JP2010112548A - Actuator for valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotation control actuator for a valve efficiently transmitting the rotating torque of high-output at a large reduction ratio, maintaining compactness thereof, by preventing internal parts from being projected when transmitting power. <P>SOLUTION: This actuator for a valve includes: an eccentric body 30 to be eccentrically rotated by a motor 23; an external gear 31 to be rotated by eccentric rotation of the eccentric body 30; and a reduction gear mechanism 25 which outputs a rotation component of the external gear 31 to an output shaft 27 from a carrier part 33 through an inner pin 32 provided in the external gear 31. In this case, a base part 29 of the output shaft 27 is made to pass through the eccentric body 30, and an auxiliary flange 44 is arranged to be fitted to the eccentric body 30, and an upper part of the inner pin 32 is fixed to the auxiliary flange 44, and a lower part of the inner pin 32 is fixed to the carrier part 33 to form the inner pin 32 into the straddle mounted structure. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a valve actuator that is mounted on a rotary valve such as a ball valve or a butterfly valve, and is compact and can obtain a large reduction ratio, and more particularly to a valve actuator that is suitable for mounting on a large and high-power valve. .

  Conventionally, there is an actuator equipped with an inscribed planetary gear mechanism as a valve actuator that is mounted on a rotary valve such as a ball valve or a butterfly valve and is compact and has a large reduction ratio. This actuator also has advantages such as many meshing points and resistance to shock load.

  In this type of valve actuator, for example, a reduction gear 1 shown in Patent Document 1 and FIG. 23 is mounted. In the reduction gear 1 of the document 1 and FIG. 23, the pinion gear 3 of the electric motor 2 meshes with the intermediate gear 4 and the intermediate gear 4 meshes with the input gear 5 in FIG. The input gear 5 is coaxially attached to the eccentric shaft 6, and the output shaft 8 is mounted on the inner peripheral side of the eccentric shaft 6 through a bearing 7 in a rotatable state. The lower side of the output shaft 8 is press-fitted and fixed to the inner peripheral side of the carrier 9 and can rotate integrally with the carrier 9. The carrier 9 is formed with press-fitting holes 9a radially from the center, and the lower end side of the inner pin 10 is press-fitted and fixed to the press-fitting holes 9a. On the other hand, the upper side of the output shaft 8 is supported by a ball bearing 13 provided on an attachment plate 12 attached to the gear case 11.

  Further, two trochoidal gears 15 and 15 are rotatably mounted on the outer peripheral side of the eccentric shaft 6 via a bearing 14, and the trochoidal gear 15 meshes with an outer pin 17 constituting an inner tooth of the inner gear 16. is doing. Further, a power transmission hole 15b is formed in the trochoid gear 15, and the above-described inner pin 10 is loosely fitted in the power transmission hole 15b. With this configuration, the inner pin 10 is in a state of supporting the trochoidal gears 15 and 15 via the power transmission hole 15b in a state where the lower end side is cantilevered.

  When the pinion gear 3 of the electric motor 2 rotates, the rotation of the pinion gear 3 is transmitted to the intermediate gear 4, and the rotation is transmitted to the input gear 5 through the intermediate gear 4 so that the eccentric shaft 6 rotates integrally. As described above, this actuator is configured such that power is transmitted to the outer peripheral side of the eccentric body 6 serving as an input shaft. The trochoid gear 15 swings and rotates in the internal gear 16 due to the eccentric rotation of the eccentric shaft 6, and this rotation is transmitted to the carrier 9 and the output shaft 8 via the inner pin 10. At this time, in the inner pin 10, power is transmitted from the contact point with the power transmission hole 15 b of the trochoid gear 15 to the press-fitting and fixing portion with the carrier 9.

  On the other hand, the reduction gear of Patent Document 2 is provided with first and second flanges disposed in a casing, and an intermeshing planetary gear reduction in which an input shaft is rotatably supported by the first and second flanges. The structure is provided with a part. In the reduction gear, when the rotation of the input shaft is rotated, the rotation is decelerated by the intermeshing planetary gear reduction unit and output from the first and second flanges.

  On the other hand, the planetary gear speed reducer of Patent Document 3 includes an input rotation shaft, an eccentric shaft, an external gear, an internal pin, and an internal pin holding flange, and fixes either the internal gear or the internal pin holding flange. Then, the decelerated rotation or the accelerated rotation is taken out from the other side. This speed reducer has an inner pin support ring on the opposite side of the inner pin holding flange, and has a structure in which both inner pins are supported by a bearing provided on the output side of the output shaft and the inner pin support ring. .

  The inscribed mesh planetary gear structure of Patent Document 4 has a structure in which one end side of an inner pin that transmits an automatic component is fixed to a flange portion, and the other end side is fixed to an annular support ring and incorporated. . In this planetary gear structure, both the support ring and the flange portion are both supported by the casing via a pair of bearings.

Japanese Patent No. 3975141 JP 2006-38108 A Japanese Patent No. 2525597 JP-A-5-44788

  However, in the actuator equipped with the reduction gear 1 of Patent Document 1 and FIG. 23, one end side of the inner pin 10 is cantilevered by the carrier 9, and the other end side is a free end. For this reason, when the trochoid gear 15 swings and rotates and the inner pin 10 receives a normal force, the inner pin 19 may swing and the output shaft 8 may swing due to the carrier 9. . In this case, an excessive radial load may be applied to the eccentric shaft 6 and the bearings 7 and 14 mounted on the inner and outer peripheral sides of the eccentric shaft 6 due to the shaft runout, which may cause a phenomenon in which they rise upward. Further, due to this rising phenomenon, the input gear 5 provided on the eccentric shaft 6 also rises or tilts, and the contact with the intermediate gear 4 becomes unstable, and the power transmission efficiency from the electric motor 2 is increased. Problems such as worsening and increased noise occurred.

  Further, when the inner pin 10 is swung, there is a risk that the diameter of the press-fitting hole 9a is enlarged and the inner pin 10 is dropped from the press-fitting hole 9a. In this case, the dropped inner pin 10 may be bitten into the gear case 11 and damage the gear case 11 or the speed reducer 1.

  Further, due to the shaft runout of the output shaft 8 due to the shaft runout of the inner pin 10, the vertically parallel trochoid gear 15 contacts the outer pin 17 in an inclined state, and at this time, the outer teeth 15 a of the upper and lower trochoidal gears 15, 15. , 15a change with respect to the outer pin 17, and as a result, the outer pin 17 may rise upward. Therefore, in FIG. 23, a presser plate 18 is provided to prevent the outer pin 17 from coming off. However, the presser plate 18 cannot suppress the shaft runout of the output shaft 8, and the trochoidal gear 15 is connected to the outer pin 17. It cannot be prevented from leaning against.

  Moreover, since a large radial load is applied to the bearings 7 and 14 due to the shaft runout, it is necessary to provide the components constituting the reduction gear 1 tough to prevent failure due to the radial load. For example, it is conceivable that the ball bearing 13 is formed larger or the thickness of the mounting plate 12 is increased. In this case, however, there is a possibility that the size of the reduction device 1 is increased due to an increase in parts. In particular, the mounting plate 12 is insufficient in strength to apply an excessive radial load, and as a countermeasure, it is necessary to reinforce a knock pin or the like in addition to the screw 19 when mounted on the gear case 11. become. Furthermore, if the strength is increased while maintaining the overall compactness, there is a case where the size of parts is restricted and sufficient output torque cannot be obtained.

