HYDRAULIC CIRCUIT FOR HYDRAULIC CONSTRUCTION AND WORKING MACHINE

Abstract: A hydraulic circuit for a construction and working machine includes hydraulic signal generating means (30,36) for generating a hydraulic signal from a hydraulic source utilizing a discharge pressure oil from a pilot pump (4) for an operating system or a pressure oil from a load-side oil chamber for an actuator for supporting a working device when a receiving section of the hydraulic signal generating means receives an external signal, a main relief valve (23,24) and a port relief valve both having boost receiving means for boosting a relief pressure of these relief valves to a value higher than a normal set pressure when the hydraulic signal from the hydraulic signal generating means is applied to the boost receiving means, operation suppressing means for holding a neutral position of a hydraulic selector valve for operating a specific one of the actuators irrespective of an operation command to the hydraulic selector valve (29) when a receiving section of the operation suppressing means receives an external signal, and signal generating means for arbitrarily generating a signal and stopping the generation of the signal by an operator, wherein the signal from the signal generating means is supplied directly to the receiving sections of the hydraulic signal generating means and the operation suppressing means, or supplied thereto through a relay circuit comprised of a pressure switch and a make contact, wherein the relay circuit functions to hold outputting of the signal received from the signal generating means as far as the operation switch is in a closed state.

Description: The present invention relates to a hydraulic circuit for a hydraulic construction and working machine. Conventionally, a construction and working machine is utilized for not only its original work but also multiple purposes owing to its good mobility and stability of a machine body. Particularly in a hydraulic construction machine having a working device overhung from the machine body, the usage thereof tends to become wide. Fig. 6 shows an example of a hydraulic shovel. The hydraulic shovel is primarily used for excavation of earth and sand at a level lower than a ground level. The material to be excavated contains hard and soft rock, earth and sand in a mixed condition, and the specific gravity of the material is unknown. Accordingly, the resistance to the excavating fluctuates according to the material, and an impact load is often applied to the machine. To prevent such a fluctuating load from adversely affecting the strength of the machine body, boom 38, arm 39, bucket 40 and members related thereto, and also ensure a sufficient stability of the machine during operation, the hydraulic shovel is provided with a limiting device for limiting an output and a holding power of hydraulic cylinders 14, 15 and 16 within a predetermined value. In other kinds of work in which the load does not fluctuate or an impact load is not applied in use of the working device or the hydraulic shovel, e.g., in hoisting a heavy load from the ground or pulling a pile in the earth by rotating the boom 38 and the arm 39 to be operated by the hydraulic cylinders 14 and 16, respectively, there is no problem of stability of the machine body and the strength of the boom 38 and the arm 39 even if the operating forces of the hydraulic cylinders 14 and 16 are greater than those in the earlier described construction work. Such increased possible operating forces are rather advantageous to increase the hoisting power of a pulling power, thus contributing to an improvement in capacity of the machine for this kind of work. Fig. 3 is a diagram of an essential part of a hydraulic system in a general-purpose hydraulic shovel of the construction and working machine. The operation of the hydraulic cylinder 14 for the boom 38 as shown in Fig. 6 will now be described. Referring to Fig. 3, discharge pressure oil from a main pump 3 is allowed to flow into a hydraulic selector valve group A, and a main relief valve 23 is provided in a line leading from the main pump 3 to the hydraulic selector valve group A so as to limit the discharge oil pressure within a predetermined value, thereby protecting parts of the hydraulic circuit and preventing excess outputs from various actuators. When a hydraulic selector valve 8 for the boom 38 is operated, the pressure oil admitted into the hydraulic selector valve group A serves to contract the hydraulic cylinder 14, wherein a contracting force of the hydraulic cylinder 14 is limited so as not to exceed a predetermined value in accordance with the set pressure of the main relief valve 23. Further, port relief valves 17 and 18 are provided in branch lines extending from lines leading from the hydraulic selector valve 8 to head-side and rod-side oil chambers of the hydraulic cylinder 14, so as to prevent an external force greater than the above predetermined value applied to the boom 38 by any factors, from causing an abnormal stress in the boom 38 which