JP2010071309A - Torque generator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a torque generator for performing driving rotation in the opening direction by hydraulic force, and performing driving rotation in the closing direction by a spring. <P>SOLUTION: This spring return type torque generator includes a piston for advancing-retreating in the axial direction while rotating via a screw means, and a shaft for taking out rotational driving force of the piston, and a forward movement chamber (49a) and a backward movement chamber (49b) are arranged by sandwiching the piston (42). The forward movement chamber (49a) constitutes a hydraulic cylinder (50) for forwardly moving the piston (42) by hydraulic pressure. The backward movement chamber (49b) constitutes a spring equipping chamber (51) for backwardly moving the piston (42) by the spring (54). A bearing (67) is interposed in a pressure contact part between mutual ones of the spring (54) and the piston (42), and thereby, rotation of the piston (42) is not transmitted to the spring (54). <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to, for example, for opening / closing hatch covers in ships, for opening / closing rotation of various valves, for opening / closing various doors, and other rotational force generators used to provide rotational force in the opening / closing direction. The drive rotation is performed with hydraulic pressure, and the drive rotation in the closing direction is performed with a spring force.

  2. Description of the Related Art Conventionally, a forward / reverse hydraulic rotation type rotational force generator is known, and an example that the applicant has proposed in the past will be described with reference to FIG.

  A piston 2 and a shaft 3 are housed inside the casing 1. The shaft 3 is pivoted on a first cover member 4 and a second cover member 5 that pass through the casing 1 and close both ends of the casing 1.

  The piston 2 includes a flange portion 2 a that is inserted into the cylinder 6 of the casing 1 and a cylindrical portion 2 b that is concentrically inserted into the shaft 3.

  The cylindrical portion 2b of the piston 2 is externally inserted to the shaft 3 via a spline 7 so as to be freely rotatable and slidable in the axial direction, and is screwed to the casing 1 via screw means 8. ing. That is, a male screw 9 is formed on the outer periphery of the cylindrical portion 2 b, and the male screw is screwed into a female screw 10 formed on the inner periphery of the casing 1.

  The cylinder 6 is positioned forward and backward in the axial direction sandwiching the flange portion 2a of the piston, constitutes a forward hydraulic chamber 6a and a backward hydraulic chamber 6b, and is provided with inlets 11a and 11b for supplying and discharging pressure oil, respectively. ing.

  When hydraulic pressure is applied to the forward hydraulic chamber 6a from the entrance / exit 11a, the piston 2 receives a thrust force in the forward direction indicated by the arrow X1 in the flange portion 2a, and is screwed by the screw means 8 in the cylindrical portion 2b. It is converted into a rotational force, and thereby rotates in the forward rotation direction F while screwing along the screw means 8. The rotational driving force of the piston 2 is transmitted to the shaft 3 by the spline 7 and rotates the output shaft 3 a at the end of the shaft 3 in the forward rotation direction F.

  On the other hand, when hydraulic pressure is applied to the forward hydraulic chamber 6b from the inlet / outlet port 11b, the piston 2 receives a thrust force in the backward direction indicated by the arrow X2 in the flange portion 2a, and the screw portion 8 of the cylindrical portion 2b. It is converted into a rotational force by screwing, and thereby rotates in the reverse rotation direction R while screwing along the screw means 8. The rotational driving force of the piston 2 is transmitted to the shaft 3 by the spline 7 and rotates the output shaft 3a at the end of the shaft 3 in the reverse rotation direction R.

  When supplying oil from the tank 14 to one of the inlets 11a and 11b by the hydraulic source 13 from the tank 14, the hydraulic device 12 constitutes a hydraulic circuit including a manual switching valve 15 for returning the oil to the tank 14 from the other inlet / outlet. is doing. The shaft 3 is configured to lock the output shaft 3a with the shaft 3 rotating forward or reversely. When the manual switching valve 15 is switched to the locked position, the hydraulic pressure from the hydraulic source 13 is blocked, and the hydraulic pressure at the inlets 11a and 11b is changed. Pilot check valves 16a and 16b are provided for hydraulically blocking the line. Thereby, the movement of the piston 2 in the reciprocating direction is sealed, and the movement of the shaft 3 is locked.