  On the other hand, since the speed reduction device of Patent Document 2 has a flange-like output side and a structure in which the flange rotates, it is difficult to detect the rotation state of the flange with a limit switch or the like. For this reason, it is difficult to mount this reduction gear on a valve actuator that can be rotationally controlled.

  In the reduction gears in Patent Documents 3 and 4, the motor, the eccentric shaft, and the gear train are housed in the body of the actuator, and the limit switch can be housed in the body as well. However, since this reduction gear has a structure in which the output shaft extends to the side opposite to the input shaft, the rotation of the output shaft cannot be detected by a limit switch. For this reason, these reduction gears cannot be used as valve actuators for rotation control.

  The present invention has been developed in order to solve the conventional problems, and the object of the present invention is to prevent the rising phenomenon of internal parts in power transmission, and to maintain a compact size while maintaining a high reduction ratio. An object of the present invention is to provide a valve actuator for rotation control that can transmit output rotation torque with high efficiency.

  In order to achieve the object, an invention according to claim 1 includes an eccentric body that rotates eccentrically by a motor, an external gear that rotates by receiving the eccentric rotation from the eccentric body, and a rotation component of the external gear. In a valve actuator having a reduction gear mechanism that outputs the output shaft to the output shaft from the carrier portion via an inner pin provided on the external gear, the base portion of the output shaft is passed through the eccentric body, and the fitting position to the eccentric body The valve actuator is provided with an auxiliary flange to be fixed, an upper portion of the inner pin fixed to the auxiliary flange, and a lower portion of the inner pin fixed to the carrier portion so that the inner pin is supported at both ends.

  In the invention according to claim 2, the eccentric step portion of the eccentric body is rotatably supported by the inner peripheral lower surface of the auxiliary flange via the bearing body mounted on the outer peripheral side of the eccentric body, and the rising of the eccentric body is suppressed. This is the valve actuator.

  The invention according to claim 3 is the valve actuator in which the upper side of the inner pin is press-fitted and fixed to the auxiliary flange.

  According to a fourth aspect of the present invention, there is provided a valve actuator in which a bearing is disposed on the outer peripheral side of the auxiliary flange, and the outer pin and the external gear that form the internal teeth meshing with the external gear are suppressed on the lower surface of the bearing. It is.

  The invention according to claim 5 is the valve actuator in which the outer pin has a divided structure corresponding to the number of external gears, and the inclination of the outer pin is prevented.

  According to a sixth aspect of the present invention, a contact portion is provided on the lower surface of the auxiliary flange so as to abut against the external gear and suppress the rising of the external gear. This is a valve actuator provided with a recess for avoiding contact of the tooth portion.

  The invention according to claim 7 is the valve actuator in which a concave portion for avoiding contact of the external tooth portion of the external gear is provided on the lower surface of the bearing.

  The invention according to claim 8 is the valve actuator in which the holding plate for pressing the auxiliary flange from above is integrally provided on the bearing.

  According to the ninth aspect of the present invention, the auxiliary flange is rotatably mounted on the base body constituting the actuator main body, and the external pin and the external gear forming the internal teeth that mesh with the external gear on the lower surface of the auxiliary flange. This is a valve actuator that suppresses the rise.

  According to a tenth aspect of the present invention, a contact portion is provided on the lower surface of the auxiliary flange so as to abut against the external gear and suppress the rising of the external gear. This is a valve actuator provided with a recess for avoiding contact of the tooth portion.

  The invention according to claim 11 is the valve actuator in which a washer concentric with the eccentric body and covering a part or all of the upper surface of the inner pin is rotatably arranged on the upper surface side of the auxiliary flange.

  The invention according to claim 12 is provided with an eccentric body that is eccentrically rotated by a motor, an external gear that is oscillated and rotated in response to the eccentric rotation from the eccentric body, and a rotation component of the external gear is provided in the external gear. In the valve actuator having a reduction gear mechanism that outputs to the output shaft from the carrier part via the inner pin, the lower part of the inner pin is fixed to the carrier part, and the upper part of the inner pin is slid to the inner peripheral surface of the annular holding plate. This is a valve actuator that holds the shaft core of the inner pin by making contact and fixing the pressing plate to the base body constituting the actuator body.

  According to the thirteenth aspect of the present invention, the presser plate is disposed on the upper surface side of the external pin and the external gear that form internal teeth that mesh with the external gear, and the upward movement of the external pin and the external gear is suppressed on the lower surface of the presser plate. This is the valve actuator.

  The invention according to claim 14 is the valve actuator in which a spacer is rotatably interposed between the external gear and the pressing plate.

  According to the fifteenth aspect of the present invention, a contact portion is provided on the lower surface of the retainer plate so as to abut against the external gear to prevent the external gear from rising, and a part of the contact portion includes an external gear. This is a valve actuator provided with a recess for avoiding contact of the tooth portion.

According to the first aspect of the invention, the inner pin is supported from both the upper and lower sides to prevent the internal parts from being lifted during power transmission, and the high reduction torque is maintained with a large reduction ratio while maintaining compactness. Can be provided with high efficiency. In this case, in particular, an actuator that has another gear train such as a spur gear train in front of the reduction gear mechanism and inputs power from the outer peripheral side of the eccentric body that serves as the input shaft of the reduction gear mechanism by this spur gear train. Is suitable. Since this actuator can penetrate the output shaft with respect to the eccentric body, the rotation of the output valve shaft can be detected by a limit switch or the like to control the rotation of the valve valve body.
The reduction gear mechanism tries to generate resonance by adding radial load due to eccentric rotation of the eccentric body and swinging rotation of the spur gear, and radial load due to rotation of the output shaft. The inner pin can be held and supported by the flange and the carrier portion, and the rotation of the valve can be accurately controlled by stabilizing the rotation.

  According to the second aspect of the present invention, the rotation of the output shaft is stabilized by supporting the eccentric body via the bearing body with the auxiliary flange and suppressing the rising of the eccentric shaft, and the meshing between the gears is stabilized. Thus, highly accurate rotation control can be performed while improving power transmission efficiency.

  According to the invention of claim 3, by improving the rigidity of the inner pin, the shaft runout of the output shaft can be prevented, and the inner pin can be prevented from falling off. Further, the auxiliary flange can be easily positioned with respect to the inner pin to integrate them.

  According to the fourth aspect of the present invention, it is possible to prevent the outer pin and the external gear from being lifted by the bearing, and to ensure a good contact between the external gear and the external pin, thereby improving the power transmission efficiency. become. Further, since the single bearing serves as both a bearing function and a lifting prevention function, the compactness of the entire actuator can be ensured.

  According to the invention which concerns on Claim 5, it can prevent that an outer pin inclines at the time of the rocking | fluctuation rotation of an external gear, and can prevent that an output shaft shakes.

