JP3839434B2 - Lock device in torque actuator mechanism - Google Patents

Description

  The present invention relates to, for example, a torque actuator mechanism using a hydraulic torque generator used for opening and closing a hatch cover of a ship, for opening and closing a ship valve, for turning a boom of a construction machine, and the like. The present invention relates to a device for suitably locking a hydraulic torque generator inside.

  A torque actuator mechanism using a hydraulic torque generator has been proposed in the past by the present applicant. The configuration of the hydraulic torque generator 1 will be described with reference to FIG. is there.

  A piston 3 and a shaft 4 are housed inside the casing 2. The shaft 4 is disposed concentrically with the casing 2 and is pivoted via a bearing by a first cover member 5 and a second cover member 6 that close both ends of the casing 2.

  The piston 3 includes a flange portion 3 a that is inserted into the cylinder 7 of the casing 2, and a cylindrical portion 3 b that is concentrically inserted around the shaft 4.

  The cylindrical portion 3b of the piston 3 is extrapolated with respect to the shaft 4 via a spline 8 so as to be rotatable along with the shaft 4 and to be movable back and forth in the axial direction, and screwed to the casing 2 via screw means 9. Has been. That is, a male screw is formed on the outer periphery of the cylindrical portion 3 b and the male screw is screwed into a female screw formed on the inner periphery of the casing 2.

  A seal ring 10 that is liquid-tightly attached to the inner periphery of the cylinder 7 and a seal ring 11 that is liquid-tightly attached to the outer periphery of the shaft 4 are mounted on the inner and outer peripheral portions of the flange portion 3 a of the piston 3. Yes. The first cover member 5 and the second cover member 6 are mounted in a liquid-tight manner on the casing 2 via sealing materials 12 and 13, respectively, and the hydraulic oil sealed inside the cylinder 7 is externally attached. It is completely sealed to prevent leakage.

  The cylinder 7 forms a first chamber 7a and a second chamber 7b located before and after the flange portion 3a of the piston 3, and each receives a pressure from a hydraulic power source via the first inlet / outlet port 14a and the second inlet / outlet port 14b. Supply hydraulic oil.

  When hydraulic oil is supplied to the cylinder 7 from one of the first inlet / outlet port 14a or the second inlet / outlet port 14b and the hydraulic pressure is applied, the piston 3 receives the thrust force at the flange portion 3a, while the screw portion 9 is screwed at the cylinder portion 3b. Thus, the torque is converted into a rotational force, whereby the piston 3 rotates while screwing along the screw means 8.

  The rotational driving force of the piston 3 is transmitted to the shaft 4 splined to the cylindrical portion 3b of the piston, and the end portion of the shaft 4 is used as the output shaft.

  Such a conventional hydraulic torque generator 1 constitutes an actuator mechanism as a whole by providing hydraulic circuit means with a hydraulic power source.

  The hydraulic torque generator 1 has a manifold block 15, a pilot check valve device 16, and a bypass valve device 17 that are sequentially connected to each other, and includes a first oil passage 18a and a second oil passage 18b. It constitutes hydraulic circuit means. That is, the first oil passage 18 a and the second oil passage 18 b are connected to the pilot check valves 16 a and 16 b of the pilot check valve device 16 from the first inlet 14 a and the second inlet 14 b of the hydraulic torque generator 1 through the manifold block 15. Then, the bypass valve device 17 is reached. Then, it turns back inside the bypass valve device 17 and returns to the manifold block 15 through the pilot check valve device 16.

Further, the first oil passage 18 a and the second oil passage 18 b are connected from the manifold block 15 to extension lines 19 a and 19 b such as pipelines, and communicated with the hydraulic source 21 and the tank 22 through the electromagnetic valve 20.
Japanese Patent No. 2860329

  The hydraulic torque generator 1 rotates the output shaft within a certain range (for example, 90 degrees, 180 degrees, or 360 degrees). The output shaft is rotated at the beginning or end of the rotation angle. Needs to be fully locked. For example, when the marine hatch is opened and closed by the hydraulic torque generator 1, when the hatch open state is set at the end of the rotation angle, the hatch is opened by completely locking the output shaft at that position. Need to maintain.