Japanese Patent No. 2860329

  The above-described forward / reverse hydraulic rotation type rotational force generator has the advantage that high torque can be generated because both the forward movement in the X1 direction and the backward movement in the X2 direction of the piston 2 are performed by hydraulic pressure. Depending on the object that the force generator is intended to use, a strong torque may not always be required. In that case, it is desirable to realize energy saving and low cost.

  Also, when using a torque generator as an actuator for opening and closing a door, airtightness is improved by applying a preload in the closing direction to the door rather than locking the door with the door closed as described above. This is preferable.

  Therefore, a spring return type torque generator as shown in FIG. 6 as a comparative example can be proposed.

  As shown in FIG. 6A, a piston 22 and a shaft 23 are housed in the casing 21. The shaft 23 is pivotally mounted on a first cover member 24 and a second cover member 25 that pass through the casing 21 and close both ends of the casing 21.

  The piston 22 includes a flange portion 22 a that is inserted into the cylinder 26 of the casing 21, and a cylindrical portion 22 b that is externally inserted to the shaft 23.

  The cylindrical portion 22b of the piston 22 is extrapolated to the shaft 23 via a spline 27 so as to be rotatable and axially slidable, and is screwed to the casing 21 via screw means 28. ing. A male screw 29 is formed on the outer periphery of the cylindrical portion 22 b, and the male screw is screwed into a female screw 30 formed on the inner periphery of the casing 21.

  A forward movement chamber 31 and a backward movement chamber 32 are provided in front and rear in the axial direction across the screw means 30. The forward movement chamber 31 constitutes a hydraulic cylinder 26 for moving the piston 22 forward by hydraulic pressure, and the backward movement chamber 32 constitutes a spring equipment chamber 34 for moving the piston 22 backward by a spring 33. An inlet / outlet port 40 for supplying / discharging pressure oil to / from the hydraulic cylinder 26 is provided in the cover 25.

  As shown in FIG. 6 (B), the spring 33 is composed of a plurality of sets of unit springs 36P, each of which has two disc springs 36 each having a hole 35 formed at the center, with the outer peripheral portion 37 being held together. The unit springs 36P, 36P,... Are arranged in the axial direction, and the inner peripheral portion 38 of the disc spring 36 is brought into contact between the unit springs facing each other, thereby forming a compression spring as a whole.

  In a compressed state, the spring 33 is externally inserted into the shaft portion 23 b of the shaft 23 that passes through the spring equipment chamber 34, and receiving plates 39 a and 39 b are arranged at both ends, and the receiving plate faces the piston 22. 39a is brought into pressure contact with the shaft end of the cylindrical portion 22b.

  When hydraulic pressure is applied to the cylinder 26 from the inlet / outlet port 40, the piston 22 receives a thrust force in the forward direction indicated by the arrow X1 in the flange portion 22a, and is turned into a rotational force by screwing of the screw means 28 in the cylindrical portion 22b. Thus, it is rotated in the forward direction F while being screwed along the screw means 28. The rotational driving force of the piston 22 is transmitted to the shaft 23 by the spline 27 and rotates the output shaft 23 a at the end of the shaft 23 in the forward rotation direction F. At this time, since the piston 22 moves forward in the X1 direction, the spring 33 is compressed by the cylindrical portion 22b and accumulates a restoring force.

  When the hydraulic circuit (not shown) is switched so that the oil filled in the cylinder 26 is freely recirculated from the inlet / outlet 40 toward the tank, the piston 22 receives the restoring force of the spring 33 so that the piston 22 While receiving the thrust force in the backward movement direction indicated by the arrow X2 in the figure, the screw means 8 is converted into a rotational force by screwing, and thereby the screw means 28 is rotated in the reverse direction R while being screwed back. The rotational driving force of the piston 22 is transmitted to the shaft 23 by the spline 27 and rotates the output shaft 23 a at the end of the shaft 23 in the reverse rotation direction R.