  According to the invention which concerns on Claim 6 or 7, the external tooth part of this external gear interferes with or contacts with adjacent members, such as an auxiliary flange and a bearing, suppressing the rising and inclination of an external gear. By avoiding this, each part can be prevented from being damaged. Moreover, since the generation of dust due to interference and contact is prevented, the smooth operation of the reduction gear mechanism can be maintained. From this, the lifetime of the entire reduction gear mechanism can be extended. Further, since the auxiliary flange prevents the outer pin from coming out, the operation of the external gear can be stabilized.

  According to the invention which concerns on Claim 8, it can mount | wear with the auxiliary | assistant flange positioned in the thrust direction by the pressing board, and it becomes possible to prevent the shift | offset | difference to the axial direction of an auxiliary | assistant flange, and to suppress the inclination of the whole reduction gear mechanism. . In addition, the auxiliary flange prevents the outer pin from coming out, so that the operation of the external gear is stabilized.

  According to the invention of claim 9, while simplifying the internal structure, the auxiliary pin and the external gear can be prevented from being lifted by the auxiliary flange, and the tooth contact can be secured satisfactorily, and the power transmission efficiency is improved. In addition, since one auxiliary flange serves as both a bearing mechanism and a lifting prevention mechanism, it is possible to contribute to the compactness of the entire actuator.

  According to the tenth aspect of the invention, it is possible to prevent the external gear from interfering with or coming into contact with the auxiliary flange while preventing the external gear from rising or tilting, thereby preventing damage to each component. Moreover, generation | occurrence | production of cutting powder is suppressed and the smooth operation | movement of a reduction gear mechanism can be maintained. Further, the outer pin is prevented from coming off by the auxiliary flange.

  According to the invention of claim 11, the washer is rotatably arranged between the inner pin and the input side to restrict the inner pin from coming out, and the inner pin is prevented from directly contacting the input side. Power loss can be reduced by suppressing friction between the inner pin and the input side mechanism.

According to the twelfth aspect of the present invention, by holding the shaft core of the inner pin on the upper and lower sides, it is possible to prevent the internal component from being lifted during power transmission, and the high reduction ratio can be achieved while maintaining the compactness. A valve actuator capable of transmitting rotational torque with high efficiency can be provided. In addition, since the output shaft can pass through the eccentric body, an actuator capable of controlling the rotation of the valve valve body by detecting the rotation of the output shaft with a limit switch or the like can be provided.
In addition, resonance that is to occur in the reduction gear mechanism can be suppressed by holding both ends of the holding plate and the carrier portion, and the rotation can be accurately controlled while stabilizing the rotation of the valve.

  According to the thirteenth aspect of the present invention, by pressing with the pressing plate, it is possible to prevent the outer pin and the external gear from rising and to improve the contact between the external gear and the external pin, thereby improving the power transmission efficiency. Can be achieved. Further, since the single presser plate serves both as a bearing function and ascending prevention function, it can contribute to the compactness of the entire actuator.

  According to the fourteenth aspect of the present invention, the lifting of the external gear is suppressed by the pressing plate and the spacer, the inclination of the entire reduction gear mechanism is suppressed, and the load concentration on the bearing portion of the output shaft is suppressed. In addition, the external teeth of the external gear are prevented from interfering with or coming into contact with the holding plate to prevent damage, and the spacer is rotatable, so that the space between the external gear and the holding plate can be reduced. Power loss due to friction is also suppressed.

  According to the fifteenth aspect of the present invention, the presser plate suppresses the rising and inclination of the external gear, suppresses the inclination of the entire reduction gear mechanism, and suppresses load concentration on the bearing portion of the output shaft. Moreover, the damage by the external tooth part of an external gear interfering with or contacting an auxiliary | assistant flange can be prevented.

1 is a partially cutaway front view showing a first embodiment of a valve actuator of the present invention. It is a principal part expanded sectional view in FIG. It is a separation perspective view of a reduction gear mechanism. It is AA sectional drawing of FIG. It is principal part sectional drawing which showed 2nd Embodiment of the actuator for valves of this invention. It is principal part sectional drawing which showed 3rd Embodiment of the actuator for valves of this invention. It is principal part sectional drawing which showed 4th Embodiment of the actuator for valves of this invention. It is the schematic diagram which showed the press-fit state of the cyclic | annular convex part and cyclic | annular concave groove in FIG. It is principal part sectional drawing which showed 5th Embodiment of the actuator for valves of this invention. It is the schematic diagram which showed the press-fit state of the pin member in FIG. It is principal part sectional drawing which showed 6th Embodiment of the actuator for valves of this invention. It is principal part sectional drawing which showed 7th Embodiment of the actuator for valves of this invention. FIG. 13 is a partially enlarged view of FIG. 12. FIG. 13A is a partially enlarged bottom view of FIG. (B) is a partially expanded sectional view of FIG. It is principal part sectional drawing which showed 8th Embodiment of the actuator for valves of this invention. It is the B section enlarged view of FIG. It is principal part sectional drawing which showed 9th Embodiment of the actuator for valves of this invention. It is the C section enlarged view of FIG. It is principal part sectional drawing which showed 10th Embodiment of the actuator for valves of this invention. It is principal part sectional drawing which showed 11th Embodiment of the actuator for valves. It is the E section enlarged view of FIG. It is principal part sectional drawing which showed 12th Embodiment of the actuator for valves. It is the F section enlarged view of FIG. It is principal part sectional drawing which showed the conventional actuator for valves.

Embodiments of a valve actuator according to the present invention will be described below in detail with reference to the drawings.
1 to 3 show a first embodiment of a valve actuator according to the present invention. The actuator main body 20 has a casing 21 and a base body 22, and inside this, a rotational drive source 23 such as a motor, an intermediate spur gear train 24 that rotates the power from the rotational drive source 23 at a reduced speed, And a reduction gear mechanism 25 composed of an inscribed planetary gear mechanism that meshes with the intermediate spur gear train 24.

  The motor 23 can be rotated bi-directionally or in one direction, and is fixed to the upper surface of the base body 22 by fixing means such as a bolt (not shown). A drive shaft (pinion gear) 26 is provided on the output side of the motor 23, and power from the drive shaft 26 is transmitted to the intermediate spur gear train 24. The intermediate spur gear train 24 includes an intermediate gear 24a and an input gear 24b. The drive shaft 26 is engaged with the input side of the intermediate gear 24a, and the input gear 24b is engaged with the output side of the intermediate gear 24a. Yes. The input gear 24b is provided coaxially with an output shaft 27 described later. With such a configuration, the rotation from the motor 23 is input to the reduction gear mechanism 25 via the drive shaft 26 and the intermediate spur gear train 24.