  Therefore, as described above, the conventional actuator mechanism has a pilot check valve 16a for preventing the return of hydraulic oil from the hydraulic torque generator 1 to each of the first oil passage 18a and the second oil passage 18b. 16b. Accordingly, when the hydraulic torque generator 1 is stopped by blocking the hydraulic pressure from the hydraulic source 21 with the solenoid valve 21, the hydraulic oil in the first chamber 7a and the second chamber 7b of the cylinder 7 is pilot-check valve. Since it is blocked by 16a and 16b, the movement of the piston 3 can be fixed by this, and the movement of the shaft 4 can be locked.

  However, the poppet type metal touch is generally used for the pilot check valve, and is configured to prevent the return of the hydraulic oil by mutual contact between the metal surfaces. Therefore, a load is applied to the shaft 4 of the hydraulic torque generator 1. In the acted state, a very small amount of hydraulic oil oozes out through the metal contact surface, so that a complete locked state cannot be obtained, and there is a problem that the holding position shifts with time. That is, for example, in the case of a marine hatch, there is a problem that the hatch that should have been held open by locking the hydraulic torque generator 1 gradually moves in the closing direction due to its weight or the like.

  In this regard, the present applicant has proposed in Japanese Patent Application No. Hei 4-221996 a lock device configured to lock the piston with a lock pin when the hydraulic torque generator is stopped, and is patented as Japanese Patent No. 2860329. It was done. However, in this case, since a locking device is provided inside the hydraulic torque generator, it is necessary to newly design the hydraulic torque generator itself, and there is a problem that the cost is increased. There is a problem that the rotational force generator becomes larger.

  In view of the above, the present inventor solves the above problem by providing a lock device in a hydraulic circuit means as a torque actuator mechanism, while allowing an existing general-purpose product to be used as the hydraulic torque generator itself. Has been found to be advantageous.

  As pointed out with respect to the prior art, the problem with the locking device is caused by the pilot check valve of the poppet type metal touch structure, and if this is solved, it becomes possible to realize a completely locked state.

  Recently, there has been provided a non-leak type pilot check valve that completely prevents the above-described hydraulic oil from seeping out. This new non-leak type pilot check valve is a soft seal type using a resin or rubber on the contact surface for preventing the return of hydraulic oil, and is provided by, for example, Hirose Valve Industrial Co., Ltd. Therefore, in the prior art shown in FIG. 6, if the pilot check valves 16a and 16b are replaced with such a new type of non-leak type, a completely locked state can be achieved when the hydraulic torque generator is stopped. Can solve the problem.

  However, as a result of intensive studies by the inventor, when a new non-leak type pilot check valve is provided as the pilot check valves 16a and 16b in the configuration shown in FIG. 6, the valves 16a and 16b and the hydraulic torque It has been found that the closed circuits 23a and 23b of the first oil passage 18a and the second oil passage 18b located between the generators 1 are completely sealed, which causes a new problem.

In other words, the completely sealed space in which the hydraulic oil is sealed increases the internal pressure as the temperature rises. In the case of a general hydraulic fluid, when the temperature rises once (C), the pressure rises by about 10 kg / cm ² . Therefore, when the temperature increases by 30 degrees (C), the pressure increases by about 300 kg / cm ² .

  For this reason, when the closed circuits 23a and 23b are completely sealed as described above, an increase in internal pressure due to a temperature change causes damage to hydraulic equipment, damage to driving equipment, and other problems. Arise.

  Thus, it has been found that if the closed circuits 23a and 23b are provided with relief valves, the above-mentioned problems such as breakage can be solved by reducing the increased pressure. Since it has a structure and allows hydraulic oil to pass through easily, the original problem of enabling a completely locked state of the hydraulic torque generator cannot be solved.

  In order to solve the above-mentioned problem of the completely locked state, the present invention provides a new non-leak type pilot check valve as described above in the hydraulic circuit means, and is located between the valve and the hydraulic torque generator. By completely closing the closed circuit of the first oil passage and the second oil passage, the hydraulic torque generator can be completely locked. And in order to solve the problem caused by the pressure increase due to the temperature rise of the closed circuit that is in a completely sealed state, a special safety valve is provided in the closed circuit, thereby preventing breakage and damage of equipment etc. and complete locking state This is a trade-off function of achievement.