  According to the spring return type torque generator shown in FIG. 6 as a comparative example, the hydraulic circuit is simpler than the forward / reverse hydraulic torque type torque generator shown in FIG. As a result, the piston 22 can be moved back by the spring 33, so that there is an advantage that the power consumption of the hydraulic motor can be saved. Further, even when the piston 22 is completely moved backward, the spring 33 always urges the piston 22 in the backward movement direction, so that when the piston 22 is used as an actuator for opening and closing the door, the closed door is closed. Therefore, there is an advantage that the air tightness of the door can be improved.

  However, the spring return type rotational force generator of the comparative example as shown in FIG. 6 has the following problems to be solved.

 When hydraulic pressure is applied to the cylinder 26 to move the piston 22 forward, the spring portion 33 is pressed and compressed while the cylinder portion 22 b of the piston 22 rotates, so that the rotational motion of the tube portion 22 b is transmitted to the spring 33. For this reason, the adjacent disc springs 36 are worn by rubbing. Further, when the hydraulic pressure of the cylinder 26 is released and the piston 22 is moved back by the restoring force of the spring 33, the cylinder portion 22b of the piston 22 moves backward while rotating, and the spring 33 is rotated. Produce. When such wear progresses, the disc spring 36 may be damaged.

  The spring 33 is held by inserting the shaft portion 23 b of the shaft 23 into the hole 35 of the disc spring 36. At this time, the inner peripheral portion 38 (inner peripheral edge of the hole 35) of the disc spring 36 has a slight clearance with respect to the outer peripheral surface of the shaft portion 23b. However, when the spring 33 is compressed, the clearance is reduced and the disc is reduced. There is a possibility that the inner peripheral portion 38 (the inner peripheral edge of the hole 35) of the spring 36 is in contact with the outer peripheral surface of the shaft portion 23a. Therefore, when the disc spring 36 comes into contact with the shaft portion 23b of the rotating shaft 23, there is a problem that the above-described wear occurs.

  Since the threaded portion of the male screw 29 and the female screw 30 constituting the screw means 28 receives a high surface pressure, it is necessary to add grease or the like. However, if the oil film of grease is deficient due to aging, seizure or abnormal wear may occur, resulting in malfunction. For this reason, it is necessary to provide the casing 21 with a grease inlet for the screw means 28, and it is necessary to periodically perform maintenance by grease injection, which is inconvenient.

  Further, the spring 33 has a plurality of unit springs 36P, 36P,... Arranged in the axial direction, and the receiving plates 39a, 39b press the inner peripheral portion 38 of the disc spring 36 in the unit springs 36P at both ends. Is configured to do. Therefore, when the spring 33 is compressed by the forward movement of the piston 22, the pressing of the disc spring 36 by the receiving plate 39a is unstable.

  The present invention provides a rotational force generator that solves the above-mentioned problems based on a spring return type, and is configured as a piston that moves forward and backward in the axial direction while rotating via screw means. And a rotational force generator having a shaft for extracting the rotational driving force of the piston, wherein the forward movement chamber and the backward movement chamber are provided across the piston, and the forward movement chamber is a hydraulic cylinder for moving the piston forward by hydraulic pressure. The return chamber is a spring-equipped chamber in which the piston is moved back by a spring. A bearing is interposed in the pressure contact portion between the spring and the piston, and the rotation of the piston is transmitted to the spring. It is in the point which comprises so that it may not be made.

  It is preferable that the screw means is connected to the hydraulic cylinder so that the pressure oil in the hydraulic cylinder enters the screw means.

  Stroke restriction that extrapolates a cylindrical shaft to the shaft portion of the shaft that passes through the spring-equipped chamber, and constitutes a guide means for mounting a spring on the outer periphery by the cylindrical shaft and makes the piston end abut on the shaft end. It is preferable to constitute the means.