  As shown in FIG. 3, the reduction gear mechanism 25 includes an eccentric body 30, an external gear 31, an inner pin 32, a carrier portion 33, and an output shaft 27. The eccentric body 30 has a substantially cylindrical shape and has a through hole 36 on the inner peripheral side. In FIG. 4, the eccentric body 30 has two rows of eccentric portions 37 that are eccentric in the direction of 180 ° by the amount of eccentricity e with respect to the axis of the output shaft 27 in the axial direction. For this reason, the absolute value in the horizontal direction when the eccentric body 30 moves with respect to the axis of the output shaft 27 is twice the eccentric amount e. Further, the eccentric body 30 is fixed coaxially with the input gear 24b, and rotates together with the input gear 24b as an input shaft when the drive shaft 26 rotates and power is input, and the two eccentric portions 37, 37 are rotated. Is designed to rotate eccentrically. In addition, the crescent-shaped eccentric step part 34 is formed in the outer peripheral side of the eccentric body 30 by the two rows of eccentric parts 37 over the substantially half circumference.

The external gear 31 is attached to the eccentric part 37 of the single or plural eccentric body 30 via a bearing body (for example, a bearing such as a needle bearing) 38 and is eccentric together with the eccentric part 37 when the eccentric body 30 rotates. It is designed to rotate. The bearing bodies 38 and 38 are respectively mounted on an eccentric portion 37 divided by the eccentric step portion 34. In the present embodiment, two external gears 31 are mounted on the eccentric body 30, and a spacer member 35 is interposed between the external gears 31. The external gear 31 has an external tooth portion 31 a composed of an epitrochoid parallel curve on the outer peripheral side, and a part of the external tooth portion 31 a is formed on an internal tooth 39 a of the internal gear 39 formed on the base body 22. Meshed.
The external gear 31 is provided with a plurality of inner pin holes 40, and the inner pins 32 are loosely fitted in the inner pin holes 40. The inner pin 32 is formed with high accuracy from a high hardness material and is attached to the carrier portion 33.

  The internal gear 39 is formed so as to be incorporated into the base body 22. In the present embodiment, the internal teeth 39 a are formed by external pins attached to the base body 22, and are provided at positions where the internal teeth 39 a mesh with the external teeth 31 a of the external gear 31. The internal teeth 39a may be formed by directly processing the base body 22.

  There is a difference in the number of teeth between the internal gear 39 and the external gear 31, and the external gear 31 is oscillated and rotated by receiving the eccentric rotation from the eccentric body 30, and the rotation component is output by the difference in the number of teeth. The For example, if the number of teeth of the internal gear 39 is n and the number of teeth of the external gear 31 is n−α, the reduction ratio is −α (n−α), and the rotation component of the external gear 31 is caused by this reduction ratio. Extracted.

  The carrier portion 33 has a mounting hole 33a to which the inner pin 32 can be attached, and the lower side of the inner pin 32 is press-fitted and fixed to the mounting hole 33a. Thereby, the swinging rotation of the external gear 31 can be output as a rotation component to the carrier portion 33 via the inner pin 32. The carrier portion 33 is formed with a press-fitting hole 33b, and the output shaft 27 is press-fitted and fixed to the press-fitting hole 33b. The carrier part 33 is accommodated in the base body 22 in a state where a lubricant such as grease is applied to the outer peripheral side.

The output shaft 27 has a shaft diameter that can be press-fitted into the press-fitting hole 33b, and is press-fitted and fixed to the press-fitting hole 33b. Thereby, the output shaft 27 is rotatably attached to the attachment recess 22 a formed in the base body 22 in a state of being integrated with the carrier portion 33. Further, a lubricant such as grease is applied between the mounting recess 22 a and the output shaft 27. A connection hole 42 for connecting the valve valve shaft 43 is formed on the bottom surface side of the output shaft 27.
A base portion 28 is integrally formed on the upper side of the output shaft 27 so as to reduce the diameter from the output shaft 27. The base portion 28 penetrates the eccentric body 30, and the upper end portion projects from the base body 22.

  Further, a bearing member 46 is provided on the outer peripheral side of the base portion 28, and the output shaft 27 can rotate relative to the eccentric body 30 via the bearing member 46. The bearing member 46 is preferably a needle roller bearing having a large load capacity capable of receiving a radial load generated between the output shaft 27 and the eccentric body 30. In this case, the base portion 28 needs to have sufficient hardness and fine surface roughness with respect to a portion of the needle roller bearing 46 where a needle roller (not shown) rolls.

  In the present embodiment, the base portion 28 is formed integrally with the output shaft 27, but this base portion may be formed separately from the output shaft. In this case, these can be integrated by forming a press-fitting part in the lower part of the base part and a press-fitting hole into which the press-fitting part press-fits on the upper surface side of the output shaft. Further, at that time, the output shaft 27 and the carrier portion 33 may be provided integrally. When these are integrated, there is no deviation in the rotation direction between the output shaft and the carrier portion, and accurate rotation transmission is performed. It comes to be.

  The upper side of the inner pin 32 is press-fitted and fixed in a loading hole 44 a formed in the auxiliary flange 44, and the inner pin 32 is supported at both ends by the auxiliary flange 44 and the carrier portion 33 described above.

The auxiliary flange 44 is formed on the upper surface side of the upper external gear 31 in a state where the outer diameter is slightly smaller than the outer diameter size of the external gear 31 and the inner peripheral side is located on the upper side of the eccentric body 30. Has been. The auxiliary flange 44 rotatably supports the eccentric step portion 34 of the eccentric body 30 via the bearing body 38 on the outer peripheral side of the eccentric body 30 by the inner peripheral lower surface 44b, and is in a state of being fitted to the eccentric body 30. The rising of the eccentric body 30 is suppressed. Further, a positioning bearing 45 made of, for example, a slide bearing is fastened and fixed to the base body 22 by a set screw (not shown) on the outer peripheral side of the auxiliary flange 44. The bearing 45 is made of an oil-impregnated metal or a resin material having self-lubricating properties, and the bearing 45 enables the auxiliary flange 44 to rotate with respect to the base body 22 together with the output shaft 27.
The bearing 45 may be fixed to the base body 22 by press fitting.

  The bearing 45 is attached to the attachment groove 22 b formed in the base body 22, and the upward movement of the outer pin 39 a and the external gear 31 is suppressed by the lower surface 47 of the bearing 45. The bearing 45 prevents the output shaft 27 from coming out due to the radial load of the output shaft 27 by sliding on the outer peripheral end surface portion and the upper end surface portion of the external gear 31 by lubrication. Further, the bearing 45 lubricates and slides on the upper end surface portion of the external gear 31, so that the external gear 31 located on the upper side, the spacer member 35, the external gear 31 located on the lower side, and the bearing body. 38 to prevent the eccentric body 30 and the output shaft 27 from coming out.

  Further, as shown in FIG. 1, a mounting portion 27a for mounting the control shaft 48 is provided on the output shaft 27, and the control shaft 48 is mounted on the mounting portion 27a. A cam member 50 is attached to the control shaft 48. When the cam member 50 rotates, the valve shaft 43 can be controlled to rotate by turning on and off a valve opening degree detection member 49 such as a limit switch. The valve opening degree detection member 49 is attached in the casing 21 at a position where the cam portion of the cam member 50 can be separated.

  In addition, a meat thinning portion (not shown) is formed inside the base body 22, and the meat thinning portion is reinforced by rib portions 22c formed at appropriate intervals. Thereby, the material used when forming the base body 22 can be reduced, and weight reduction of the actuator main body 20 whole can be achieved.

