Safety device for hydraulic closed circuit

Abstract: A variable displacement hydraulic pump (11) and a hydraulic motor (18) are connected in a closed circuit (17A, 17B). A pressure oil supply means (100) includes the variable displacement hydraulic pump (11) and a tilt controlling means (16) for controlling the tilt angle of the hydraulic pump (11) and supplying an amount of oil, corresponding to the tilt angle of the hydraulic pump, to the hydraulic motor (18). When rotation of a prime mover (6) is detected by a rotation detecting means (101), an opening and closing valve (102) is changed over to a first position in which the pressure oil supply means (100) is permitted to supply oil. When stopping of the prime mover (6) is detected by the rotation detecting means (101), the opening and closing valve (102) is changed over to a second position in which the pressure oil supply means (100) is inhibited from supplying oil. Upon starting of the prime mover (6), at least the opening and closing valve (102) remains in the second position, and the tilt controlling means (16) increase its tilt angle from its neutral position so that the pressure oil supply means (100) supplies oil. Consequently, upon re-starting of the prime mover (6), oil is prevented from being supplied inadvertently to the hydraulic motor (18), and the safety upon starting is assured.

Description: This invention relates to a hydraulic closed circuit as defined by the features of the preamble of claim 1 for use with a construction machine or an industrial vehicle, and more particularly to a safety device for such a hydraulic closed circuit which is effective upon starting of a prime mover. A generic hydraulic closed circuit of the type described above is known from practice and shown in FIG. 8. Referring to FIG. 8, if a starter switch 2 is turned on when an operating lever 1 is at its neutral position, a battery 4 and a starter motor 5 are connected to each other via a relay 3, so that an engine 6 is started to rotate a variable displacement hydraulic pump 11 and a charge pump 12. Oil delivered by the charge pump 12 is introduced from the downstream side of a restrictor 13 into left and right cylinder chambers 16a and 16b of a tilt control cylinder 16 by way of a control valve 14 and a pair of pipe lines 15A and 158. The cylinder chambers 16a and 16b thus have an equal internal pressure, and accordingly, a piston 16c of the tilt control cylinder 16 is positioned at its neutral position wherein the amount of tilting motion of the variable displacement hydraulic pump 11 is set to zero to restrict the delivery from the variable displacement hydraulic pump 11 to zero. If the operating lever 1 is operated to change over the control valve 14 to a side thereof denoted by 1, then the pressure on the upstream side of the restrictor 13 acts upon the cylinder chamber 16a while the pressure on the downstream side of the restrictor 13 acts upon the other cylinder chamber 16b, the piston 16c is displaced leftwardly in FIG. 8 by a distance corresponding to a difference between the pressures on the opposite sides of the restrictor 13, thereby setting an amount of tilting motion of the variable displacement hydraulic pump 11. Consequently, the variable displacement hydraulic pump 11 delivers pressure oil by an amount corresponding to the thus set amount of tilting motion into a main pipe line 17A to rotate a hydraulic motor 18 forwardly. On the contrary, if the control valve 14 is changed over to the other side denoted by m, then an amount of tilting motion of the variable displacement hydraulic pump 11 is set in the reverse direction, and consequently, pressure oil is delivered into another main pipe line 17B to rotate the hydraulic motor 18 reversely. 19 is a crossover load relief valve and 20 is a flashing valve. A pair of check valves 21A and 21B is connected to the charge pump 12 by way of a pair of pipe lines 22a and 22b. The position of the operating lever 1 is detected by a switch 7. When the operating lever 1 is, for example, at its neutral position, the switch 7 assumes its "ON" position so that a coil 3C of the relay 3 is energized to close a switch 3S of the relay 3 to interconnect the starter switch 2 and the starter motor 5. Thus, only when the operating lever 1 is at its neutral position, starting of the engine 6 is permitted. To the contrary, if the operating lever 1 is operated, then the relay switch 3S is opened so that the engine 6 cannot be started. As a result, when the engine 6 is started, the variable displacement hydraulic pump 11 will not deliver pressure oil therefrom, thereby assuring the safety upon starting. However, when the temperature is very low, the viscosity of operating oil is very high and accordingly the flow resistance of oil in the individual pipe lines is very high. This will raise the following problems. In particular, if the engine 6 is started and then the control valve 14 is changed over to the 1 side, the pressures on the opposite sides of the restrictor 13 act upon the cylinder chambers 16a and 16b of the tilt control cylinder after a predetermined delay in response due to very low temperature, so that the piston 16c is displaced in the leftward direction in FIG. 8 and the vari- able displacement hydraulic pump 11 delivers pressure oil to the main pipe line 17A. By the pressure oil, the hydraulic motor 18 is caused to start its rotation to drive a load, for example, to drive a vehicle to run. When the temperature is very low, however, the torque loss at the variable displacement hydraulic pump 11 and the charge pump 12 is so high and/or the viscosity of lubricating oil in the engine 6 itself is so high