  It is preferable that a cylindrical adapter extending from the piston toward the spring equipment chamber is provided, a receiving plate is provided between the adapter and the spring, and the bearing is provided between the pressure contact surfaces of the adapter and the receiving plate, The cylindrical adapter is preferably extrapolated on the outer periphery of the cylindrical shaft so as to be relatively rotatable and slidable.

  According to the first aspect of the present invention, since a spring return type rotational force generator can be provided, a lock mechanism is not required as compared with the conventional forward / reverse hydraulic rotational type rotational force generator shown in FIG. This simplifies the hydraulic circuit. In particular, the piping from the hydraulic device 69 to the rotational force generator is reduced to one piping 77, so that the number of piping man-hours can be reduced by half and the provision at a low cost is possible. Become. Moreover, since it is a spring return type, energy saving is possible. Further, even when the piston 42 is completely moved backward, the spring 54 always urges the piston 42 in the backward movement direction. Therefore, when the piston 42 is used as an actuator for opening and closing the door, the spring 42 is closed in the closing direction. Thus, it is possible to hold the door in a state where a preload is applied, and the airtightness of the door can be improved.

  In particular, with respect to a spring return type torque generator, a bearing 67 is interposed at a pressure contact portion between the spring 54 and the piston 42 so that the rotation of the piston 42 is not transmitted to the spring 54. The wear of 54 can be suitably prevented and long-term durability can be guaranteed.

  In this case, according to the second aspect of the present invention, the screw means 53 is connected to the hydraulic cylinder 50 and the pressure oil in the hydraulic cylinder is allowed to enter the screw means 53. Even if grease injection means for 53 is not provided, there is no possibility of causing malfunction due to seizure of screw means 53 or abnormal wear, and there is an effect of being maintenance-free.

  According to the third aspect of the present invention, the guide means 64 on which the spring 54 is mounted can be constituted by the cylindrical shaft 58 extrapolated to the shaft portion 43a of the shaft 43, and at the same time, the cylinder There is an advantage that the stroke limiting means 65 of the piston 42 can be constituted by the shaft end of the shaft 58.

  According to the fourth aspect of the present invention, the receiving plate 63a is provided between the adapter 66 provided on the piston 42 and the spring 54, and the bearing 67 is provided between the pressure contact surfaces of the adapter 66 and the receiving plate 63a. Therefore, it is only necessary to prepare adapters 66 having different lengths according to the total length of the spring 54 (the number of the disc springs 60 in the case of the disc spring type). It is possible to cope with this, contributing to the ease of design and production.

  In this case, according to the present invention as set forth in claim 5, since the cylindrical adapter 66 is configured to be extrapolated relative to the outer periphery of the cylindrical shaft 58 so as to be relatively rotatable and slidable, the mounting state of the adapter 66 is There is an advantage of being stable.

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

  As shown in FIG. 1, a piston 42 and a shaft 43 are housed inside the casing 41. The shaft 43 is inserted into the casing 41 and is pivoted on an end plate 44 that closes the tail end of the casing 41 and a bearing plate 45 that closes the tip. In the case of the illustrated example, the casing 41 has a small diameter cylindrical body 41a on the distal end side and a large diameter cylindrical portion 41b on the tail end side coupled and integrated with each other by a bolt 46, and an end plate 44 is attached to the tail end of the large diameter cylindrical portion 41b. A bearing plate 45 coupled with bolts 47 and oil-tightly inserted at the tip of the small-diameter cylindrical portion 41a is fixed with a locking ring 48.

  The piston 42 is located in the vicinity of the connecting portion between the small-diameter cylindrical portion 41a and the large-diameter cylindrical portion 41b, and is built in the small-diameter cylindrical portion 41a. The forward movement direction indicated by the arrow X1 in FIG. The flange portion 42a is slidable in the backward movement direction indicated by the arrow X2. A forward chamber 49a is formed by the small-diameter cylindrical portion 41a and a backward chamber 49b is formed by the large-diameter cylindrical portion 41b across the flange portion 42a. The forward chamber 49a is hydraulically connected to the piston 42 by hydraulic pressure. The return cylinder 49b constitutes a spring equipped chamber 51 in which the piston 42 is moved back by a spring 54.