Next, the operation and action of the above-described embodiment of the valve actuator of the present invention will be described.
When the motor 23 is operated and the drive shaft 26 rotates, this rotation is decelerated by the intermediate spur gear train 24 and then transmitted from the input gear 24 b of the intermediate spur gear train 24 to the eccentric body 30. When the eccentric body 30 rotates, the external gear 31 swings and rotates while being inscribed in the internal gear 39.

  When the external gear 31 swings and rotates, the rotation component of the external gear 31 is extracted due to the difference in the number of teeth between the internal gear 39 and the external gear 31, and between the internal pin hole 40 and the internal pin 32. The oscillation component of the external gear 31 is absorbed by the provided gap, and only the rotation component is transmitted to the carrier portion 33 via the inner pin 32. When the carrier portion 33 rotates, the output shaft 27 integral with the carrier portion 33 rotates, and the valve shaft 43 connected to the output shaft 27 rotates. This rotation direction is opposite to the rotation direction of the eccentric body 30.

  At that time, the transmission of power by meshing between the internal gear 39 and the external gear 31 causes a force vector in the direction of the rotational center of the mesh load due to a pressure angle (not shown) between the internal gear 39a and the external gear 31a. This vector generates a radial load on the eccentric body 30.

  Due to this load, the output shaft 27 tends to run out, but the upper and lower portions of the inner pin 32 are fixed to the auxiliary flange 44 and the carrier portion 33, and the inner pin 32 is fixed by the auxiliary flange 44 and the carrier portion 33. Since both ends are supported, shaft runout is prevented. Thereby, the shaft runout of the output shaft 27 is also prevented, and a radial load is prevented from being applied to the eccentric body 30, the bearing body 38, and the bearing member 46.

  At this time, the eccentric stepped portion 34 is rotatably supported by the inner peripheral lower surface 44b of the auxiliary flange 44 via the bearing body 38, and the rising of the eccentric body 30 is suppressed, so that the rotation of the output shaft 27 is stabilized. In addition, the external gear 31 is prevented from being inclined, and the meshing between the external gear 31 and the internal gear 39 is stabilized. For this reason, a decrease in transmission efficiency from the motor 23 is suppressed, and generation of noise is also suppressed. Further, since the shaft runout of the inner pin 32 is prevented, there is no possibility that the inner pin 32 falls off.

Here, a technique for directly and rotatably supporting the outer periphery of the eccentric body 30 by the inner peripheral lower surface 44b of the auxiliary flange 44 is also assumed. However, the auxiliary flange 44 has a smaller number of rotations than the eccentric body 30, and Since the direction of rotation is also opposite, there is a risk that power transmission efficiency from the motor 23 will be reduced, friction of each part, etc. will occur.
According to the structure of the present embodiment, the eccentric step portion 34 formed in a crescent shape on the outer periphery of the eccentric body 30 is supported by the auxiliary flange 44 via the bearing body 38, so that the minimum necessary contact is achieved. Therefore, it is possible to prevent the eccentric body 30 from rising.

  Further, since the bearing 45 is disposed on the outer peripheral side of the auxiliary flange 44 and the lower surface 47 of the bearing 45 suppresses the rising of the outer pin 39a and the external gear 31, the external gear 31 is connected to the outer pin 39a. Oscillating and rotating in a stable state. In addition, since the auxiliary flange 44 and the bearing 45 can be arranged in a narrow space, high output torque can be obtained without increasing the strength by changing the shape or size of each component.

  Further, in the present embodiment, the size of the auxiliary flange 44 in the diameter direction is slightly smaller than the outer diameter of the external gear 31 so that the lower surface 47 of the bearing 45 is on the upper surface side of the external gear 31 as described above. By abutting and lubricating the grease between them, the movement of the carrier portion 33 and the output shaft 27 in the radial direction is suppressed via the two external gears 31 and 31 and the spacer member 35. can do. Further, during this operation, there is also a function of suppressing the movement of the eccentric body 30 and the input gear 24b provided coaxially with the eccentric body 30 in the radial direction via the external gear 31, the spacer member 35, and the bearing 45. ing. As a result, the contact between the intermediate gear 24a and the input gear 24b is stabilized, and the noise during the rotation operation is further reduced.

  At this time, the auxiliary flange 44 and the bearing 45 prevent leakage of grease from the base body 22 when the outer pin 39a is about to move. Further, since this grease is enclosed in the reduction gear mechanism 25 by the auxiliary flange 44 and the bearing 45, the external gear 31 swings and rotates, and from between the external gear 31 and the external pin 39a. Even if it is once pumped, the external gear 31 is returned to the meshing position between the external gear 31 and the external pin 39a by repeated swinging and rotation of the external gear 31. Thereby, the lubrication by grease is stabilized.

Next, FIG. 5 shows a second embodiment of the valve actuator in the present invention. In the following embodiments, the same parts as those in the above embodiments are represented by the same reference numerals, and the description thereof is omitted.
In the speed reduction gear mechanism 51 in this embodiment, the outer pin 52 has a divided structure corresponding to the number of external gears 31, and the outer pin 52 is disposed at a position where the external gear portion 31 a of the external gear 31 meshes. This inclination of the outer pin 52 is prevented. For example, when two external gears 31, 31 are provided as shown in the figure, these external gears 31, 31 are opposed to each other at an angle of 180 ° and are eccentrically moved, so that only the upper and lower outer pins 51 are provided. Engage so that it touches. As a result, the upper and lower external gears 31 and 31 mesh with the upper and lower sides of the outer pin as in the case where the two external gears 31 and 31 mesh with one outer pin. There is no such thing as tilting. Therefore, the rising of the outer pin 52, the external gear 31, the eccentric body 30, and the like due to the inclination of the outer pin 52 is prevented.

  Furthermore, since the outer diameter of the spacer member 35 mounted between the upper and lower outer pins 52, 52 is widened to partition the outer pin 52, the external gear 31, the internal gear 39, the base body 22, etc. The upper and lower intervals of the outer pins 52 are kept constant without being affected by the machining accuracy, and the external gear 31 is prevented from contacting any portion other than the engaging outer pins 52. For this reason, it is possible to stabilize the operation of the reduction gear mechanism 25 without adding extra parts or performing additional processing. The above-described outer pin splitting structure and the partition structure by the spacer member can be provided as appropriate for an actuator having a structure other than the present embodiment.

  FIG. 6 shows a third embodiment of the valve actuator of the present invention. The actuator in this embodiment is provided with tapered surfaces 63 and 64 each having a Morse taper at the joint portion between the output shaft 61 and the carrier portion 62, and a pressing force is applied from the output shaft 27 side by a bolt or the like (not shown). 61 and the carrier part 62 are integrated. In this case, the output shaft 61 and the carrier portion 62 can be firmly fixed while exerting a large wedge force on the tapered surfaces 63 and 64.

  Further, by applying an adhesive (not shown) between the tapered surfaces 63 and 64, the output shaft 61 and the carrier portion 62 can be assembled with the adhesive adhered to the entire tapered surfaces 63 and 64. These can be integrated in a state in which the variation is prevented. For this reason, it is possible to join the output shaft 61 and the carrier portion 62 while maintaining the accuracy during joining and increasing the joining strength, and it is possible to suppress variations in product accuracy.

