of a restriction means employed in the hydraulic circuit shown in Fig. 1; and Fig. 3 is a schematic diagram of a hydraulic crcuit of the present invention. DESCRIPTION OF THE PREFERRED EMBODIMENTS As shown in Fig. 1, a plurality of directional control valves 2 are provided in 2 discharge line or passage 1a of a hydraulic pump 1, so that pressurized oil discharged from the pump 1 is supplied to a pair of hydraulic actuators 3 by operating the directional control valves 2. One of the actuators 3 forms a hydraulic motor used for traveling in a power shovel machine, and the other of the actuators 3 forms a boom hydraulic cylinder of the power shovel machine a boom member of which is swingably moved up and down by the cylinder in operation. Each of the directional control valves 2 is provided with a valve body 4 forming a spool hole 5 in which is slidably received a spool 6 through which communication of pressurized fluid or oil from a first pump port 7, a first reservoir port 9, a second pump port 11 and a second reservoir port 13 to a first outlet port 8, a first port 10, a second outlet port 12 and a second port 14 respectively is permitted and blocked off. In each of the directional control valves 2, the spool 6 is normally held in its neutral position by a spring 15 so as to block off the above communication of the pressurized oil. In operation, under the influence of a pilot pressure supplied to a first pressure chamber 16 of the directional control valve 2, the spool 6 is moved to the left as viewed in Fig. 1 so as to be held in its first operating position in which: the first pump port 7 communicates with the first outlet port 8; and the second port 14 communicates with the second reservoir port 13, respectively. On the other hand, under the influence of another pilot pressure supplied to a second pressure chamber 17 of the directional control valve 2, the spool 6 is moved to the right as viewed in Fig. 1 so as to be held in its second operating position in which: the second pump port 11 communicates with the second outlet port 12; the first port 10 communicates with the first reservoir port 9; the first outlet port 8 communicates with the first port 10 through a pressure-compensated flow control valve 18: the second outlet port 12 communicates with the second port 14 through another pressure-compensated flow control valve 18, respectively. At this time, in each of the directional control valves 2, pressure of the pressurized oil received in the first outlet port 8 or the second outlet port 12 is detected through a drill hole (not shown) formed in the spool 6 and a detecting hole 19. These pressures thus detected in a pair of the directional control valves 2 are compared with each other in shuttle valves 20 formed in the directional control valves 2 so that a higher one of the thus compared pressures is supplied to a spring chamber 18a of each of pressure-compensated flow control valves 18, whereby each of the pressure-compensated flow control valves 18 is set at a pressure corresponding to such higher one of the thus compared pressures, thereby permitting each of the pressure-compensated flow control valves 18 to be set at a pressure corresponding to the highest one of load pressures when the plurality of the directional control valves 2 are simultaneously operated. As a result, the single hydraulic pump 1 can supply the pressurized oil to the plurality of the hydraulic actuators 3 which are different in load pressure from each other. A restriction means R is provided in a load pressure lead-in circuit of each of the pressure-compensated flow control valves 18 provided in one of the directional control valves 2, which one is used for supplying the pressure oil to one of the actuators 3, for example such as a hydraulic motor used for traveling in the power shovel machine, so that load pressures supplied to the spring chambers 18a of the pressure-compensated flow control valves 18 are prevented from varying at a drastic rate. Incidentally, it is possible to employ the following construction: namely, as shown in Fig. 2, a bypass passage r 2 provided with a check valve r 1 is connected with the restriction means R in parallel therewith so as to permit the pressurized oil to smoothly flow from the spring chamber 18a to the shuttle valve 20, and to prevent a load pressure from being supplied to the spring chamber 18a at a drastic rate. In other words, it is possible to gradually increase the setting pressure of the pressure-compensated flow control valve 18 by preventing the load pressure from being supplied to the spring chamber 18a of the pressure-compensated flow control valve 18 at a drastic rate. As described above, in a condition in which the hydraulic pump 1 supplies the pressurized oil to one of the actuators 3, for example such as the hydraulic motor used for traveling in the power shovel machine through one of the directional control valves 2 in operation, when another one of the directional control valves 2 is operated to supply the pressurized oil discharged from the pump 1 to another one of the actuators 3, for example such as the boom hydraulic cylinder of the power shovel machine, a load pressure of the boom hydraulic cylinder Is gradually supplied to the spring chamber 18a of the pressure-compensated flow control valve 18 so as to gradually increase the setting pressure of the pressure-compensated flow control valve, so that the pressurized oil is supplied from this directional control valve 2 to the boom hydraulic cylinder at a moderate rate, whereby the pressurized oil supplied to the hydraulic motor used for traveling in the power shovel machine decreases at a moderate rate to moderately decelerate the power shovel machine in traveling, thereby permitting the machine to decrease its traveling speed without experiencing any shock. Now, with reference to Fig. 3, an embodiment of the present invention will be described in detail. As for this embodiment of the present inventtion shown in Fig. 3, its parts denoted by the same reference numerals as those employed in the Figs. 1 and 2 have the same constructions as those parts. Consequently, in order to avoid redundancy in description, these parts of the embodiment of the present invention, which are denoted by the same reference numerals as those of parts according to Figs. 1 and 2 will not be described hereinbelow. Formed in the valve body 4 of