that the engine may stall. If the operating lever 1 is returned to its neutral position immediately after such engine stall and then the starter switch 2 is turned on, then the engine 6 will be started because the relay switch 3S remains at its closed position. Since the pipe lines 15A and 15B are communicated with each other by way of the control valve 14 as the operating lever 1 is returned to its neutral position, the pressures within the hydraulic cylinders 16a and 16b are immediately made equal to each other. As a result, the piston 16c is returned from the leftwardly displaced position to the neutral position. In this instance, when oil discharged from the cylinder chamber 16a flows through the pipe line 15A, a high resistance acts upon the oil, so that it takes considerable time for the piston 16c to return to its neutral position. Accordingly, if the engine 6 is started before the piston 16c is returned to its neutral position, then pressure oil will be delivered from the variable displacement hydraulic pump 11 to activate the hydraulic motor 18 inadvertently although the operating lever 1 remains in its neutral position. It is an object of the present invention to provide a safety device for a hydraulic closed circuit which prevents pressure oil from being supplied to a hydraulic motor if a prime mover is restarted immediately after stopping thereof, due to very low temperatures. According to the invention this object is achieved by the features as defined in claim 1. The principle of the present invention is elucidated in Figure 1A, in which a hydraulic closed circuit is shown comprising a hydraulic motor 18; a pressure oil supply means 100 including a variable displacement hydraulic pump 11 driven by a prime mover 6 and a tilt control means 16 for controlling a tilt angle of the variable displacement hydraulic pump 11, the pressure oil supply means 100 being provided to supply pressure oil to the hydraulic motor 18 in accordance with a tilt angle of the variable displacement hydraulic pump 11 by way of either one of a pair of main pipe lines 17A and 17B connected to the variable displacement hydraulic pump 11; the hydraulic motor 18 and the variable displacement hydraulic pump 11 being connected in a closed circuit. According to the present invention, a safety device for such a hydraulic closed circuit as described just above comprises a rotation detecting means 101 for detecting a rotational condition of the prime mover 6, and an opening and closing valve means 102 having a first position in which the opening and closing valve means permits the pressure oil supply means 100 to supply pressure oil and a second position in which the opening and closing valve means inhibits the pressure oil supply means 100 from supplying pressure oil. When the stopping of the prime mover 6 is detected by the rotation detecting means, the opening and closing valve means 102 is changed over to the second position. When the prime mover 6 is started, the opening and closing valve means 102 is changed over to the first position and the tilt control means 16 may increase its tilt angle from its neutral position to permit the pressure oil supply means 100 to supply pressure oil. The insertion of a rotation detecting means and an opening and closing valve means into the safety device provides a second safety condition, apart from and in addition to the first safety condition being that the prime mover can only be started when the control valve for the tilt control means is placed in the neutral position. This second safety condition ensures that no pressure oil is supplied to the hydraulic motor 18 when the prime mover 6 is restarted immediately after the stopping thereof has occurred. There are several possibilities to ensure that this object is achieved. In a first embodiment according to the invention a hydraulic circuit is provided in which said opening and closing valve means is a valve of the hydraulic pilot type, arranged in a bypass pipe line connected to said first and second chambers of said tilt control means, said rotation detecting means and said change-over controlling means comprising a hydraulic pilot pressure line, connecting said oil supplying hydraulic pump to the pilot port of said hydraulic pilot valve. In this embodiment the tilt control means bring the swash plate of the variable displacement hydraulic pump in a neutral position immediately after the stopping of the prime mover is detected, so that no pressure oil can be delivered by that pump when the prime mover is restarted shortly after such stopping. According to a modification of this first embodiment the opening and closing valve means is an electro magnetically operated valve, arranged in a bypass pipe line connected to said first and second chambers of said tilt control means, said rotation detecting means and change-over controlling means comprising a rotation detecting sensor capable of placing said electro magnetically operated valve in the first position. In a second embodiment according to the invention a hydraulic circuit is provided in which said opening and closing valve means is a valve of the hydraulic pilot type arranged in a bypass pipe line interconnecting said main pipe lines, said rotation detecting means and said change-over controlling means comprising a hydraulic pressure line, connecting said oil supplying hydraulic pump to the pilot port of said hydraulic pilot valve, a restriction being provided in said hydraulic pressure line in order to delay the time of arrival at said pilot port of the pressure oil, supplied by said oil supplying hydraulic pump, said hydraulic pilot valve being placed in the second position