Therefore, the present invention is configured as means for solving the above-mentioned problems. A piston that moves forward and backward in the axial direction while rotating via screw means inside the cylinder, and a shaft that extracts the rotational driving force of the piston are provided. A hydraulic torque generator including a first inlet and a second inlet and outlet for supplying hydraulic oil to a first chamber and a second chamber of a cylinder located before and after the piston, and the first inlet and the second inlet In a torque actuator mechanism comprising a first oil passage and a hydraulic circuit means having a second oil passage respectively communicating with the hydraulic power source, the hydraulic circuit means comprising a first oil passage (28a) and a second oil passage. Each of (28b) is provided with a non-leak pilot check valve (33a) (33b) that prevents the return of hydraulic oil from the hydraulic torque generator to block the hydraulic pressure from the hydraulic source (31). Yo When the hydraulic torque generator (1) is stopped, the non-leak pilot check valve (33a) is supplied to the hydraulic oil in the first chamber and the second chamber of the cylinder in the hydraulic torque generator (1). 33b) is configured to lock the movement of the piston (3) and lock the movement of the shaft (4) by blocking the first oil path (28a) and the second oil path (28b). A closed circuit (34a) (34b) is constituted by a circuit portion located between the non- leak type pilot check valve (33a) (33b) and the hydraulic torque generator , and the closed circuit (34a) (34b) ) Are provided with safety valves (35a) and (35b), and the safety valves (35a) and (35b) have the rated pressure of the closed circuits (34a) and (34b) during the rotational driving of the hydraulic torque generator. When p1 is set, it is configured to operate when the internal pressure of the closed circuit (34a) (34b) exceeds p1 × 1.5 with temperature rise to prevent equipment damage. The point is that

  In a preferred embodiment of the present invention, a drain passage for guiding hydraulic oil leaked from the safety valve is provided, and the drain passage is provided in each of the first oil passage and the second oil passage located between the pilot check valve and the hydraulic pressure source. An extension passage that allows communication is formed, and a check valve that prevents the hydraulic oil from flowing from the first oil passage and the second oil passage toward the drain passage is provided in each of the extension passages.

  The safety valve includes a cylinder means that constitutes a leakage path that leaks hydraulic oil from the closed circuit toward the drain path, a spool that is slidably inserted into the cylinder means, and the spool is opposed to the leakage direction of the hydraulic oil. And a spring that is biased in the direction of movement. The spool is integrally provided with an operating part located on the closed circuit side and an extension part located on the leakage path side, and allows one end of the communication path formed inside the extension part to communicate with the leakage path and the other end of the spool. Opened on the outer peripheral surface of the extension. The cylindrical means is provided with a sealing material on the inner peripheral surface thereof that is in close contact with the outer peripheral surface of the operating portion of the spool in a state where the spool is biased by the spring. Then, when the outer peripheral surface of the operating part moves away from the sealing material due to the movement of the spool against the spring due to the increase in the internal pressure of the closed circuit, the outer peripheral surface of the operating part and the inner peripheral surface of the cylinder means slide against each other. The hydraulic fluid oozes out from the closed circuit toward the communication path via the clearance of the moving surface.

  It is preferable that the clearance of the mutual sliding surface of the outer peripheral surface of an action | operation part and the internal peripheral surface of a cylinder means is formed in the range of 10micro to 40micro.

  According to the present invention, the first oil passage and the second oil passage constituting the hydraulic circuit means are provided with the non-leak type pilot check valve for preventing the return of the hydraulic oil from the hydraulic torque generator. Since the closed circuit of the first oil passage and the second oil passage located between the valve and the hydraulic torque generator is completely sealed, the hydraulic torque generator can be completely locked. become. Therefore, even when a load is applied to the shaft of the hydraulic torque generator in a stopped state, there is no problem that the operated device such as a marine hatch will move the holding position with the passage of time as in the prior art. Since the existing hydraulic product can be used for the hydraulic torque generator itself, it is advantageous in terms of cost and does not cause an increase in size of the hydraulic torque generator.