  Further, since the joining between the output shaft 61 and the carrier portion 62 is not press-fit, joining is possible even when the difference in hardness is small, and stainless steel or the like having excellent corrosion resistance can be used as the output shaft 61. In this case, since the base 65 has insufficient hardness as a surface to which the bearing member 46 is inserted, a reinforcing cylindrical member (not shown) for sliding the bearing member 46 is provided on the outer peripheral side of the base 65. It is preferable to press-fit.

7 and 8 show a fourth embodiment of the valve actuator of the present invention. In the actuator according to this embodiment, an annular groove 73 is formed in a part of the press-fitting portion of the output shaft 71 into the carrier portion 72, as shown in FIG. An annular convex portion 74 is formed at a position corresponding to the annular concave groove 73 in the carrier portion 72. When the output shaft 71 and the carrier portion 72 are joined, after the output shaft 71 is press-fitted into the carrier portion 72, the formation portion of the annular convex portion 74 of the carrier portion 72 is crimped from the outer peripheral side and crushed. To integrate them. At this time, when the annular convex portion 74 is press-fitted into the annular concave groove 73, the output shaft 71 and the carrier portion 72 are firmly joined to each other by the knurl processing portion or the spline processing portion. Thereby, the load capability with respect to the rotational torque which acts on these improves.
As described above, the output shaft 71 and the carrier portion 72 are press-fitted in a cylinder to ensure the assembling accuracy, and the caulking process is used in combination with the cylindrical press-fitting, thereby improving the strength against the output torque that is applied during driving.

  9 and 10 show a fifth embodiment of the valve actuator of the present invention. In the actuator in this embodiment, the output shaft 81 is formed of a material having a post-processing hardness, and a reinforcing cylindrical member 82 for sliding the bearing member 46 on the outer peripheral side of the base portion 86 of the output shaft 81 is used. Is press-fitted. Further, when the output shaft 81 and the carrier portion 83 are joined, after the output shaft 81 is press-fitted into the carrier portion 83, as shown in FIG. 10, a pin member is provided at the boundary portion between the output shaft 81 and the carrier portion 83. A mounting hole 85 for inserting 84 is drilled, and the pin member 84 is press-fitted into the mounting hole 85. The pin member 84 may be other than a normal pin. For example, a spring pin may be used. Moreover, what is necessary is just to make it increase / decrease the number of the pin members 84 as needed.

  By adopting such a configuration, it is possible to improve the joining accuracy by cylindrical press-fitting between the output shaft 81 and the carrier portion 83, and when rotational torque is applied between them, the output shaft 81 and the carrier portion 83 And the shear resistance of the pin member 84 between the output shaft 81 and the carrier portion 83 are exerted, and the strength against the output torque acting during driving can be increased.

  FIG. 11 shows a sixth embodiment of the valve actuator of the present invention. In the actuator in this embodiment, a knurled portion 93 is provided by a knurling process at a press-fitting portion of the output shaft 91 into the carrier portion 92, and cylindrical portions 94 and 95 are provided on the upper and lower sides of the knurled portion 93. The cylindrical portion 94 on the upper side of the knurled portion 93 is formed to guide the knurled portion 93 to the carrier portion 92, and has an outer diameter that can be press-fitted into the press-fitting hole 92 a of the carrier portion 92. On the other hand, the cylindrical portion 95 on the lower side of the knurled portion 93 is formed to correct the position of the output shaft 91 with respect to the carrier portion 92 and has an outer diameter that can be press-fitted into the enlarged diameter hole portion 92b formed in the carrier portion 92. Is done.

With this configuration, the actuator can be easily joined while correcting the inclination of the output shaft 91 and the carrier portion 92 as compared with the case where only the knurled portion is provided. Even if the knurled portion 93 is distorted by applying the hardness, the output shaft 91 and the carrier portion 92 can be joined while maintaining high accuracy to increase the strength against the output torque during driving.
As shown by the two-dot chain line in FIG. 11, the lower cylindrical portion 95 may be formed in a bowl shape. In this case, the plane portion on the upper surface side of the flange portion 96 is contacted with the bottom surface side of the carrier portion 92. The assembly accuracy of the output shaft 91 and the carrier portion 92 is corrected by incorporating them so as to contact each other.

  Next, FIG. 12 shows a seventh embodiment of the valve actuator of the present invention. In the actuator in this embodiment, an auxiliary flange 100 is provided on the upper surface side of the external gear 31, and a contact portion 101 and a recess 102 are provided on the lower surface 100 a of the auxiliary flange 100.

  The abutting portion 101 is an inner peripheral area of the auxiliary flange lower surface 100 a and is provided at a position where the abutting portion 101 abuts on the external gear 31 and suppresses the rising of the external gear 31. More specifically, the contact portion 101 is provided on the inner side (inner diameter side) of the root circle 31b when the external gear 31 of FIG. 4 rotates eccentrically as shown in FIG. With this structure, the abutment portion 101 abuts on the abutment surface 103 of the external gear 31 and has a function of suppressing the rising and inclination of the external gear 31.

  Therefore, the recess 102 is notched in the outer peripheral area of the abutting portion 101. Specifically, as shown in FIGS. 13 (a) and 13 (b), the outermost flange of the auxiliary flange 100 is formed. A ring L is provided on the surface side facing the external tooth portion 31a by a width L from the radial side, and this width L is relative to the eccentric amount e of the external tooth portion 31a when the external gear 31 of FIG. 4 rotates eccentrically. , Width L> eccentric amount e × 2 is set. Thereby, the recessed part 102 is formed wider than the eccentric motion area | region R of the external tooth part 31a of the external gear 31. FIG. Due to the concave portion 102, when the external gear 31 comes into contact with the contact portion 101, contact of the external tooth portion 31a that enters and exits due to the eccentric motion to the auxiliary flange 100 is avoided. Then, the rising of the external gear 31 that oscillates and rotates in the thrust direction is restricted, and output by the smooth rotation operation of the reduction gear mechanism 25 is enabled.

  Thus, by providing the contact portion 101 and the recess 102 in the auxiliary flange 100, without increasing the processing accuracy of each component such as the external gear 31 or complicating the internal structure, a high torque, for example, An actuator capable of generating a torque of 1000 N can be provided. For this reason, the quarter turn type as in this embodiment is a type in which a part of the output shaft 27 comes into contact with the base body 22 and stops rotating, and an actuator that does not require relatively high accuracy can be manufactured at a cost. It becomes possible to produce while suppressing ups.

  In addition, since it is not necessary to increase the thickness of each component or to make it large, the size of the entire actuator can be prevented. In addition, since the non-contact structure between the external tooth portion 31a and the auxiliary flange 100 prevents the generation of cutting powder, it is avoided that the cutting powder mixes with grease or the like filled therein, and the operation of each section is hindered. No wear or wear is promoted.