when the hydraulic pressure in the hydraulic pressure line is reduced to a tank pressure and being placed in the first position after a predetermined delay time has lapsed since the starting of said prime mover. In this second embodiment a flow bypass is provided for the pressure oil, that could be delivered by the variable displacement pump during the period of time which is necessary for the variable displacement pump to arrive at its neutral position after stopping of the prime mover. According to a modification of this second embodiment said opening and closing valve means is an electro mechanically operated valve, arranged in a bypass line interconnecting said main lines, said rotation detecting means comprising a rotation detector sensor and said change-over controlling means including a neutral position detecting means for detecting the neutral position of said tilt control means, the electro magnetically operated valve being placed in the second position immediately after said prime mover is stopped and being changed over to the first position when the rotation of said prime mover as well as the neutral position of said tilt control means are both detected. The above and other objects, features and advantages of the present invention will become apparent from the following description and the appended claims, taken in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1A is a diagrammatic representation illustrating the principle of construction of a safety device for a hydraulic closed circuit according to the present invention; FIG. 1B is a schematic circuit diagram of a safety device for a hydraulic closed circuit showing a first embodiment of the present invention; FIG. 2 is a similar view but showing a modification to the safety device of FIG. 1B; FIG. 3 is a similar view but showing a second embodiment of the present invention; FIGS. 4 and 5 are similar views but showing two different modifications to the safety device shown in FIG. 3; FIG. 6 is a flow chart illustrating a process of operations of a controller of the safety device shown in FIG. 5; FIG. 7 is a schematic circuit diagram showing a further modification common to the safety devices of FIGS. 1B and FIG. 3; and FIG. 8 is a schematic circuit diagram showing a conventional safety device for a hydraulic closed circuit. DETAILED DESCRIPTION OF THE PREFERRED EMB0DIMENTS FIRST EMBODIMENT Referring first to FIG. 1B, there is shown a safety device for a hydraulic closed circuit according to a first preferred embodiment of the present invention. In FIG. 1B, like parts or elements are denoted by like reference symbols to those of FIG. 8. (I) Construction of the First Embodiment A variable displacement hydraulic pump 11 and a hydraulic motor 18 are connected to each other by a pair of main pipe lines 17A and 17B. The main pipe lines 17A and 17B are connected to each other by a crossover load relief valve 19 and also to a tank 90 by way of a flashing valve 20. The main pipe lines 17A and 17B are further connected via a pair of check valves 21A and 21B, respectively, to a pipe line 22a connected to a delivery port of a charging gear pump (hereinafter referred to as charge pump) 12. The amount of tilting motion of the variable displacement hydraulic pump 11 is controlled by a tilting cylinder 16. The tilting cylinder 16 has a pair of left and right cylinder chambers 16a and 16b in which a pair of springs 16d and 16e are disposed, respectively, so that a piston 16c of the tilting cylinder 16 may be normally held at a neutral position by the spring forces of the springs 16d and 16e. The cylinder chambers 16a and 16b are connected to an A port and a B port of a control valve 14 by way of a pair of pipe lines 15A and 15B, respectively. Meanwhile, the cylinder chambers 16a and 16b are connected by way of a pair of bypass pipe lines 31A and 31B, respectively, to an opening and closing valve 32 of the pilot hydraulic change-over type having two positions. The opening and closing valve 32 thus has a pilot port 32A connected to the delivery port of the charge pump 12. The control valve 14 is a manually operable three position directional control valve having a P1 port connected to the pipe line 22b on the upstream side of a restrictor 13 and a P2 port connected to the pipe line 22a on the downstream side of the restrictor 13. A switch 7 is operatively associated with an operating lever 1 of the control valve 14 and detects a neutral position of the operating lever 1. In particular, when the operating lever 1 assumes the neutral position, the switch 7 assumes its on position. The switch 7 is interposed between a battery 4 and a coil 3C of a relay 3. A switch 3S of the relay 3 is interposed between a starter switch 2 and a starter motor 5. Thus, when the switch 7 is turned on, a circuit of the battery 4, starter switch 2, relay switch 3S and starter motor 5 is completed so that the starter motor 5 is energized. It is to be noted that reference numeral 8 in FIG. 1B denotes an operating member for controlling a rotational speed of an engine 6. A pair of relief valves 19A and 19B and a pair of check valves 19C and 19D are also provided and generally form a crossover load relief valve 19. If, for example, the pressure in the main pipe line 17A rises to a relief pressure of the relief valve 19A, the relief valve 19A is opened so that pressure oil will flow through the check valve 19D into the main pipe line 17B. Further, a change-over valve 20A of the hydraulic pilot type and a relief valve 20B are also provided and generally constitute a flashing valve 20. If, for example, the pressure in the main pipe line 17A rises to a pressure higher than that