may cause breakage and deformation. The set pressure of the port relief valves 17 and 18 is normally set to be slightly higher than that of the main relief valve 23, so that there may be no problem in a normal excavating operation by the boom 38, and only when an abnormal external force is applied to the boom 38, the hydraulic cylinder 14 may be freely expanded and contracted. Although the above description is directed to the hydraulic cylinder 14 only with reference to Fig. 3, the same measures are provided for the other hydraulic cylinders 15 and 16. However, in the hoisting or pulling work with the set pressure of each relief valve set at a value suitable for the excavating work there occurs a problem that the working efficiency is impaired. To cope with this problem, the prior art has often taken the following measures. That is, as shown in Fig. 4, the main relief valve 23 is provided with a boosting pilot oil chamber 27 for boosting the set pressure of the main relief valve 23 by means of a pilot pressure. Furthermore, the set pressure of a port relief valve 17a leading to the load-side oil chamber of the hydraulic cylinder 14 is set to be higher than that in the normal excavating work in a range such that a static load stress generating in each part of the machine is permitted. In hoisting a heavy load or pulling a pile where no impact load is applied, a switch 30 located near a driving seat is operated as required to actuate hydraulic signal generating means 31 which in turn supplies a discharge pressure oil from a pilot pump 4 as a signal to the boosting pilot oil chamber 27. Although the above description is directed to the hydraulic cylinder 14 for the boom 38, the same measures are taken for the other hydraulic cylinders 15 and 16 for the bucket 40 and the arm 39, respectively. According to the hydraulic circuit as shown in Fig. 4, the operating force of the hydraulic cylinders can be increased by the increase in the set pressure of the main relief valve 23 during hoisting or pulling work which generate no impact load, and a resisting force against an external force can of course be increased by an increased amount of the set pressure of the port relief valve 17a. Fig. 5 is a diagram of an essential part of a hydraulic system as improved from the prior art shown in Fig. 4. Referring to Fig. 5, the port relief valve 17 leading to the load-side oil chamber of the hydraulic cylinder 14 is provided with a boosting pilot oil chamber 25 similar to the boosting pilot oil chamber 27 for the main relief valve 23. Both the boosting pilot oil chambers 25 and 27 are connected through pilot lines to the hydraulic signal generating means 31. In such an improved hydraulic system, when the switch 30 is in an open state, the set relief pressures of the main relief valve 23 and the port relief valve 17 are maintained at the normal set pressures suitable for excavating work thus avoiding the application of an excess load due to an external force. For hoisting or pulling work generating in which no impact load is applied as mentioned above with reference to Fig. 4, when the switch 30 is closed, the set pressures of the main relief valve 23 and the port relief valve 17 are increased to thereby increase the operating force of the hydraulic cylinder and the holding force in the oil chamber of the hydraulic cylinder 14 leading to the port relief valve 17. In the construction machine employing the above-mentioned hydraulic circuit, there is a chance that an excavating force could be instantaneously increased during excavation as well during the hoisting or pulling work. In this case, the hydraulic signal generating means 31 may be operated by depressing an auto-return switch such as a push-button switch, wherein the operator must make sure of absolutely no application of an impact load; otherwise the strengths of the boom 38, the arm 39 and the bucket 40 must be increased so as to endure the increased excavating force, and the machine body must be so constructed as to endure a gravity of the strengthened working device. As described above, the prior art hydraulic circuit for the construction and working machine is designed to increase the set pressure of the main relief valve by operating the switch or the push-button switch with the set pressure of the port relief valve previously boosted in hoisting a heavy load or pulling a pile or the like. However, when the engine is unintentionally stopped by any factors, or the operator erroneously opens the switch or releases his hand from the push-button switch whilst a heavy load is being hoisted there is a danger that the heavy load will fall. Moreover, as the excavating work can be carried out with the set pressure of the main relief valve remaining increased, an excess force can be applied to the attachments at all times. Even if the set pressure of the main relief valve is not increased, the attachments inclusive of the boom, the arm and the bucket as well as the machine body will be adversely effected by an external force since the set pressure of the