  The piston 42 includes a cylindrical portion 42b extending from the flange portion 42a in the backward movement direction X2. The cylindrical portion 42b is concentrically inserted with respect to the shaft 43 through the spline 52 so as to be able to rotate along and slide in the axial direction, and is screwed into the small-diameter cylindrical portion 41a via the screw means 53. Has been. The screw means 53 is formed by screwing a male screw 53a formed on the outer periphery of the cylindrical portion 42b and a female screw 53b formed on the inner periphery of the small-diameter cylindrical portion 41a.

  As shown in FIG. 1, a flange 56 facing the end of the cylindrical portion 42 b is provided on the shaft 43 in a state where the piston 42 is moved in the backward movement direction X <b> 2, and between the flange 56 and the bearing plate 45. A thrust bearing 57 is interposed therebetween.

  A cylindrical shaft 58 is externally inserted into the shaft portion 43 a of the shaft 43 that passes through the spring equipment chamber 51, and a spring 54 is externally inserted into the cylindrical shaft 53, and receiving plates 63 a and 63 b that press-contact both ends of the spring 54. Is extrapolated to the cylindrical shaft 53. As shown in FIG. 2, the spring 42 constitutes one set of unit springs 60 </ b> P in a state in which the outer peripheral portion 61 of the two disc springs 60 each having a hole 59 formed in the center is held between the two. The springs 60P, 60P,... Are arranged in the axial direction, and the inner peripheral portion 62 of the disc spring 60 is brought into contact between the unit springs facing each other, thereby forming a compression spring as a whole. At that time, end disk springs 60a and 60b are arranged outside the unit springs 60P at both ends by adding one disk spring 60, and the end disk springs 60a and 60b are received by the receiving plate 63a, 63b. Accordingly, the end disc springs 60a and 60b press the respective outer peripheral portions 61 to the receiving plates 63a and 63b.

  As shown in FIGS. 1 and 3, the cylinder shaft 53 constitutes a guide means 64 having a spring 54 mounted on the outer periphery, and a flange of the piston 42 at the time of forward movement at the shaft end facing the forward movement chamber 49a. Stroke limiting means 65 for abutting the portion 42a is formed.

  Between the piston 42 and the spring 54, a cylindrical adapter 66 extending from the flange portion 42a toward the spring equipment chamber 51 is provided. The adapter 66 is formed separately from the piston 42 in the illustrated example, but may be formed integrally with the piston 42. When the adapter 66 is formed separately, the adapter 66 may be coupled to the flange portion 42a of the piston 42. However, as shown in the drawing, the adapter 66 may be simply sandwiched between the flange portion 42a and the receiving plate 63a by the force of the spring 54. good.

  The adapter 66 has an extended end portion inserted on the outer periphery of the shaft end of the cylindrical shaft 58 so as to be relatively rotatable and slidable. Between the flange 66a provided at the extended end portion and the receiving plate 63a, A thrust bearing 67 is interposed.

  An inlet / outlet port 68 for supplying / discharging pressure oil to / from the hydraulic cylinder 50 is provided in the small-diameter cylindrical portion 41a, and is connected to a hydraulic device 69 as shown in FIG. The hydraulic device 69 includes a tank 70 that stores oil, a hydraulic source 71 that supplies oil, a first valve 73 that is provided in a flow path 72 that supplies oil by the hydraulic source 71, and a branch from the flow path 72. The second valve 75 provided in the reflux path 74 communicated with the tank 70 is provided, and the flow path 72 of the hydraulic device 69 is communicated with the inlet / outlet 68 of the rotational force generator through one pipe 77. . Accordingly, by opening the first valve 73 and closing the second valve 75, oil is supplied to the inlet / outlet 68, and conversely, by closing the first valve 73 and opening the second valve 75, the inlet / outlet is opened. The oil is discharged from 68 and returned to the tank 70, and a release valve 76 is provided between the hydraulic power source 71 and the first valve 73. The hydraulic power source 71 may be a motor-driven pump or a human-powered pump.