  By the way, as a result of using the non-leak type pilot check valve, the closed circuit of the first oil passage and the second oil passage located between the valve and the hydraulic torque generator is completely sealed space. According to the present invention, since a special safety valve is provided in each closed circuit, it is preferable to cause damage to hydraulic equipment, drive equipment, and other troubles due to pressure increase due to temperature rise of the closed circuit. Can be prevented. That is, the safety valve is configured to operate when the internal pressure of the closed circuit exceeds p1 × 1.5 when the rated pressure of the closed circuit during rotation of the hydraulic torque generator is p1. Therefore, during operation to operate the hydraulic torque generator with the hydraulic pressure from the hydraulic power source, there is no fear that the hydraulic oil will decrease due to leakage of hydraulic oil from the safety valve, and the hydraulic torque generator is suitable Can be activated. Further, even when a load is applied to the shaft of the hydraulic torque generator at the time of stop, the load applied to the shaft from an actuated device such as a marine hatch is empirically more than 1.5 times the rated pressure p1. Therefore, the safety valve does not allow the hydraulic oil to leak, and the holding position of the operated device is not shifted by loosening the lock state of the hydraulic torque generator. On the other hand, the internal pressure of the closed circuit increases as the temperature rises, and only when the rated pressure p1 exceeds 1.5 times the rated pressure p1 is the safety valve leaking hydraulic oil and reducing the pressure. Can be prevented.

  According to the embodiment of the present invention, the drain passage for guiding the hydraulic oil leaked from the safety valve is provided, and the drain passage is disposed between the pilot check valve and the hydraulic pressure source, and the second oil passage and the second oil passage. An extension passage that communicates with each of the oil passages is formed, and a check valve that prevents the hydraulic oil from flowing from the first oil passage and the second oil passage toward the drain passage is provided in each of the extension passages. Since it is a structure, the hydraulic fluid which leaked from the safety valve at the time of the internal pressure increase by a temperature rise can be suitably recirculated to the 1st oil path and the 2nd oil path via the extension path. At this time, since the extension path is connected to each of the first oil path and the second oil path via the check valve, the hydraulic oil leaked from the safety valve is removed from the first oil path and the second oil path. Of these, the internal pressure can be returned to the lower oil passage, and the balance of the internal pressures of the first oil passage and the second oil passage is maintained.

  In the present invention, the safety valve having a special function that operates when the internal pressure of the closed circuit exceeds p1 × 1.5 is a cylinder means that constitutes a leakage path that leaks hydraulic oil from the closed circuit toward the drain path. And a spool that is slidably inserted into the cylinder means, and a spring that urges the spool in a direction opposite to the leakage direction of the hydraulic oil. The spool is integrally provided with an operating part located on the closed circuit side and an extension part located on the leakage path side, and allows one end of the communication path formed inside the extension part to communicate with the leakage path and the other end of the spool. The cylindrical means has an opening on the outer peripheral surface of the extension portion, and the cylindrical means is provided with a sealing material on the inner peripheral surface that is in close contact with the outer peripheral surface of the operating portion of the spool while being urged by the spring. Accordingly, when the outer peripheral surface of the operating part moves away from the sealing material due to the movement of the spool against the spring due to the increase in the internal pressure of the closed circuit, the outer peripheral surface of the operating part and the inner peripheral surface of the cylinder means slide against each other. The hydraulic oil is allowed to leak from the closed circuit toward the drain path through the clearance of the moving surface. The amount of hydraulic fluid that leaks is limited to that which can pass through the clearance between the sliding surfaces, and it is sufficient if it is of a level that “bleeds out”. Therefore, the safety valve is always “complete”. Although it is “non-leak”, it has a structure that should be called “incomplete non-leak type” that allows a very small amount of leak to a limit that prevents damage to the device for the first time due to an excessive increase in internal pressure due to temperature rise.

  Such a special “incomplete non-leak type” safety valve can be realized by forming the clearance between the outer peripheral surface of the operating portion and the inner peripheral surface of the cylinder means in the range of 10 μ to 40 μ.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings.

  In the embodiment shown in FIGS. 1 and 2, the hydraulic torque generator 1 has the same configuration as the conventional configuration described based on FIG. 6. Therefore, the above-described explanation is used by attaching the same reference numerals to common technical configurations, and duplicate explanation is omitted.