in the main pipe line 17B, the change-over valve 20A is changed over to its position ℓ so that low pressure oil in the main pipe line 17B on the lower pressure side will flow through the change-over valve 20A and the relief valve 20B into the tank 90. A relief valve 23 for the charge system is also provided. (II) Operation of the First Embodiment Operation of the embodiment having such a construction as described above when the temperature is very low will be described. (1) When the operating lever 1 is positioned at its neutral position and the starter switch 2 is turned on, then the starter motor 5 is energized to start the engine 6 because the relay switch 3S remains at its closed position. As the engine 6 is started, the charge pump 12 delivers therefrom pressure oil, which is introduced by way of the pipe line 22b and pilot pipe line 33 into the pilot port 32A of the opening and closing valve 32. The opening and closing valve 32 is changed over to the position m in which the cylinder chambers 16a and 16b are disconnected from each other. Since the operating lever 1 remains at its neutral position, the control valve 14 assumes its neutral position n, so that the the pressure on the downstream side of the restrictor 13 acts upon both of the cylinders 16a and 16b of the tilting cylinder 16. Accordingly, the piston 16c assumes its neutral position. Consequently, the tilt angle of the variable displacement hydraulic pump 11 is set to zero and accordingly the amount of delivery from the variable displacement hydraulic pump 11 is zero. When the operating lever 1 is operated to change over the control valve 14 to the ℓ side, the pressure on the upstream side of the restrictor 13 is introduced into the cylinder chamber 16a of the tilting cylinder 16 while the pressure on the downstream side of the restrictor 13 is introduced into the other cylinder chamber 16b. Consequently, the piston 16c is displaced leftwardly in FIG. 1B by a distance corresponding to a difference between the pressures on the opposite sides of the restrictor 13 proportional to the rotational speed of the engine 6, so that the variable displacement hydraulic pump 11 delivers oil therefrom to rotate the hydraulic motor 18. (2) In this instance, if the engine 6 should stall, the amount of delivery from the charge pump 12 is reduced to zero. Consequently, the pressures in the pipe lines 22a and 22b are reduced by a leak of the charge pump 12, and the pressure at the pilot port 32A of the opening and closing valve 32 is decreased immediately by way of the pilot pipe line 33, so that the opening and closing valve 32 is changed over to the position ℓ by a return spring 32B. As a result, the cylinder chambers 16a and 16b are communicated with each other by way of the bypass pipe lines 31A and 31B and opening and closing valve 32. Meanwhile, since reduction in pressure in the pipe lines 22a and 22b acts also upon the cylinder chambers 16a and 16b by way of the pipe lines 15A and 15B, respectively, the piston 16c is displaced rightwardly by the spring force accumulated in the spring 16e. In this instance, since the cylinder chamber 16a remains in communication with the other cylinder chamber 16b by way of the bypass pipe line 31A, the opening and closing valve 32 and the other bypass pipe line 31B as described hereinabove, oil which is discharged from the cylinder 16 as the piston 16c is displaced rightwardly flows along a route including the bypass pipe line 31A, the opening and closing valve 32, the other bypass pipe line 31B and the cylinder chamber 16b. Since the route can be made very short and thick comparing with a route of the pipe lines 15A and 15B, the influence of a viscous resistance is so small that the piston 16c will be immediately returned to its neutral position. Accordingly, even if the operating lever 1 is returned to its neutral position and the starter switch 2 is turned on to re-start the engine 6 immediately after an engine stall, the amount of delivery from the variable displacement hydraulic pump 11 will remain zero and accordingly the hydraulic motor 18 will not be rotated. Thus, the safety in starting in a very low temperature condition is assured. (III) Modifications to the First Embodiment (1) A modification shown in FIG. 2 is different from the first embodiment shown in FIG. 1B in that the relief valve 23 and the pilot port 32A of the opening and closing valve 32 are connected to the pipe line 22a on the downstream side of the restrictor 13, that the manually operable control valve 14 for controlling the direction of rotation of the hydraulic motor 18 is replaced by an electromagnetic control valve 140, and that the switch 7 is omitted and instead a switch 70 for changing over the electromagnetic control valve 140 is provided. Where the hydraulic motor 18 is utilized as a motor for running a vehicle, the switch 70 is provided with three terminals of F (forward), R (rearward) and N (neutral), and the terminals F and R are connected to a pair of solenoids 140S provided at the opposite ends of the control valve 140 while the remaining terminal N is grounded by way of the relay coil 3C. When the engine 6 is started with the switch 70 positioned at the N position, the charge pump 12 is rotated. When the switch 70 is shifted to the F position, then the control valve 140 is changed over to the position ℓ in which the pressure on the upstream side of the restrictor 13 is introduced into the cylinder chamber 16a of the tilting cylinder 16 and the pressure on the downstream side of the restrictor 13 is introduced into the other cylinder chamber 16b. The piston 16c is displaced in the leftward direction in FIG. 2 to a