port relief valve is set to be higher than that in the normal excavating work. Reference is made to US Patent No 4,365,429 which discloses a maximum lift system for a hydraulic hoe having a hydraulic hoist cylinder and associated circuit, a double-acting hydraulic wrist cylinder with an associated wrist circuit, a dual pressure relief valve in the hoist circuit that has a normal lower operating setting and can be hydraulically biased to a higher maximum setting, and actuating means to supply a bias signal to the relief valve, the improvement wherein there is a lockout means in the wrist circuit that is selectively operable to block the wrist circuit and lock the wrist cylinder in whatever position it is then in, and the actuating means operates the lockout means simultaneously with supplying the bias signal. Reference is also made to DE-A-3 012 844 which, discloses a drive circuit for a hydraulic load-handling machine in which the maximum output pressure of said circuit is determined by a main relief valve provided on the delivery side of a hydraulic pump, said drive circuit comprising means for increasing the relief pressure of said main relief valve above a rated pressure of said circuit for a short period of time of about a few seconds and then automatically returning said relief pressure to the level of said rated pressure. This arrangement enables a maximum output pressure to be normally determined by a main relief valve but which when necessary, is capable of producing automatically a tenacious sprint power in a manner similar to a mechanical drive. An object of the invention is to provide a safety hydraulic circuit which may automatically suppress an excavating work, for example, where an impact load is applied to the attachments when the relief set pressures of the main relief valve and the port relief valve are exceeded, and further may prevent that a heavy load being hoisted will fall even when the engine is stopped or the operator erroneously releases his hand from the push-button switch. According to the invention there is provided a hydraulic circuit for a hydraulic construction and working machine having a motor, a main pump adapted to be driven by said motor, a plurality of hydraulic selector valves adapted to be supplied with a discharge pressure oil from said main pump, and a plurality of actuators for operating a plurality of working devices, said actuators being selectively supplied with the pressure oil from said hydraulic selector valves to effect various operations; said hydraulic circuit comprising a main relief valve for relieving a discharge pressure from said main pump when the discharge pressure exceeds a set pressure, said main relief valve including a boost receiving means for increasing said set pressure of said main relief valve on receipt of a signal, signal generating means for control by an operator to selectively generate said signal, and operation suppressing means for maintaining a neutral position of at least one of said plurality of hydraulic selector valves irrespective of operation of said signal generating means, and a plurality of port relief valves for preventing the pressures in lines connected to said actuators becoming higher than a set port relief pressure: characterised in that there are provided at least some of said port relief valves include boost receiving means for increasing the set port-relief pressures of said some of said port relief valves on receipt of said signal so that the set pressures of said main relief valve and said at least some port relief valves are increased at the same time; said signal generating means is controlled by an electrical signal selectively provided by a switch; and said operations suppression means is connected to said switch and is adapted to be operated by receipt of said electrical signal from said switch. During normal construction work, e g, excavating, the signal generating means operates to stop the generation of a signal therefrom, and the working is started. Under this condition, the set pressure of the main relief valve and the port relief valve is maintained at a normal value suitable for the excavating work. Therefore, there is no possibility that an impact load or an excess load will be applied to the attachment to cause breakage thereof during the excavating work. During operations which require a maximum capacity such as the hoisting of a heavy load or pulling of a pile, the signal generating means is operated to apply a signal directly to or through the relay circuit to the receiving sections of the hydraulic signal generating means and the operation suppressing means. As a result, the hydraulic signal from the hydraulic signal generating means is applied to the boost receiving means of the main relief valve and the port relief valve to thereby boost the relief set pressure to a value higher than the normal value mentioned above. Accordingly, the working power and the holding power of the attachment can be increased. At the same time, since the receiving section of the operation suppressing