  The hydraulic torque generator 1 constitutes an actuator mechanism as a whole by providing hydraulic circuit means with a hydraulic power source. For this reason, a manifold block 24, a safety valve device 25, a pilot check valve device 26, and a bypass valve device 27 are sequentially connected to the hydraulic torque generator 1 in order to connect the first oil passage 28a. The hydraulic circuit means provided with the 2nd oil path 28b is comprised. That is, the first oil passage 28 a and the second oil passage 28 b are connected to the bypass valve device through the manifold block 24, the safety valve device 25, and the pilot check valve device 26 from the first inlet / outlet port 14 a and the second inlet / outlet port 14 b of the hydraulic torque generator 1. 27, is turned back inside the bypass valve device 27, and returns to the manifold block 24 through the pilot check valve device 26 and the safety valve device 25. Further, the first oil passage 28 a and the second oil passage 28 b are connected from the manifold block 24 to extension lines 29 a and 29 b such as pipelines, and communicated with the hydraulic source 31 and the tank 32 via the electromagnetic valve 30.

  The pilot check valve device 26 includes non-leak type pilot check valves 33 a and 33 b that prevent the return of hydraulic fluid from the hydraulic torque generator 1 toward the bypass device 27. Therefore, when the hydraulic torque generator 1 is stopped by blocking the hydraulic pressure from the hydraulic source 31 with the electromagnetic valve 30, the internal operation of the first chamber and the second chamber of the cylinder in the hydraulic torque generator 1 is stopped. The oil is blocked by the non-leak type pilot check valves 33a and 33b, thereby fixing the movement of the piston 3 and locking the movement of the shaft 4. The non-leak type pilot check valves 33a and 33b are not the poppet type metal touch structure pilot check valves described in relation to the prior art. For example, a soft seal made of resin or rubber as recently provided by Hirose Valve Industry Co., Ltd. A non-leak type pilot check valve that completely prevents bleeding of hydraulic oil due to its structure is used. Accordingly, even when a load is applied to the shaft of the hydraulic torque generator 1 at the time of stopping, the hydraulic oil is not allowed to ooze out, and a complete lock state is enabled, and the holding position of the operated device such as a marine hatch is held. Hold it fixed.

  As a result of the provision of the non-leak type pilot check valves 33a and 33b, the first and second oil passages 28a and 28b include the valves 33a and 33b, the first inlet / outlet port 14a of the hydraulic torque generator 1, and the first oil passage 28a. The closed circuits 34a and 34b positioned between the two inlets 14b are completely sealed spaces, but the safety valve device 25 is provided with special safety valves 35a and 35b in the closed circuits 34a and 34b, respectively.

  The safety valves 35a and 35b have an internal pressure of the closed circuit p1 when the rated pressure of each of the closed circuits 34a and 34b during driving for rotating the hydraulic torque generator 1 by the hydraulic pressure from the hydraulic source 31 is p1. It is configured to operate when x1.5 is exceeded. The rated pressure p1 refers to the maximum allowable value of normal operating pressure. Accordingly, there is no fear that the hydraulic pressure is reduced by operating the safety valves 35a and 35b during the operation of the hydraulic torque generator 1, and the hydraulic torque generator 1 is preferably operated with a predetermined hydraulic pressure. Even when a load acts on the shaft of the hydraulic torque generator 1 at the time of stopping, the safety valves 35a and 35b operate as long as the internal pressure of the closed circuits 34a and 34b does not exceed p1 × 1.5. There is nothing.

  The safety valves 35a and 35b, when the internal pressure of the closed circuits 34a and 34b enclosing the hydraulic oil increases with the temperature rise and exceeds 1.5 times the rated pressure p1, the hydraulic oil leaks for the first time. Preventing equipment damage by reducing

  Examples of the safety valves 35a and 35b having special functions that operate when the internal pressure of the closed circuits 34a and 34b exceeds p1 × 1.5 are shown in FIGS.

  As shown in FIG. 3, the pair of safety valves 35a and 35b are arranged so as to face each other across the drain path 36 and are symmetrical with each other, but the basic configuration of each is common. The structure of one safety valve 35a will be described, and the structure of the other safety valve 35b will be referred to by the same reference numeral, and the description of one safety valve 35a will be used.

  As shown in FIG. 4, the safety valve 35 a includes a cylinder means 38 that constitutes a leakage path 37 that leaks hydraulic oil from the closed circuit 34 a to the drain path 36 via the internal flow path 36 a, and slides on the cylinder means 38. The spool 39 is movably inserted, and a spring 40 that urges the spool 39 in a direction opposite to the hydraulic oil leakage direction.

