JP5184293B2 - Valve actuator - Google Patents

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 of Patent Document 1 or FIG. 6 is mounted as an inscribed planetary gear mechanism. As shown in FIG. 6, the reduction gear 1 is usually provided at a position where the electric motor 2 and the input gear 3 are eccentric. The rotation from the electric motor 2 is transmitted to the eccentric shaft 4 via the input gear 3, and the eccentric rotation of the eccentric shaft 4 is transmitted from the inner pin 6 to the substantially annular carrier 7 by the swinging rotation of the trochoid gear 5. An output shaft 8 provided integrally with the carrier 7 rotates. The output shaft 8 and the carrier 7 are integrated in combination in order to reduce the waste of materials during processing and facilitate processing. When these are integrated, the output shaft 8 is set to the carrier 7 such as the degree of perpendicularity in order to secure the mounting accuracy such as the eccentric amount of the eccentric shaft 4 with respect to the output shaft 8, the mounting position, and the inclination. It is necessary to connect in a state where the mounting accuracy is maintained. In order to ensure this assembly accuracy, the output shaft 8 is usually press-fitted and fixed to the carrier 7.

  In addition, the reduction gear 1 is provided with an eccentric shaft support shaft 9 that supports the eccentric shaft 4 above the output shaft 8. The eccentric shaft support shaft 9 is formed integrally with the output shaft 8 so as to penetrate the eccentric shaft 4. A control shaft 10 is connected above the eccentric shaft support shaft 9, and a rotation angle of a valve body connected to the drive shaft 11 by turning on and off a limit switch for detecting the valve opening by a cam attached to the control shaft 10. Can be detected (not shown). The actuator equipped with the speed reduction device 1 detects rotation of the output shaft 8 coaxial with the carrier 7 by the control shaft 10.

Japanese Patent No. 3975141

  However, since the actuator equipped with the reduction gear of Patent Document 1 and FIG. 6 integrates the output shaft 8 by press-fitting the output shaft 8 into the carrier 7 as described above, it can be used when transmitting high-output rotational torque or in the valve. When an overload such as a foreign matter biting in is applied, the carrier 7 and the output shaft 8 may shift in the rotation direction, and rotation transmission may not be performed accurately. In order to avoid this, it is conceivable to increase the fitting shaft diameter of the both, or lengthen the fitting length so as not to deviate from both. However, if the fitting shaft diameter is increased, the output shaft 8 As the outer diameter increases, the waste of material increases, and the advantage of having the output shaft 8 and the carrier 7 as separate structures is lost. On the other hand, when the fitting length is lengthened, the height of the speed reduction mechanism 1 is increased, and as a result, the overall size of the actuator is increased. In addition, an adhesive may be required to fix the output shaft 8 and the carrier 7 more firmly.

  Further, in order to press-fit the output shaft 8 into the carrier 7, it is necessary to provide a hardness difference between the output shaft 8 and the carrier 7, and the output shaft 8 needs to be formed of a material harder than the carrier 7. Quenching is necessary to make the output shaft 8 high in hardness, but if steel-based materials are used for quenching, the corrosion resistance deteriorates due to the characteristics of the steel-based materials. This deterioration in corrosion resistance is not desirable for an actuator for use in corrosive environments or for flowing corrosive fluids. For this reason, it has been difficult to integrally form the output shaft 8 and the carrier 7 while ensuring corrosion resistance.

  The present invention has been developed to solve the conventional problems, and the object of the present invention is to be able to transmit high-output rotational torque obtained by a large reduction ratio with high efficiency while maintaining compactness, Another object of the present invention is to provide a valve actuator that can exhibit excellent durability and corrosion resistance.

To achieve the above object, the invention according to claim 1, the rotational component of the external gear which swings rotated by the eccentric rotation of the eccentric body rotates eccentrically in conjunction with the rotation drive source of the motor, the outer In an actuator using a reduction gear mechanism capable of outputting from a carrier part to an output shaft via an inner pin loosely fitted to a toothed gear, a reaction force due to eccentric oscillating rotation via a bearing at a penetrating position penetrating the eccentric body The base shaft is provided, and an upper portion of the base shaft is provided with a control mounting portion for controlling the valve opening degree detection member, and the lower portion of the base shaft is press-fitted and fixed to the carrier portion provided integrally with the output shaft. The base shaft material is a valve actuator that is made of a material harder than the carrier portion and has a hardness difference between the base shaft and the carrier portion .