means receives the signal from the signal generating means, the opertaion suppressing means functions to hold a hydraulic selector valve in a neutral position for operating a specific actuator, e.g. , a bucket in a hydraulic backhoe, irrespective of an operation command to the actuator, which actuator is necessary for the excavating work or the like but unnecessary for the hoisting or pulling work. Therefore, the specific actuator, e.g., the bucket is inhibited from being actuated. That is, the excavating work cannot be naturally carried out when the main relief valve and the port relief valve have an increased set pressure, thus protecting the attachment or the like. When the pressure oil in the load-side oil chamber of an actuator for supporting the working device and receiving a load thereof, (e.g., a hydraulic boom cylinder in a hydraulic backhoe) is supplied as a hydraulic source to the hydraulic signal generating means, and the signal from the signal generating means is supplied through the relay circuit to the receiving sections of the operation suppressing means and the hydraulic signal generating means, an output signal from the relay circuit continues to be generated as far as the pressure switch in the relay circuit is maintained operative by the pressure oil from the load-side oil chamber of the hydraulic boom cylinder, thereby maintaining the boosted condition of the main relief valve and the port relief valve. Accordingly, even when the engine is unintentionally stopped during operation or the operator erroneously stops the signal from the signal generating means, there is no danger that the working device and the heavy load supported thereby will fall. At the same time, the output signal from the relay circuit also continues to be supplied to the selector valve as the operation suppressing means. Other objects and features of the invention will be more fully understood from the following detailed description and appended claims when taken with the accompanying drawings. Fig. 1 is a diagram of an electric and hydraulic system according to a first preferred embodiment of the present invention; Fig. 2 is a diagram of an electric and hydraulic system according to a second preferred embodiment of the present invention; Fig. 3 is a diagram of a hydraulic system in a general-purpose hydraulic shovel; Fig. 4 is a diagram of a hydraulic system in a hydraulic shovel having a boosting device in the prior art; Fig. 5 is a diagram of a hydraulic system which is an improvement of Fig. 4; and Fig. 6 is a side view of the hydraulic shovel. There will now be described some preferred embodiments of the present invention with reference to the drawings. Fig. 1 is a diagrammatic view of an electric and hydraulic system of part of a hydraulic circuit according to a first preferred embodiment of the present invention as applied to a hydraulic shovel. Referring to Fig. 1, reference numeral 1 designates an motor for driving main pumps 2 and 3 and a pilot pump 4. Pressure oil from the main pump 2 is adapted to flow into a hydraulic selector valve group A consisting of hydraulic selector valves 6, 7, 8 and 9, while pressure oil from the main pump 3 is adapted to flow into a hydraulic selector valve group B consisting of hydraulic selector valves 10, 11, 12 and 13. Further, pressure oil from the pilot pump 4 is employed primarily as a hydraulic pressure source for an operating system, and it is fed to a line 42. Reference numeral 14 designates a hydraulic boom cylinder adapted to be operated by select operation of the hydraulic selector valves 8 and 12; 15 designates a hydraulic bucket cylinder adapted to be operated by select operation of the hydraulic selector valve 7; and 16 designates a hydraulic arm cylinder adapted to be operated by select operation of the hydraulic selector valves 13 and 9. Reference numerals 17, 18, 19, 20, 21 and 22 designate port relief valves provided in branch lines 14c, 14d, 15c, 15d, l6c and l6d extending from lines leading to head-side and rod-side oil chambers 14a, 14b, 15a, l5b, 16a and l6b of the above-mentioned hydraulic cylinders, respectively; and 23 and 24 designate main relief valves for preventing that the discharge oil pressure from the main pumps 2 and 3 will become higher than a set pressure. Generally, a relief set pressure of the port relief valves is set to be slightly higher than that of the main relief valves. Reference numerals 25, 26 and 27, 28 designate boosting pilot oil chambers provided at relief pressure setting sections of the port relief valves 17 and 22 and the main relief valves 23 and 24, respectively. The boosting oil chambers 25 to 28 function as boost receiving means for boosting the relief set pressure of the port relief valves 17 and 22 and the main relief valves 23 and 24 up to a predetermined value when a signal pressure is applied to the boosting pilot oil chambers. Reference numeral 29 designates a selector valve for normally opening pilot lines 43 and 43a or pilot lines 44 and 44a extending from a remote control valve 41 so that a