  The cylinder means 38 is constituted by a cylinder body screwed into the apparatus main body 25a, and the plug 41 is screwed inwardly from the tail end of the cylinder means 38, and further from the tail end of the plug 41 to the inside. An advancing / retracting member 42 made of a bolt is inserted. Seal members 43 and 44 such as O-rings are inserted between the apparatus main body 25a and the cylinder means 38, and seal members 45 such as O-rings are inserted between the cylinder means 38 and the plug 41, A sealing member 46 such as an O-ring is inserted between the advancing and retracting members 42, thereby sealing the closed circuit 34a and the leakage path 37 in a liquid-tight manner.

  The spool 39 is slidably inserted into the mouth portion 38a of the cylinder means 38 facing the closed circuit 34a, and integrally includes an operating portion 39a positioned on the closed circuit side and an extension portion 39b positioned on the leakage path side. One end of the communication passage 47 formed inside the extension portion 39b is connected to the leakage path 37, and the other end is opened to the outer peripheral surface of the extension portion 39b. In the illustrated embodiment, the spool 39 is inserted into a seat member 49 disposed inside the cylindrical member 38 at the tip end of the extension 39b, and the seat member 49 connects the communication passage 47 to the leakage passage 37. A communication path 49 a that allows communication is formed, and a flange portion 49 b that constitutes a seat for the spring 40 is provided. In the case of the illustrated example, a compression coil spring is used as the spring 40. Therefore, the urging force of the spring 40 always acts on the seat member 49, and the seat member 49 is applied to the inside of the mouth portion 38a of the cylindrical means 38. The normal position of the spool 39 is determined in the contacted state. A nut 50 is screwed onto the tail end of the advance / retreat member 42 inserted from the plug 41. By rotating the nut 50 forward and backward, the advance / retreat member 42 is moved forward and backward in the axial direction, and the spring 40 is attached. The power can be adjusted.

  A sealing material 51 such as an O-ring is provided on the inner peripheral surface of the mouth portion 38a of the cylinder means 38 so as to be in close contact with the outer peripheral surface of the operating portion 39a of the spool 39 at the normal position of the spool 39 biased by the spring 40. It has been. In the case of the illustrated example, the seal member 51 is fixed in place by a sleeve 52 inserted from the opening of the mouth portion 38a.

  The operation of the safety valve 35a is shown in FIG. As shown in FIG. 5A, the seat member 49 is normally brought into contact with the inside of the mouth portion 38a of the cylindrical means 38 by receiving the urging force of the spring 40, and the spool 39 is fixed in the normal position. . In this state, the outer peripheral surface of the operating portion 39a of the spool 39 is in intimate contact with the sealing material 51, and the sliding surface between the outer peripheral surface of the operating portion 39a and the inner peripheral surface of the mouth portion 38a is liquid-tightly sealed. ing. Therefore, the hydraulic oil inside the closed circuit 34 a does not leak toward the leakage path 37. As described above, the biasing force of the spring 40 is determined by adjusting the movement of the advance / retreat member 42 by the nut 50. This urging force leaks the spool 39 as long as the internal pressure of the closed circuit 34a does not exceed p1 × 1.5 when the rated pressure of the closed circuit 34a during the rotational drive of the hydraulic torque generator 1 is p1. The strength is set so as not to move toward the road 37.

  Therefore, since the internal pressure of the closed circuit 34a increases as the temperature rises, the pressure exceeding the urging force of the spring 40 acts on the spool 39 when the above p1 × 1.5 is exceeded. As shown in FIG. 5B, the seat member 49 slides against the spring 40 against the spring 40 and moves until the outer peripheral surface of the operating portion 39 a is separated from the seal material 51. In the case of the illustrated example, the spool 39 is stopped by the flange portion 49b of the seat member 49 coming into contact with the tip of the plug 41. In this operating state, the outer peripheral surface of the operating portion 39a of the spool 39 is the opening of the cylinder means 38. They are in contact with each other via the sliding surface 53 between the inner peripheral surface of the portion 38a. Accordingly, the hydraulic oil inside the closed circuit 34a having increased internal pressure oozes out from the closed circuit 34a toward the clearance of the sliding surface 53, as shown by the arrows in the drawing, and the hydraulic fluid that has oozed out slides into the sliding surface 53. The clearance is allowed to enter the communication passage 47 through the opening 48 of the spool 39 and leak into the leakage passage 37. The leaked hydraulic oil enters the internal flow path 36 a from the leak path 37 through the plug 41 and the cylindrical member 38 through the plug 41 and the cylindrical member 38, and is guided to the drain path 36.