position corresponding to a difference of the pressures on the opposite sides of the restrictor 13. The tilt angle of the variable displacement hydraulic pump 11 is controlled by the piston 16c, and the hydraulic pump 11 delivers pressure oil by an amount corresponding to the thus controlled tilt angle of the variable displacement hydraulic pump 11. By the pressure oil, the hydraulic motor 18 is rotated to advance the vehicle. If an engine stall should take place during running of the vehicle which has started its advancing movement in this manner, an operator will change over the switch 70 once to the N position, and then the engine 6 will be re-started. As a result of the engine stall, delivery of pressure oil from the charge pump 12 is also stopped. Consequently, the pressure in the pilot pipe line 33 drops immediately due to a leak of the charge pump 12, so that the opening and closing valve 32 is changed over to the position ℓ by the spring 32B. Accordingly, the leftwardly shifted piston 16c is returned to its neutral position immediately after the engine stall as described hereinabove. As a result, the vehicle is prevented from being advanced inadvertently upon re-starting of the engine. (2) An alternative arrangement may be employed wherein the opening and closing valve 32 is in the form of an electromagnetic opening and closing valve and a sensor for detecting rotation of the engine is provided so that the opening and closing valve 32 may be changed over to the position m by rotation of the engine but to the positions ℓ by stopping of the engine. (3) While in the foregoing description the tilting cylinder 16 is of the type wherein the cylinder chambers 16a and 16b in pair are disposed in an opposing relationship on the left and right sides of the piston 16c and, for example, an end of a cam plate of the variable displacement hydraulic pump 11 and the piston 16c are connected to each other in order that the cam plate is tilted by a movement of the piston 16c, the present invention can be applied to such a modification that a pair of tilting cylinders are employed and piston rods of the tilting cylinders are connected to the opposite ends of the cam plate on the opposite sides of a fulcrum for rocking motion of the cam plate. (4) Further, while in the foregoing description the two cylinders 16a and 16b are connected to or disconnected from each other by way of the opening and closing valve 32, they may otherwise be connected to or disconnected from the lower pressure side of a tank each by way of an opening and closing valve. According to this modification, when the engine is stopped, the two opening and closing valves may be opened to relieve the pressures of the cylinder chambers 16a and 16b. In this instance, the cylinder chambers 16a and 16b are connected to or disconnected from each other by way of the pair of opening and closing valves and the tank. (IV) Construction of the Second Embodiment A second embodiment of the present invention will be described with reference to FIG. 3. In FIG. 3, like parts or elements are denoted by like reference symbols to those of FIG. 1B. A pair of main pipe lines 17A and 17B which interconnect a variable displacement hydraulic pump 11 and a pair of input/output ports of a hydraulic motor 18 are connected to an opening and closing valve 32 of the hydraulic pilot type by way of a pair of bypass pipe lines 31A and 31B, respectively. A pilot port 32A of the opening and closing valve 32 is connected by way of a slow return valve 33 to a pipe line 22a connected to a delivery port of a charging gear pump (hereinafter referred to as charge pump) 12. It is to be noted the pressure for changing over the opening and closing valve 32 from a position ℓ to another position m is set lower than a preset pressure of a relief valve 23 of the charge hydraulic circuit. A tilting cylinder 16 for controlling the amount of tilting motion of the variable displacement hydraulic pump 11 has similar construction to that shown in FIG. 1B, and a piston 16c of the tilting cylinder 16 is normally held at its neutral position by the spring forces of a pair of springs 16d and 16e. The tilting cylinder 16 has a pair of cylinder chambers 16a and 16b which are connected to an A port and a B port of a control valve 14 by way of a pair of pipe lines 15A and 15B, respectively. (V) Operation of the Second Embodiment Operation of the second embodiment having such a construction as described above when the temperature is very low will be described. (1) When a starter switch 2 is turned on with an operating lever 1 positioned at its neutral position, a starter motor 5 is energized because a switch 3S of a relay 3 is in a closed position, and consequently, an engine 6 is started. As the engine 6 is started, the charge pump 12 delivers therefrom pressure oil, which is introduced through the pipe lines 22a and 22b and a restrictor 33A of the slow return valve 33 into the pilot port 32A of the opening and closing valve 32, so that the opening and closing valve 32 is changed over to the position m. As a result, the bypass pipe lines 31A and 31B connected to the main pipe lines 17A and 17B, respectively, are disconnected from each other. When the viscosity of oil is high as in a very low temperature condition, it will take a predetermined delay time from starting of the engine 6 to closing of the opening and closing valve 32 by an action of the restrictor 33A. Since the operating lever 1 is positioned now at its neutral position as described above, the control valve 14 assumes its neutral position in which the pressure on the downstream side of the restrictor 13 acts upon both of the cylinder chambers 