pilot pressure as an operating signal from the remote control valve 41 may be transmitted via the pilot lines 43, 43a or 44, 44a to the hydraulic selector valve 7 to thereby operate the same, while being selected when a signal is received by a receiving section of the selector valve 29, closing the pilot lines 43 and 44 from the remote control valve 41 and communicating the pilot lines 43a and 44a with each other to lead the same to the hydraulic selector valve 7. Thus, the selector valve 29 functions as operation suppressing means for automatically maintaining a neutral position of the hydraulic selector valve 7 when a signal is applied to the selector valve 29, in spite of the condition where the remote control valve 41 is operated to generate a pilot pressure in the pilot lines 43 and 44. Reference numeral 31 designates hydraulic signal generating means for boosting the relief set pressure of the port relief valves 17 and 22 and the main relief valves 23 and 24. That is, when a receiving section of the hydraulic signal generating means 31 receives a signal, pressure oil from the line 42 is employed as a hydraulic pressure source, and the pressure oil as a pilot pressure is transmitted through a pilot line 45 to the boosting pilot oil chambers 25, 26, 27 and 28, thereby boosting the relief set pressure. Reference numeral 30 designates a switch provided near a driving seat and adapted to be arbitrarily operated by an operator. The switch 30 functions to switch the transmission and cutting of the signals to the respective receiving sections of the selector valve 29 as the operation suppressing means and the hydraulic signal generating means 31. The switch 30 may be constructed as a push-button switch adapted to switch on only when it is depressed. The operation of the above-mentioned preferred embodiment will now be described. When using the hydraulic shovel as a normal construction machine (ie to excavate), the switch 30 is maintained open. Accordingly, both the selector valve 29 and the hydraulic signal generating means 31 are not operated, and the pilot lines 43 and 44 from the remote control valve 41 are communicated through the selector valve 29 to the pilot lines 43a and 44a, respectively, thereby making the hydraulic selector valve 7 in an operative condition. Further, as the pilot line 45 communicates through the hydraulic signal generating means 31 to a tank 5, no hydraulic signals are applied to the boosting pilot oil chambers 25, 26, 27 and 28. Accordingly, the port relief valves 17 and 22 and the main relief valves 23 and 24 maintain respective normal set pressures suitable for excavating work, thus preventing the application of an excess force to working devices such as the boom 38, arm 39 boom 38, arm 39 and bucket 40 as well as a machine body and thereby ensuring stability and safety during excavating work. In some kinds of work, the hydraulic shovel lifts hangs and moves a heavy load such as equipment and materials in a similar manner to a crane. In such a kind of work which is different from excavating work, the working speed is low, and a known weight is handled. Furthermore, no impact load is generated. Therefore, even when the load on the boom 38 and the arm 39 as shown in Fig. 6 is increased, safety in working from the viewpoints of strength and stability is ensured, and the working efficiency is improved. However, there is a possibility that excavation work could be carried out with the lifting capacity still increased, thus causing damage to the machine. In the electric and hydraulic system shown in Fig. 1, when the switch 30 is closed, a signal is applied to the hydraulic signal generating means 31, and the pressure oil from the line 42 is brought into communication through the hydraulic signal generating means 31 to the pilot line 45. Then, the pressure oil is applied to the boosting pilot oil chambers 25, 26, 27 and 28. Therefore, the relief set pressures of the port relief valves 17 and 22 and the main relief valves 23 and 24 are set higher than those in normal excavating work. Accordingly, a discharge pressure from the main pumps 2 and 3 to be applied to the head-side oil chamber 14a of the hydraulic boom cylinder 14 and the rod-side oil chamber 16b of the hydraulic arm cylinder 16 and a retaining pressure of the above oil chambers can be increased, thereby increasing the lifting capacity of the arm 39 at its forward end and its heavy load retaining capacity and improving the working efficiency. At the same time, the signal from the switch 30 is also applied to the selector valve 29 as the operation suppressing means, and the hydraulic selector valve 7 is brought into an inoperative condition. That is, even when the remote control valve 41 is operated to generate a pilot pressure in the pilot line 43 or 44, the pilot lines 43a and 44a are brought into communication with each other through an internal passage in the selector valve 29 having been selected in its position, thereby maintaining a neutral position of the hydraulic selector valve 7. Therefore, the hydraulic