  The amount of hydraulic oil oozing out by the sliding surface 53 is preferably as small as possible. For this reason, in the illustrated embodiment, the clearance of the sliding surface 53 is formed in the range of 10 μ to 40 μ. Yes. The most preferred example of clearance dimension value is about 30μ.

  In the illustrated embodiment, the hydraulic oil sealed in the closed circuits 34a and 34b formed between the hydraulic torque generator 1 and the non-leak pilot check valves 33a and 33b has an internal pressure as described above. When the temperature is increased by 15 degrees (C) so as to exceed p1 × 1.5, which is the critical point of the rated pressure, the amount of oil (volume of hydraulic oil) is increased by about 1%. Therefore, the internal pressure of the closed circuits 34a and 34b, which has increased due to the temperature rise, can be sufficiently reduced only by leaking the hydraulic oil by the safety valves 35a and 35b by a limited amount of oozing due to the clearance of the sliding surface 53. Can do.

  Therefore, as soon as the internal pressure of the closed circuits 34a and 34b is reduced by the operation of the safety valves 35a and 35b, the spool 39 is returned to the normal position again by the spring 40 as shown in FIG. 5A, and the operating portion 39a is sealed. The material 51 is brought into close contact with each other to seal between the closed circuits 34 a and 34 b and the leakage path 37.

  As shown in FIG. 1, the drain path 36 of the safety valve device 25 is provided for each of the first oil path 28 a and the second oil path 28 b located between the non-leak type pilot check valves 33 a and 33 b and the hydraulic pressure source 31. Furthermore, it communicates via the extended drain path 54 and the extended paths 55a and 55b. In the case of the illustrated example, the extension drain path 54 and the extension paths 55 a and 55 b are formed through the manifold block 24. The extension passages 55a and 55b are provided with check valves 56a and 56b for preventing hydraulic oil from flowing from the first oil passage 28a and the second oil passage 28b toward the drain passage 36. Therefore, the hydraulic oil supplied from the hydraulic source 31 to the first oil passage 28a or the second oil passage 28b in order to operate the hydraulic torque generator 1 does not flow toward the safety valves 35a and 35b.

  As described above, the increase in the internal pressure of the closed circuits 34a and 34b due to the temperature rise is reduced by the hydraulic oil oozing out toward the drain path 36 by the safety valves 35a and 35b, and the leaked hydraulic oil is extended to the extended drain path. 54, the first oil passage 28a or the second oil passage 28b is returned to the first oil passage 28a or the second oil passage 28b via the extension passages 55a and 55b. Of the oil passage 28a and the second oil passage 28b, the oil is recirculated toward the extension passage 55a or 55b connected to the oil passage 28a or 28b having the lower internal pressure. Thereby, the balance of the internal pressure of the 1st oil path 28a and the 2nd oil path 28b which has a pressure difference is maintained.

  A torque actuator mechanism configured by assembling a safety valve device 25, a pilot check valve device 26, and a bypass valve device 27 to the hydraulic torque generator 1 as described in detail above is shown in FIG. As a result, the whole is extremely compact and can be provided at a relatively low cost.

1 is a hydraulic circuit diagram showing an embodiment of a torque actuator mechanism of the present invention based on a hydraulic torque generator and hydraulic circuit means. It is a front view which shows the external appearance of one Embodiment of this invention. It is sectional drawing which shows one Example of the safety valve in this invention. It is an expanded sectional view of a safety valve. The action of a safety valve is shown, (A) is a sectional view showing an action in a normal state, and (B) is a sectional view showing the action at the time of operation. It is explanatory drawing shown in the state which combined the cross-sectional view of the hydraulic-type rotational force generator based on a prior art, and the circuit diagram of the hydraulic circuit means based on a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Hydraulic type rotational force generator 14a 1st entrance / exit 14b 2nd entrance / exit 24 Manifold block 25 Safety valve apparatus 25a, 25b Safety valve 26 Pilot check valve apparatus 27 Bypass valve apparatus 28a 1st oil path 28b 2nd oil path 29a, 29b Extension line 30 Solenoid valve 31 Hydraulic source 32 Tank 33a, 33b Non-leak type pilot check valve 34a, 34b Closed circuit 35a, 35b Safety valve 36 Drain path 37 Leakage path 38 Cylindrical means 38a Mouth 39 Spool 39a Actuator 39b Extension 40 Spring 47 Communication path 48 Opening 49 Seat member 51 Sealing member 53 Sliding surface 55a, 55b Extension path 56a, 56b Check valve