16a and 16b so that the piston 16c is positioned at its neutral position. Accordingly, the tilt angle of the variable displacement hydraulic pump 11 is set to zero and the amount of delivery from the variable displacement hydraulic pump 11 is zero. When the operating lever 1 is operated to shift the control valve 14 to the ℓ side, the pressure on the upstream side of the restrictor 13 is introduced into the cylinder chamber 16a while the pressure on the downstream side of the restrictor 13 is introduced into the other cylinder chamber 16b. Consequently, the piston 16c is displaced leftwardly in FIG. 3 by a distance corresponding to a difference between the pressures on the opposite sides of the restrictor 13 proportional to the rotational speed of the engine 6, so that the variable displacement hydraulic pump 11 delivers oil therefrom to rotate the hydraulic motor 18. (2) In this instance, if the engine 6 should stall, the amount of delivery from the charge pump 12 is reduced to zero, and since the charge pump 12 is a gear pump, the pressures in the pipe lines 22a and 22b are decreased by a leak of the charge pump 12. Consequently, the pressure at the pilot port 32A is immediately decreased by way of the slow return valve 33, so that the opening and closing valve 32 is changed over to the position ℓ by the spring force of the return spring 32B. As a result, the main pipe lines 17A and 17B are communicated with each other immediately after stopping of the engine 6. It is to be noted that where the leak of the pump 12 is too small, the pipe line 22a should be connected to a tank 90 by way of a restrictor 96 as indicated by a two-dot chain line block denoted by reference numeral 95. Meanwhile, since reduction in pressure in the pipe lines 22a and 22b acts also upon the cylinder chambers 16a and 16b by way of the pipe lines 15A and 15B, respectively, the piston 16 begins to be moved rightwardly in FIG. 3 by the spring force accumulated in the spring 16e. As a result, oil discharged from the cylinder 16 as the piston 16c is displaced rightwardly flows along a route including the pipe line 15A, the control valve 14, the other pipe line 15b and the cylinder chamber 16b. In this instance, the resistance in the pipe lines is so high due to a high viscous resistance of the oil because of the very low temperature that the piston 16c will be returned to its neutral position not directly after stopping of the engine but after lapse of a predetermined interval of time. (3) If the operating lever 1 is returned to its neutral position and the starter switch 2 is turned on to re-start the engine 6 directly after the engine stall (i.e., within a predetermined interval of time until the piston 16c is returned to its neutral position), the charge pump 12 and the variable displacement hydraulic pump 11 are rotated. The delivery pressure of the charge pump 12 acts upon the pilot port 32A of the opening and closing valve 32 after a predetermined time of delay by the restrictor 33A of the slow return valve 33 as described hereinabove, so that the opening and closing valve 32 is changed over to the position m. Consequently, the main pipe lines 17A and 17B are disconnected from each other after the predetermined delay time after starting of the engine 6. Meanwhile, if the operating lever 1 is not operated and remains at its neutral position, the variable displacement hydraulic pump 11 which is rotated upon re-starting of the engine 6 delivers pressure oil therefrom only for an interval of time until the tilting cylinder 16 is returned to its neutral position after starting of the engine 6. However, the main pipe lines 17A and 17B remain in a mutually communicating condition by way of the opening and closing valve 32 for an interval of time until after lapse of the delay time described above after re-starting of the engine 6 being in stall condition. Accordingly, oil delivered from the variable displacement hydraulic pump 11 flows along a loop formed by the main pipe lines 17A and 17B, bypass pipe lines 31A and 31B and opening and closing valve 32, so that the hydraulic motor 18 will not be rotated. In short, if a delay time, which is longer than the interval of time until the tilting cylinder 16 is returned to its neutral position after the engine 6 has been stopped in a very low temperature condition, is set to the restrictor 33, then even if the pressure oil is delivered from the variable displacement hydraulic pump 11 upon re-starting of the engine in a very low temperature condition, pressure coil will not be supplied to the hydraulic motor 18 within the delay time. Consequently, the safety upon starting is assured. It is to be noted that since the viscous resistance of oil is low at the normal temperature, the delay time by the restrictor 33A is reduced to a level which can be ignored in an actual operation, and accordingly there is no trouble. (VI) Modifications to the Second Embodiment (1) A modification shown in FIG. 4 is different from the second embodiment shown in FIG. 3 in that the relief valve 23 is connected to the pipe line 22a on the downstream side of the restrictor 13, that the manually operable control valve 14 is replaced by an electromagnetic control valve 140, and that a switch 70 for changing over the electromagnetic control valve 140 is provided in place of the switch 7. Operation of the modification originating in the different structure is similar to corresponding operation of the modification to the first embodiment shown in FIG. 2, and operation originating in the other structure is similar to that of the second embodiment shown in FIG. 3. Accordingly, description of operation is omitted herein