the embodiment of the present invention are: a first oil port 21 a through which the first port 10 communicates with the first reservoir port 9; and a second oil port 21 b through which the second port 14 communicates with the second reservoir port 13, respectively. A relief valve 22 is provided in each of the first oil port 21 a and the second oil port 21 b . In the relief valve 22, a poppet valve 26 is slidably mounted in a sleeve-lime main body 25 provided with an inlet port 23 and a restriction orifice 24, while resiliently held against an opening or seat of the inlet port 24 by a spring 27 to block off communication of pressurized oil from the inlet port 23 to the restriction orifice 24. The inlet port 23 communicates with the first port 10 or the second port 14. On the other hand, the restriction orifice 24 communicates with the second reservoir port 13 or the first reservoir port 9. A spring chamber 27a of the relief valve 22 communicates with the first pressure chamber 16 or the second pressure chamber 17 through a port 28 and a shuttle valve 29. Incidentally, in the shuttle valve 29, as soon as pressure is applied at the port 28, a ball element of the shuttle valve 29 will move over to an inlet port 30 to close it off, and leave the connection from the port 28 to the first pressure chamber 16 or the second pressure chamber 17 open to supply the pressurized oil thereto, as shown in Fig. 3. Similarly, when pressure is applied at the inlet port 30, the ball element will move over to the port 28 to close it off, and leave the connection from the inlet port 30 to the first pressure chamber 16 or the second pressure chamber 17 open to supply the pressurized oil thereto. In this embodiment of the present invention shown in Fig. 3, in case that the pilot pressure is applied to the first pressure chamber 16 of each of the directional control valves 2 to move the spool to the left, thereby permitting the spool to be held at its first operating position to supply the pressurized oil discharged from the pump 1 to each of the actuators 3, since each of the pressure-compensated flow control valves 18 is set at a pressure corresponding to the highest one of load pressures which are supplied to the pressure chamber 18a of each of the pressure-compensated flow control valves 18 through the shuttle valve 20, it is possible to supply, without any trouble, the pressurized oil discharged from the single hydraulic pump 1 to each of the actuators 3 which are different in load pressure from each other. In addition, it is also possible to supply the pressurized oil to each of the actuators at the same flow rate, because the pressurized oil is distributed to each of the actuators at a rate corresponding to the valve opening area of each of the directional control valves, i. e., at a flow rate corresponding to a ratio, in communication area, of the first pump port 7 to the first outlet port 8, and there is no difference in stroke of the spool 6 and communication area between the directional control valves 2. At this time, as is in the above case, in case that the hydraulic motor used for traveling in the power shovel machine is not turned to merely hold a load in a stationary condition while the boom hydraulic cylinder is extended in operation, a pressure of the pressurized oil received in the first port 10 of one of the directional control valves 2 increases and applies the pressure of pressurized oil to the relief valve 22 through the first oil port 21a to unseat the poppet valve 26 of the relief valve 22, thereby permitting the pressurized oil to flow into the first reservoir port 9 through the restriction orifice 28. As a result, since pressure is increased upstream of the restriction orifice 28, the thus increased pressure is supplied to the second pressure chamber 17 through the spring chamber 27a, port 28 and the shuttle valve 29 to move the spool 6 to the right. Consequently, the first pump port 7 and the first outlet port 8 of one of the directional control valves 2 reduce their communication areas so as to: reduce the flow rate of the pressurized oil supplied to the motor used for traveling, and increase the flow rate of the pressurized oil supplied to the boom hydraulic cylinder.

Claims: A hydraulic system comprising: a plurality of closed-center type directional control valves (2); and a plurality of pressure-compensated flow control valves (18) each of which is provided in a connecting circuit interposed between each of said directional control valves (2) and each of a plurality of hydraulic actuators (3) each of which is controlled by each of said directional control valves in operation, each of said pressure-compensated flow control valves (18) being set at a setting pressure corresponding to the highest one of load pressures of each of said hydraulic actuators (3), characterized in that a restriction means (R) is provided in a load pressure lead-in passage of each of said pressure-compensated flow control valves (18), which each of said pressure-compensated flow control valves is provided in one of said plurality of said directional control valves (2), a pair of relief valves (22) are provided in a first and a second port (10, 14) respectively, said first and second port being in communication with pressure chambers of each of said hydraulic actuators (3) to permit each of said relief valves (22) to relieve pressurized fluid under the influence of load pressure of each of said hydraulic actuators (3) controlled by said directional control valves (2), and said hydraulic circuit system comprises another restriction means (24) for producing a pressure in a drain side of each of said relief valves (22), whereby each of said directional control valves (2) reduces its opening area under the influence of said pressure produced in said drain side of each of said relief valves (22).

Inventors: AKIYAMA T, ISHIZAKI N, SHINOHARA S, SHIRAI K, TAKIGUCHI T, AKIYAMA, T., ISHIZAKI, N., SHINOHARA, S., SHIRAI, K., TAKIGUCHI, T., AKIYAMA, T. KAWASAKI FACT. OF K.K. KOMATSU SEISA-, ISHIZAKI, N. KAWAS. FACT. OF K.K. KOMATSU SEISA-, SHINOHARA, S. KAWAS.FACT. OF K.K. KOMATSU SEISA-, SHIRAI, K. KAWASAKI FACT.OF K. K. KOMATSU SEISA-, TAKIGUCHI, T. KAWASAKI FACT.OF K.K. KOMATSU SEISA-
Applicants: KOMATSU MFG CO LTD, KABUSHIKI KAISHA KOMATSU SEISAKUSHO
Application year: 1990
Main classification: F15B11
IPC codes: F15B13, E02F9, F15B11