Further, a bearing 104 is provided on the outer peripheral side of the auxiliary flange 100, and a concave portion 105 is provided on a surface of the lower surface 104a of the bearing 104 facing the external tooth portion 31a of the external gear. The concave portion 105 prevents the external tooth portion 31a from coming into contact with the bearing 104, and prevents the external tooth portion 31a from coming into contact with the bearing 104 during the swing motion and damaging the bearing 104.
In this example, the above-described width L is secured by the concave portion 102 provided on the lower surface of the auxiliary flange 100 and the concave portion 105 provided on the lower surface 104 a of the bearing 104. Note that the lower surface 104a of the bearing 104 prevents the outer pin 39a from rising.

  FIG. 14 shows an eighth embodiment of the valve actuator of the present invention. In this actuator, a bearing 111 is disposed on the outer peripheral side of the auxiliary flange 100, and a disc-shaped pressing plate 112 is integrally formed on the upper side of the bearing 111.

  In the enlarged view of part B in FIG. 15, the bearing 111 is mounted in the mounting groove 22 b and is fixed to the base body 22 without interfering with the intermediate spur gear train 24 by a bolt or the like (not shown). At this time, the bottom surface 112a of the pressing plate 112 is disposed on the outer peripheral side of the upper surface of the auxiliary flange 100, the auxiliary flange 100 is pressed from above by the pressing plate 112, and the inner peripheral surface 111a of the bearing 111 is the outer periphery of the auxiliary flange 100. By being arranged on the side surface, the auxiliary flange 100 is restrained in the thrust direction and the radial direction by the bearing 111 to prevent shaft runout, and further, the rising of the entire reduction gear mechanism 25 is restrained. The presser plate 112 can effectively prevent the internal parts including the auxiliary flange 100 from rising even in a narrow space between the auxiliary flange 100 and the intermediate spur gear train 24.

  Moreover, since the pressing plate 112 holds the upper surface side of the auxiliary flange 100, the tilt of the output shaft 27 is effectively suppressed even when the bearing 111 is a small slide bearing, and the rotation state of the output shaft 27 is reduced. Is detected with high accuracy by a limit switch or the like via the control shaft 48. Further, since the upper surface of the inner pin 32 abuts against the bottom surface 112a, the bearing 111 prevents the inner pin 32 from slipping out and avoids a decrease in efficiency or malfunction, and the holding plate 112 prevents the input side input gear 24b. And the auxiliary flange 100 on the output side are cut off, and the actuator operates stably. Also in this embodiment, the above-mentioned width L is secured by the concave portion 102 and the concave portion 105, and contact of the external tooth portion 31a with the auxiliary flange 100 and the bearing 111 is avoided.

  FIG. 16 shows a ninth embodiment of the valve actuator of the present invention. In this actuator, an annular auxiliary flange 120 is disposed on the upper surface side of the external gear 31, and an outer peripheral side surface 120a of the auxiliary flange 120 is rotatably mounted on a base body 22 constituting the actuator body. In this way, by adopting a structure in which the bearing is omitted, the actuator has a simplified internal structure and is made compact, and the internal teeth that mesh with the external gear 31 by the lower surface 120b of the auxiliary flange 120 can be obtained. The rising of the outer pin 39a and the external gear 31 formed is suppressed.

  A contact portion 121 and a recess 122 are provided on the lower surface 120 b of the auxiliary flange 120. As shown in the enlarged view of part C in FIG. 17, the contact portion 121 is an inner peripheral region of the auxiliary flange lower surface 120 b and is provided at a position that contacts the external gear 31 and suppresses the rising of the external gear 31. It is done. Specifically, as in the seventh embodiment, the contact portion 121 is provided on the inner side of the root circle 31b when the external gear 31 in FIG. 4 rotates eccentrically. With this structure, the abutting portion 121 abuts against the abutting surface 103 of the external gear 31 and suppresses the rising and inclination of the external gear 31.

Therefore, the recess 122 is notch formed in the outer peripheral region of the contact portion 121, specifically, annular surface facing the external teeth portion 31a by the width L ₁ from the outermost diameter side of the auxiliary flange 120 The width L ₁ is set to a relationship of width L ₁ > eccentricity e × 2 of the external teeth 31 as in the seventh embodiment. Thereby, when the external gear 31 contacts the contact portion 121, the external tooth portion 31a is prevented from contacting the auxiliary flange 120.

  Further, at this time, since the inner pin 31 is supported at both ends by the carrier portion 33 and the auxiliary flange 120, the internal parts such as the eccentric body 30 are prevented from being lifted up. Therefore, the rotation of the reduction gear mechanism 25 including the auxiliary flange 120 is stabilized and vibration is suppressed. With such a configuration, the outer periphery of the auxiliary flange 120 can be directly supported on the inner peripheral side of the base body 22 without requiring a bearing. At this time, as described above, the contact between the lower surface 120b of the auxiliary flange 120 and the external tooth portion 31a is avoided by the recess 122, and the auxiliary flange 120 can also prevent the outer pin 39a from protruding. Yes.

  The reduction gear mechanism 25 includes an eccentric body 30, an external gear 31, an inner pin 32, a carrier portion 33, and an output shaft 27, and is accommodated in the base body 22. The auxiliary flange 120 is disposed at the upper portion of the reduction gear mechanism 25, and the outer periphery thereof is larger in diameter than the reduction gear mechanism 25.

Accordingly, the speed reduction gear mechanism 25 is rotatably supported with respect to the base body 22 by at least the sliding contact portion 22c with the output shaft 27 at the lower portion of the base body and the sliding contact portion 22d with the auxiliary flange 120 at the upper portion of the base body. Therefore, the inclination and swinging of the reduction gear mechanism 25 itself can be suppressed. That is, the auxiliary flange 120 itself functions as a bearing for the reduction gear mechanism with respect to the base body 22. As with the output shaft 27, the auxiliary flange 120 is rotated at a low speed after being decelerated, and therefore has little friction with the base body 22.
The width L ₁ is set to a minimum value having a relationship of width L ₁ > eccentric amount e × 2 of the external teeth 31, and on the outer peripheral side of the auxiliary flange, similarly to the bearing 104 of the seventh embodiment, A lower surface in contact with the upper end of the outer pin 39a may be provided.

  In this embodiment, the auxiliary flange 120 only needs to have an outer diameter that is inserted into the mounting groove 22b and is rotatable, and the clearance between the outer peripheral surface side of the auxiliary flange 120 and the mounting groove 22b side is small. Is preferred.

  FIG. 18 shows a tenth embodiment of the valve actuator of the present invention. In the actuator in this embodiment, a washer 125 is rotatably arranged on the upper surface side of the auxiliary flange 120 with respect to the actuator of FIG.

  The washer 125 is attached concentrically with the eccentric body 30 and has an outer diameter that covers a part or the whole of the upper surface 32a of the inner pin 32 when performing the eccentric motion. The upper surface 32a side of the inner pin abuts against the washer 125 to prevent the inner pin 32 from coming out, and the occurrence of power loss during input that may occur when the inner pin 32 contacts the input gear 24b is prevented. The risk of falling in efficiency and malfunctioning is avoided. Further, since the washer 125 is arranged in a rotatable state, friction during power transmission is reduced.