to avoid redundancy. (2) Another modification to the second embodiment is shown in FIGS. 5 and 6. The present modification is constituted such that the opening and closing valve 32 is replaced by an electromagnetic opening and closing valve 320 and the slow return valve 33 is omitted. In the modification, the opening and closing valve 320 is changed over to the position m under the condition where the tilting cylinder 16 is positioned at its neutral position and the engine 6 is rotating, and the opening and closing valve 320 will thereafter be changed over to the position ℓ when rotation of the engine 6 is not detected. To this end, according to the present modification, the safety device for the hydraulic closed circuit includes a pump neutral detecting sensor 51 for detecting a neutral position of the tilting cylinder 16, a rotation detecting sensor 52 for detecting that the engine 6 is rotating, and a controller 53 for changing over the opening and closing valve 320 from the position ℓ to the position m or vice versa in response to detection outputs of the sensors 51 and 52. FIG. 6 illustrates a process of operations of the controller 53 shown in FIG. 5. Referring to FIG. 6, the controller 53 determines, at step S1, in accordance with a detection output from the rotation detecting sensor 52 whether or not the engine 6 is rotating. If it is determined that the engine 6 is rotating, then the controller 53 determines, at step S2, in accordance with a detection output from the pump neutral sensor 51 whether or not the tilting cylinder 16 is at its neutral position. In case the determination is in the affirmative, the controller 53 delivers, at step S3, a change-over signal to the opening and closing valve 320 so that the opening and closing valve 320 is energized and thus changed over to the position m. On the contrary, if it is determined at step S1 that the engine 6 is not rotating, the controller 53 stops, at step S4, delivery of the change-over signal so that the opening and closing valve 320 is deenergized and consequently changed over to the position ℓ. According to the procedure, if the two requirements are met that the engine 6 is rotating and that the tilting cylinder 16 remains at its neutral position, the opening and closing valve 320 is changed over to the position m to disconnect the main pipe lines 17A and 17B from each other. Accordingly, the hydraulic motor 18 is rotated by oil delivered from the hydraulic pump 11. Then, if the engine 6 is stopped by an engine stall, the opening and closing valve 320 is changed over to the position ℓ so that the main pipe lines 17A and 17B are communicated with each other. In case an operator shifts the control valve 14 to its neutral position immediately after the engine stall and restarts the engine 6, if the tilting cylinder 16 is not yet returned to its neutral position under the circumstances of a very low temperature, pressure oil is delivered from the hydraulic pump 11. In this case, however, the step S2 is repeated until the tilting cylinder 16 is returned to its neutral position and the opening and closing valve 320 remains at the position ℓ so that the main pipe lines 17A and 17B remain in a mutually communicating condition. Accordingly, there is no possibility that the hydraulic motor 18 may be rotated. It is to be noted that the pump neutral position sensor 51 may be omitted while the construction is modified such that if stopping of rotation of the engine 6 is detected by the sensor 52, the controller 53 controls the opening and closing valve 320 to be immediately changed over to the position ℓ, and after lapse of a predetermined time of delay after such changing over of the opening and closing valve 320, the controller 53 controls the opening and closing valve 320 to be changed over to the position m. In this instance, the delay time may be increased as a temperature of the atmosphere or oil, which is detected by a suitable detector, lowers. The first and second embodiments described above can be further modified in such a manner as shown in FIG. 7. The modification will be described with reference to FIG. 7. (VII) Modification Common to the First and Second Embodiments (1) While in the first and second embodiments the piston 16c of the tilting cylinder 16 is displaced in response to a difference between the pressures on the opposite sides of the restrictor 13 proportional to the number of rotation of the engine in order to control the amount of delivery from the variable displacement hydraulic pump 11, the present invention can be applied to such an arrangement as shown in FIG. 7. In the arrangement shown in FIG. 7, a pressure proportional to an amount of operation of an operating member 8 for controlling the rotational speed of the engine is produced by means of a pressure reducing valve 41. The pressure thus produced is introduced into the cylinder chamber 16a or 16b so as to control the amount of displacement of the piston 16c in proportion to the rotational speed or number of rotation of the engine. (2) Further, while in the embodiments and modifications described above starting of the engine 6 is permitted only when the control valve 14 remains at its neutral position, it may be permitted otherwise when the control valve 14 is at the position ℓ or m. Further, while the variable displacement hydraulic pump 11 and the charge pump 12 are driven by the engine 6, the present invention can be applied to an alternative apparatus wherein they are driven by an electric motor. In addition, the present invention can be applied a different apparatus wherein the hydraulic motor 18 is used for an object other than for running of a vehicle.