bucket cylinder 15 is not operated irrespective of the operation of the remote control valve 41. Consequently, while the relief set pressures of the relief valves 17, 22, 23 and 24 are being increased, the excavating work generating an impact load can be automatically suppressed. Fig. 2 shows an electric and hydraulic system according to a second preferred embodiment of the present invention, wherein the same parts as those in Fig. 1 are designated by the same reference numerals. The second preferred embodiment is different from the first preferred embodiment in the following ways. Firstly, while the pressure oil from the pilot pump 4 is employed as the hydraulic source for the hydraulic signal generating means 31 in the first preferred embodiment, the pressure oil from the branch line l4c extending from the head-side oil chamber 14a of the hydraulic cylinder 14 where a load pressure due to the dead weight of the working device, and the weight of an object to be lifted, etc. is employed as the hydraulic source for hydraulic signal generating means 35 consisting of a pressure reducing valve 36 and a selector valve 37 in the second preferred embodiment. Secondly, a relay circuit 32 is provided between each receiving section of the selector valve 29 and the hydraulic signal generating means 35 and the switch 30. In other words, the signal from the switch 30 is connected and cut through the relay circuit 32. The relay circuit 32 comprises a pressure switch 33 adapted to close an internal electric circuit when the pressure in the branch line l4c is increased near a normal relief set pressure of the port relief valve 17 and a contact 34 adapted to be closed when a signal is supplied from the switch 30. Once the contact 34 is closed, it continues to be closed and a signal irrespective of an open or closed state of the switch 30 as far as the pressure switch 33 is closed, thus forming a retaining circuit. Accordingly, during hoisting work with the hydraulic shovel having the electric and hydraulic system as shown in Fig. 2, in the event that the motor 1 is stopped for any reason and stops the supply of the discharge oil pressure from the pilot pump 4, or that the operator erroneously opens the switch 30 (or unintentionally releases the switch 30 if it is a push-button switch) there is no possibility that the boosted condition of the relief valves will be eliminated or that an object being hoisted will fall. Although the above-mentioned preferred embodiments employ electric and hydraulic signals as a signal medium in connection with the equipment to be used, needless to say a pneumatic signal and/or a mechanical cable-link may be employed solely or in combination. Further, although the description in the above preferred embodiments concerning an actuator refers to the boom, arm and bucket cylinders of the hydraulic shovel, the present invention may be of course applied to any other hydraulic construction and working machine such as a tractor shovel similar to the hydraulic shovel, wherein a working device is replaced for various purposes, and each working device is required to exhibit different outputs for different works. As described above, the hydraulic circuit according to the present invention is advantageously applied to a construction and working machine such as a hydraulic shovel to be subjected to various kinds of work which differ in load condition. That is, the set pressures of the main relief valve and the port relief valve which are suitably set for a normal construction work where an impact load is applied can be inercased within a range not influencing on an attachment and a machine body when the machine is subjected to any other works where no impact load is applied. Therefore, a variety of works can be efficiently effected by the same machine. Moreover, when the relief set pressure is increased, the execution of works which might generate an impact load is automatically suppressed to thereby prevent damage of the machine. According to another aspect of the present invention, a simple circuit is additionally provided to ensure safety in hoisting work, for example. That is, whilst hoisting a heavy load under an increased relief set pressure, even when the motor is stopped or the switch for increasing the relief set pressure is erroneously opened, the relief set pressure can be increased by a load pressure during hoisting the heavy load. Furthermore, once a signal is supplied from the switch, it continues to be output irrespective of the subsequent operation of the switch as long as the load pressure is not reduced. Therefore, it is possible to prevent the heavy load from falling whilst being hoisted, thus ensuring a safer hoisting operation. While the invention has been described with reference to specific embodiments, the description is illustrative and is not to be construed as limiting the scope of the invention. Various modifications and changes may occur to those skilled in the art without departing from the spirit and scope of the invention as defined by the appended claims.