  FIG. 19 shows an eleventh embodiment of a valve actuator, and this actuator has a pressing plate 130. The holding plate 130 is formed in an annular shape, is attached to the attachment groove 22b of the base body 22 constituting the actuator body, and is disposed on the upper surface side of the external gear 31 and the outer pin 39a on the eccentric body 30. The lower part of the inner pin 32 is fixed to the carrier part 33, and the upper part of the inner pin 32 is in sliding contact with the inner peripheral surface 130 a of the pressing plate 130. Due to the shaft core holding structure of the upper and lower portions of the inner pin 32 by such a holding plate 130 and the carrier portion 33, the deflection of the external gear 31 is suppressed by suppressing the deflection of the inner pin 32 and the deflection of the output shaft 27. The rise is prevented. At this time, the outer pin 39a and the external gear 31 are pressed by the lower surface 130b of the pressing plate 130, so that the rising of these pins is also suppressed.

  At this time, as shown in the enlarged view of part E in FIG. 20, a ring-shaped spacer 131 is rotatably interposed between the external gear 31 and the pressing plate 130. The spacer 131 is inscribed in the inner pin 32 rotating on the inner peripheral side, and is positioned at a predetermined position by this inscription. By preventing the inclination of the external gear 31 by the spacer 131 and the pressing plate 130, the inclination of the entire reduction gear mechanism 25 is suppressed, and the load concentration on the bearing portion of the output shaft 27 is suppressed. Further, since a gap is provided between the external gear 31 and the pressing plate 130 by the spacer 131, the external tooth portion 31a of the external gear 31 during the eccentric motion may interfere with or come into contact with the pressing plate 130. In addition, since the spacer 131 is rotatable, the friction generated between the external gear 31 and the pressing plate 130 can be minimized.

  FIG. 21 shows a twelfth embodiment of the valve actuator. This actuator has a structure in which the lower side of the inner pin 32 is fixed to the carrier portion 33 and the upper side is in sliding contact with the inner peripheral surface 140a of the pressing plate 140, and the abutting portion 141 and the lower surface 140b of the pressing plate 140 are in contact with each other. A recess 143 is formed. In this case, the pressing plate 140 is formed by forging or pressing, for example.

Similar to the seventh embodiment, the contact portion 141 is an inner peripheral region of the lower surface 140b of the pressing plate 140, and is provided on the inner side of the root circle 31b when the external gear 31 rotates eccentrically. The recess 143 is a outer peripheral area of the contact portion 141, the width L ₂ from the outermost diameter side of the retainer plate 140 is provided on the side facing the outer teeth 31a. Similarly to the seventh embodiment, the width L ₂ is set such that the width L ₂ > the eccentric amount e × 2 of the external teeth 1a.

  This structure prevents the external tooth portion 31a from coming into contact with the contact portion 141 in the F section enlarged view shown in FIG. 22, and the actuator has the contact portion 141 cut away by the external tooth portion 31a. Is prevented, the rising of the external gear 31 is suppressed, and the inclination of the entire reduction gear mechanism 25 is suppressed.

DESCRIPTION OF SYMBOLS 20 Actuator main body 23 Motor 25 Reduction gear mechanism 27 Output shaft 28 Base 30 Eccentric body 31 External gear 31a External tooth 32 Inner pin 33 Carrier part 34 Eccentric step part 38 Bearing (bearing body)
39 Internal gear 39a External pin (internal tooth)
44 Auxiliary flange 44b Inner peripheral lower surface 45, 114 Bearing 47 Lower surface 101 Abutting portion 102 Recessed portion 125 Washer 131 Spacer

Claims (15)

  An eccentric body that rotates eccentrically by a motor, an external gear that rotates by receiving the eccentric rotation from the eccentric body, and a carrier part through an internal pin provided on the external gear with the rotation component of the external gear. In the valve actuator having a reduction gear mechanism that outputs to the output shaft, the base portion of the output shaft is passed through the eccentric body, an auxiliary flange that is fitted to the eccentric body is disposed, and the inner pin An actuator for a valve, characterized in that an upper part is fixed to the auxiliary flange, and a lower part of an inner pin is fixed to the carrier part so that the inner pin is supported at both ends.   The eccentric step of the eccentric body is rotatably supported by the inner peripheral lower surface of the auxiliary flange via a bearing body mounted on the outer peripheral side of the eccentric body, and the rising of the eccentric body is suppressed. Actuator for valves.   The valve actuator according to claim 1 or 2, wherein an upper side of the inner pin is press-fitted and fixed to the auxiliary flange.   The bearing is arrange | positioned in the outer peripheral side of the said auxiliary | assistant flange, and the rising of the external pin and external gear which comprise the internal gear which meshes with the said external gear on the lower surface of this bearing was suppressed. The valve actuator according to Item.   The valve actuator according to claim 4, wherein the outer pin has a divided structure corresponding to the number of the external gears, and the inclination of the outer pin is prevented.   Provided on the lower surface of the auxiliary flange is a contact portion that contacts the external gear and suppresses the rising of the external gear, and a part of the contact portion is in contact with the external tooth portion of the external gear. The valve actuator according to claim 4 or 5, wherein a concave portion to be avoided is provided.   The valve actuator according to claim 4 or 5, wherein a concave portion for avoiding contact of an external tooth portion of the external gear is provided on a lower surface of the bearing.   The valve actuator according to claim 6 or 7, wherein a pressing plate for pressing the auxiliary flange from above is provided integrally with the bearing.   The auxiliary flange is rotatably mounted on a base body constituting an actuator body, and the rising of the external pin and the external gear constituting the internal teeth meshing with the external gear on the lower surface of the auxiliary flange is suppressed. 4. The valve actuator according to any one of 1 to 3.   Provided on the lower surface of the auxiliary flange is a contact portion that contacts the external gear and suppresses the rising of the external gear, and a part of the contact portion is in contact with the external tooth portion of the external gear. The valve actuator according to claim 9, wherein a concave portion to be avoided is provided.   The valve actuator according to claim 9 or 10, wherein a washer that is concentric with the eccentric body and covers part or all of the upper surface of the inner pin is rotatably disposed on the upper surface side of the auxiliary flange.   An eccentric body that rotates eccentrically by a motor, an external gear that rotates by receiving the eccentric rotation from the eccentric body, and a carrier part through an internal pin provided on the external gear with the rotation component of the external gear. In the valve actuator having a reduction gear mechanism that outputs to the output shaft, the lower portion of the inner pin is fixed to the carrier portion, and the upper portion of the inner pin is brought into sliding contact with the inner peripheral surface of the annular pressing plate. The valve actuator is characterized in that the shaft core of the inner pin is held by fixing to the base body constituting the actuator body.   The presser plate is disposed on an upper surface side of an external pin and an external gear that form internal teeth that mesh with the external gear, and the upward movement of the external pin and the external gear is suppressed on the lower surface of the presser plate. The actuator for a valve as described.   The valve actuator according to claim 12 or 13, wherein a spacer is rotatably interposed between the external gear and the pressing plate.   Provided on the lower surface of the pressing plate is a contact portion that contacts the external gear and suppresses the rising of the external gear. The valve actuator according to claim 12 or 13, wherein a recess to be avoided is provided.

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