Claims (4)

A piston that moves forward and backward in the axial direction while rotating via screw means inside the cylinder, a shaft that takes out the rotational driving force of the piston, and a first chamber and a second chamber of the cylinder that are located before and after the piston, respectively A hydraulic rotational force generator having a first inlet and a second inlet for supplying hydraulic oil, and a first oil passage and a second oil passage for connecting the first inlet and the second inlet to a hydraulic source, respectively. In the torque actuator mechanism composed of hydraulic circuit means,
The hydraulic circuit means includes a non-leak pilot check valve (33a) that prevents the return of hydraulic oil from the hydraulic torque generator in each of the first oil passage (28a) and the second oil passage (28b). 33b), and when the hydraulic torque generator (1) is stopped by blocking the hydraulic pressure from the hydraulic power source (31), the first chamber of the cylinder in the hydraulic torque generator (1) and The hydraulic oil in the second chamber is blocked by the non-leak type pilot check valve (33a) (33b) so that the movement of the piston (3) is fixed and the movement of the shaft (4) is locked. ,
The first oil passage (28a) and the second oil passage (28b) are closed circuit (34a) by a circuit portion located between the non- leak type pilot check valves (33a) (33b) and a hydraulic torque generator. ) (34b), and each of the closed circuits (34a) (34b ) is provided with safety valves (35a) (35b),
The safety valve (35a) (35b) has an internal pressure of the closed circuit (34a) (34b) when the rated pressure of the closed circuit (34a) (34b) during rotation of the hydraulic torque generator is p1. A lock device in a torque actuator mechanism, which is configured to operate when p1 × 1.5 is exceeded as temperature rises to prevent equipment damage . A drain passage (36) for guiding hydraulic oil leaked from the safety valve (35a) (35b) is provided, and the drain passage (36) is provided between the pilot check valve (33a) (33b) and the hydraulic pressure source (31). Extension passages (55a) and (55b) communicating with each of the first oil passage (28a) and the second oil passage (28b) are formed, and hydraulic oil is supplied to each of the extension passages. The lock device for a torque actuator mechanism according to claim 1, further comprising a check valve (56a) (56b) for preventing inflow from the two oil passages toward the drain passage. The safety valve (35a) (35b) includes a cylinder means (38) that constitutes a leak path (37) for leaking hydraulic oil from the closed circuit (34a) (34b) toward the drain path (36), and the cylinder means. The spool (39) inserted slidably, and a spring (40) that urges the spool in a direction opposite to the leakage direction of the hydraulic oil,
The spool (39) is integrally provided with an operating part (39a) located on the closed circuit side and an extension part (39b) located on the leakage path side, and a communication path formed inside the extension part (39b) ( One end of 47) is in communication with the leakage path (37) and the other end is opened (48) in the outer peripheral surface of the extension (39b),
The cylindrical means (38) is provided with a sealing material (51) on the inner peripheral surface thereof which is in close contact with the outer peripheral surface of the operating portion (38a) of the spool in a state where the spool (39) is biased by the spring (40). And
When the outer peripheral surface of the actuating part (39a) moves away from the sealing material (51) due to the spool (39) moving against the spring (40) due to an increase in the internal pressure of the closed circuit (34a) (34b), Via the clearance between the outer sliding surface (53) of the outer peripheral surface of the operating portion (39a) and the inner peripheral surface of the cylinder means (38), hydraulic fluid is connected from the closed circuit (34a) (34b) to the communication path (47). The lock device in the torque actuator mechanism according to claim 1, wherein the lock device is configured to ooze out toward the head. The clearance between the outer sliding surface (53) of the outer peripheral surface of the actuating portion (39a) and the inner peripheral surface of the cylinder means (38) is formed in the range of 10µ to 40µ. Locking device in the torque actuator mechanism.

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