Claims: A hydraulic circuit, comprising a variable displacement hydraulic pump (11) driven by a prime mover (6) and capable of supplying pressure oil to a hydraulic motor (18) having an inlet and an outlet port connected in a closed circuit to corresponding inlet/outlet ports of said variable displacement hydraulic pump (11) by means of main pipe lines (17A, 17B), a tilt control means (16) including first and second chambers (16a, 16b) to control a tilt angle of said variable displacement hydraulic pump (11) in response to pressure oil supplied to said first or second chamber (16a, 16b), a three position control valve (14) provided between an oil supplying hydraulic pump (12) driven by said prime mover (6) and said first and second chambers (16a, 16b) of said tilt control means (16), said control valve (14) being capable of supplying pressure oil to one or the other of said first and second chambers (16a, 16b) or, in the neutral position of said control valve (14), being capable of at least communicating both chambers (16a, 16b) with each other, a safety device (3, 7) being provided, characterized in that said safety device further comprises a rotation detecting means to detect a rotational condition of said prime mover (6); an opening and closing valve means (32) to control the supply of pressure oil to said hydraulic motor (18), said opening and closing valve means (32) having a first position (m) in which said valve means (32) enables the supply of pressure oil to said hydraulic motor (18) and a second position (ℓ) in which the supply of pressure oil is inhibited; change-over controlling means (32B, 33) to change over said valve means (32) to the second position (ℓ) in response to the stopping of said prime mover (6) being detected by said rotation detecting means (33) and to change over said valve means (32) to the first position (m) in response to the rotation of said prime mover (6) being detected. A hydraulic circuit according to claim 1, characterized in that said opening and closing valve means (32) is a valve of the hydraulic pilot type, arranged in a bypass pipe line (31A, 31B) connected to said first and second chambers (16a, 16b) of said tilt control means (16), and said change-over controlling means (32B, 33) comprising a hydraulic pilot pressure line (33), connecting said oil supplying hydraulic pump (12) to the pilot port (32A) of said hydraulic pilot valve (32). A hydraulic circuit according to claim 1, characterized in that said opening and closing valve means (32) is an electro magnetically operated valve, arranged in a bypass pipe line (31A, 31B) connected to said first and second chambers (16a, 16b) of said tilt control means (16), said rotation detecting means comprising a rotation detecting sensor (52) capable of placing said electro magnetically operated valve (32) in the first position (m). A hydraulic circuit according to claim 1, characterized in that said opening and closing valve means (32) is a valve of the hydraulic pilot type arranged in a bypass pipe line (31A, 31B) interconnecting said main pipe lines (17A, 17B), said change-over controlling means comprising a hydraulic pressure line (22a) connecting said oil supplying hydraulic pump (12) to the pilot port (32A) of said hydraulic pilot valve (32), a restriction (33A) being provided in said hydraulic pressure line (22a) in order to delay the time of arrival at said pilot port (32A) of the pressure oil supplied by said oil supplying hydraulic pump (12), said hydraulic pilot valve (32) being placed in the second position (ℓ) when the hydraulic pressure in the hydraulic pressure line (22a) is reduced to a tank pressure and being placed in the first position (m) after a predetermined delay time has lapsed since the starting of said prime mover. A hydraulic circuit according to claim 1, characterized in that said opening and closing valve means (32) is an electro mechanically operated valve (320), arranged in a bypass line (31A, 31B) interconnecting said main lines (17A, 17B), said rotation detecting means comprising a rotation detector sensor (52) and said change-over controlling means (51, 53) including a neutral position detecting means (51) for detecting the neutral position of said tilt control means (16), the electro magnetically operated valve (320) being placed in the second position (ℓ) immediately after said prime mover (6) is stopped and being changed over to the first position (m) when the rotation of said prime mover (6) as well as the neutral position of said tilt control means (16) are both detected.

Inventors: KANAI TAKASHI, NOZAKI KOJI, OCHIAI MASAMI, OSHINA MORIO, KANAI, TAKASHI, NOZAKI, KOJI, OCHIAI, MASAMI, OSHINA, MORIO
Applicants: HITACHI CONSTRUCTION MACHINERY, HITACHI CONSTRUCTION MACHINERY CO., LTD.
Application year: 1988
Main classification: F16H61
IPC codes: F16H61, F15B11