Claims: A hydraulic circuit for a hydraulic construction and working machine having a motor (1), a main pump (2,3) adapted to be driven by said motor (1), a plurality of hydraulic selector valves (6-9, 10-13) adapted to be supplied with a discharge pressure oil from said main pump (2,3), and a plurality of actuators (14-16) for operating a plurality of working devices, said actuators (14-16) being selectively supplied with the pressure oil from said hydraulic selector valves (6-9, 10-13) to effect various operations; said hydraulic circuit comprising a main relief valve (23,24) for relieving a discharge pressure from said main pump (2,3) when the discharge pressure exceeds a set pressure, said main relief valve (23,24) including a boost receiving means (27,28) for increasing said set pressure of said main relief valve (23,24) on receipt of a signal, signal generating means (31,37) for control by an operator to selectively generate said signal, operation suppressing means (29) for maintaining a neutral position of at least one (7) of said plurality of hydraulic selector valves (6-9,10-12) irrespective of operation of said signal generating means (31,37), and a plurality of port relief valves (17-22) for preventing the pressures in lines connected to said actuators (14-16) becoming higher than a set port relief pressure; characterised in that there are provided at least some of said port relief valves (17, 22) include boost receiving means (25, 26) for increasing the set port-relief pressures of said some of said port relief valves on receipt of said signal so that the set pressures of said main relief valve (23, 24) and said at least some port relief valves (17, 22) are increased at the same time; said signal generating means (31, 37) is controlled by an electrical signal selectively provided by a switch (30); and said operations suppression (29) means is connected to said switch (30) and is adapted to be operated by receipt of said electrical signal from said switch (30). A hydraulic circuit as claimed in claim 1, characterised in that said signal generating means (31, 37) is an hydraulic signal generating means which generates a hydraulic signal for said boost receiving means (25, 26, 27, 28) and is controlled by an electrical signal, said electrical signal being provided by said switch (30); and a relay circuit (32) for outputting said electrical signal from said switch (30) to said hydraulic signal generating means (31, 37) and maintaining said electrical signal even after said switch (30) ceases to provide said electrical signal. A hydraulic circuit as claimed in claim 1 to 2, characterised in that said relief valves (23, 24) serve to relieve pressure in said hydraulic circuit when said pressure exceeds a first preset pressure, said boost means (27-28) serves to increase said first preset pressure of said relief valves (23, 24) to a second higher preset pressure in response to a control signal; and said plurality of port relief valves (17-22) serve to prevent the pressure applied to said actuators (14-16) exceeding a third preset pressure. A hydraulic circuit as claimed in claim 3, characterised in that said signal generating means (30-36) includes a manually operable switch (30) to cause said signal to be produced. A hydraulic circuit as claimed in claim 4, characterised in that said manually operable switch (30) comprises an electrical switch. A hydraulic circuit as claimed in claim 5, characterised in that said manually operated switch (30) is connected to a relay circuit (35) for outputting said signal, and for holding said output of said signal so long as the pressure of a hydraulic source is higher than a predetermined pressure irrespective of the open or closed state of said manually operated switch (30) after said relay circuit has been operated. A hydraulic construction and working machine including a motor (1), a main pump (12) adapted to be driven by said motor (1), a plurality of hydraulic selector valves (6-9, 10-13) adapted to be supplied with a discharge pressure oil from said main pump (2, 3), and a plurality of actuators (14-16) for operating a plurality of working devices, said actuators (14-16) being selectively supplied with the pressure oil from said hydraulic selector valves (6-9, 10-13) to effect various operations, characterised by a hydraulic circuit as claimed in any one of claims 1 to 6.

Inventors: MIYAOKA, SATOSHI
Applicants: KABUSHIKI KAISHA KOBE SEIKO SHO
Application year: 1990
Main classification: E02F3
IPC codes: E02F9, E02F3, F15B11