  When the first valve 73 of the hydraulic device 69 is opened and the second valve 75 is closed so that oil is fed to the inlet / outlet 68, the hydraulic pressure acts on the hydraulic cylinder 50 as shown in FIG. The flange portion 42a receives a thrust force in the forward movement direction indicated by the arrow X1 in the figure, and is converted into a rotational force by screwing of the screw means 53 at the cylindrical portion 42b, thereby being screwed along the screw means 28. It is rotated in the forward direction F. The rotational driving force of the piston 42 is transmitted to the shaft 43 by the spline 52, and rotates the output shaft 43 b at the end of the shaft 43 in the normal rotation direction F. At this time, since the screw means 53 is connected to the hydraulic cylinder 50, the oil supplied to the hydraulic cylinder 50 enters the screw means 53 and lubricates. A bearing plate 45 is inserted in an oil-tight manner at the tip of the small-diameter cylindrical portion 41a to prevent oil leakage.

  During the forward movement of the piston 42, the adapter 66 moves forward in the X1 direction while rotating and compresses the spring 54 by pushing the receiving plate 63a. At this time, since the thrust bearing 67 is interposed between the adapter 66 and the receiving plate 63a, the rotational force of the adapter 66 is not transmitted to the spring 54 via the receiving plate 63a. Therefore, wear of the disc spring 60 as described with respect to the comparative example of FIG. 6 is not caused. It is preferable to form a gap S1 as shown in the figure so that the rotational force of the adapter 66 is not transmitted to the cylindrical shaft 58, or a bearing may be interposed between them.

  When the adapter 66 moves forward, the spring 54 is compressed by narrowing the interval between the receiving plates 63a and 63b, but the outer peripheral portions 61 of the end disc springs 60a and 60b arranged at both ends are received by the receiving plates 63a and 63b. Since it pushes, the compression operation becomes stable.

  The cylindrical shaft 58 is preferably extrapolated so as to be rotatable relative to the shaft portion 43a of the shaft 43 so that the rotational force of the shaft 43 is not transmitted to the cylindrical shaft 58 on which the spring 54 is mounted. Or a bearing is interposed between them. Thereby, the cylindrical shaft 58 constitutes the guide means 64 that is mounted in a state where no rotational force is applied to the spring 54.

  After the piston 42 moves forward, the piston 42 stops at a position where the flange portion 42 a contacts the stroke limiting means 65 of the cylindrical shaft 58.

  As described above, with the piston 42 moving forward, the spring 54 is compressed and accumulates a restoring force. Therefore, when the first valve 73 of the hydraulic device 69 is closed and the second valve 75 is opened to release the oil filled in the hydraulic cylinder 50 so as to be freely discharged from the inlet / outlet 68, as shown in FIG. In addition, the restoring force of the compressed spring 54 acts on the piston 42 via the receiving plate 63a and the adapter 66, and the piston 22 receives the thrust force in the backward movement direction indicated by the arrow X2 in the drawing, while the screw means 53 It is converted into a rotational force by screwing, and thereby rotates in the reverse rotation direction R while screwing along the screw means 53. The rotational driving force of the piston 42 is transmitted to the shaft 43 by the spline 52 and rotates the output shaft 43b at the end of the shaft 43 in the reverse rotation direction R.

  Thus, even when the piston 42 moves in the backward movement direction while rotating in the reverse rotation direction, the rotational force is not transmitted to the spring 54 as in the forward movement. Also, the oil in the hydraulic cylinder enters the screw means 53 in the same manner as described above.

  The piston 42 stops at a position where the end portion of the cylindrical portion 42 b comes into contact with the flange 56. When a rotational force in the forward rotation direction F is applied to the output shaft 43b from this stopped state, the piston 42 is rotated via the spline 52 and tries to compress the spring 54 while being screwed in the forward movement direction X1 by the screw means 53. However, since the spring 54 repels this, when the rotational force generator is used as an actuator for opening and closing the door, it becomes possible to hold the closed door with a pressure applied in the closing direction. Improves airtightness.

  Of course, the present invention is not limited to the illustrated embodiment. For example, the thrust bearing 67 may be provided between the adapter 66 and the receiving plate 63a, and may be provided on the receiving plate 63a in addition to the case where it is provided on the flange 66a of the adapter as in the illustrated embodiment. Further, since the thrust bearing 67 is intended to prevent the rotational force of the piston 42 from being transmitted to the spring 54, the thrust bearing 67 may be provided between the flange portion 42a of the piston 42 and the adapter 66. Any structure provided between the springs 54 may be used.

  Moreover, since the rotational force of piston 42 is not transmitted to the spring 54 by such a structure, the spring 54 can also be comprised by a coil spring other than the above-mentioned disc spring.

1 is a cross-sectional view showing a state in which a piston is moved backward according to an embodiment of a rotational force generator of the present invention. It is a disassembled perspective view which shows an example of the spring in the rotational force generator of this invention. 1 is a cross-sectional view showing a state in which a piston is moved forward according to an embodiment of a rotational force generator of the present invention. It is a hydraulic circuit diagram which shows an example of the hydraulic device connected with the rotational force generator of this invention. It is sectional drawing which shows the conventional forward / reverse hydraulic rotation type rotational force generator. The spring return type rotational force generator as a comparative example is shown, (A) is a sectional view of the rotational force generator, and (B) is an exploded perspective view showing a spring.

Explanation of symbols

41 Casing 42 Piston 42a Flange 42b Tube 43 Shaft 43a Shaft 43b Output shaft 49a Forwarding chamber 49b Returning chamber 50 Hydraulic cylinder 51 Spring equipment chamber 53 Screw means 54 Spring 58 Tube shaft 60 Disc spring 60a End disc spring 63a 63b Receiving plate 64 Guide means 65 Stroke limiting means 66 Adapter 67 Thrust bearing 68 Entrance / exit 69 Hydraulic device

Claims (5)

In a rotational force generator comprising a piston that moves forward and backward in the axial direction while rotating via a screw means, and a shaft that takes out the rotational driving force of the piston,
A forward chamber (49a) and a backward chamber (49b) are provided across the piston (42), and the forward chamber (49a) constitutes a hydraulic cylinder (50) for moving the piston (42) forward by hydraulic pressure. The return chamber (49b) constitutes a spring equipped chamber (51) in which the piston (42) is moved back by the spring (54),
A bearing (67) is interposed in a pressure contact portion between the spring (54) and the piston (42), and the rotation of the piston (42) is configured not to be transmitted to the spring (54). Rotating force generator. The rotation according to claim 1, wherein the screw means (53) is connected to the hydraulic cylinder (50), and the pressure oil in the hydraulic cylinder is allowed to enter the screw means (53). Force generator. The cylindrical shaft (58) is extrapolated to the shaft portion of the shaft (43) that passes through the spring equipment chamber (51),
The cylindrical shaft (58) constitutes a guide means (64) for mounting a spring (54) on the outer periphery, and constitutes a stroke limiting means (65) for contacting the piston (42) during forward movement to the shaft end. The rotational force generator according to claim 2 or 3, characterized by comprising: A cylindrical adapter (66) extending from the piston (42) toward the spring equipment chamber (51) is provided, and a receiving plate (63a) is provided between the adapter (66) and the spring (54). 4. The rotating force generator according to claim 1, wherein the bearing (67) is provided between the pressure contact surfaces of the receiving plate (63) and the receiving plate (63a). 5. The rotational force generator according to claim 4, wherein the cylindrical adapter (66) is externally attached to the outer periphery of the cylindrical shaft (58) so as to be relatively rotatable and slidable.

Images