In the invention according to claim 2 , the carrier portion is divided into upper and lower carrier portions, the lower carrier portion and the output shaft are integrally provided, and the lower portion of the base shaft is press-fitted and fixed to the upper carrier portion.

In the invention according to claim 3 , a reduced diameter press-fit portion is formed in the lower portion of the base shaft, and the reduced diameter press-fit portion is press-fitted and fixed to the upper carrier portion.

In the invention according to claim 4 , the middle of the lower part of the inner pin is press-fitted and fixed to the upper carrier part, and the lower part of the inner pin is detachably fitted to the lower carrier part.

According to the first aspect of the present invention, the valve actuator is capable of transmitting the high-output rotational torque obtained by the large reduction ratio while maintaining compactness with high efficiency without the shaft center being shaken. In this case, the reduction gear mechanism tends to generate resonance due to the radial load caused by the eccentric rotation of the eccentric body and the swinging rotation of the spur gear and the radial load caused by the rotation of the output shaft. Resonance to be generated in the entire mechanism can be suppressed by the base shaft fixed to the output shaft, and the rotation of the valve can be accurately controlled by outputting a stable rotation.
In particular, a suitable reduction gear that is eccentric with an equal angle to the axis of the eccentric body in a state in which several sheets of external gears double are arranged vertically, according to the case, the swinging rotation of the external tooth gear Since the radial loads cancel each other, the base shaft is less likely to receive a reaction force due to eccentric oscillating rotation.
Further, it is excellent in durability and corrosion resistance, and the output shaft can be prevented from being damaged or corroded.

Further, it provided the valve opening degree detecting member limit switch can be detected to control the valve body rotation angle of the output shaft by attaching a control shaft for controlling the valve opening detecting member to the attachment portion. In addition, in this case, since the swing of the base shaft is suppressed, the swing of the control shaft is also suppressed, and the rotation of the valve can be controlled by turning on and off accurately without causing the valve opening degree detection member to malfunction.

Further, for the base shaft in the carrier portion can press fit with high accuracy, also be achieved durability eccentric to improve the support function of the eccentric by the base shaft.

In addition , it is possible to reliably transmit high-output rotational torque by eliminating the shift in the rotational direction between the carrier portion and the output shaft. Furthermore, since the carrier portion and the base shaft rotate together to suppress the swing of the base shaft, the operation of the reduction gear mechanism is stabilized. Further, the base shaft can be easily attached by press-fitting the carrier portion , and the base shaft is not subjected to complicated processing.

According to the invention which concerns on Claim 2 , a carrier part can be divided | segmented by providing an output shaft in a lower carrier part, and a base shaft in an upper carrier part, respectively, and an output shaft can be provided detachably from an actuator main body.

According to the invention which concerns on Claim 3 , a base axis can be integrated with respect to an upper carrier part, suppressing the force at the time of press injection.

According to the invention of claim 4 , the valve can be replaced with a lower carrier part having a different output shaft connection form or material according to the type of valve to be connected or the type of fluid flowing in the valve, and can be used for any valve or fluid. Actuators can be provided.

Hereinafter, an embodiment of a valve actuator according to the present invention will be described in detail with reference to the drawings.
1 to 3, a valve actuator main body 20 according to the present invention includes a rotary drive source 23 such as a motor and an intermediate for decelerating and rotating the power from the rotary drive source 23 inside a casing 21 and a base body 22. A spur gear train 24 and a reduction gear mechanism 25 formed of an internal planetary gear mechanism that meshes with the intermediate spur gear train 24 are provided.

  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 driving shaft (pinion gear) 26 is provided on the output side of the motor 23, and power from the driving shaft 26 can be 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, an output shaft 27, and a base shaft 35. The eccentric body 30 has a substantially cylindrical shape and has a through hole 36 on the inner peripheral side. Further, the eccentric body 30 has two rows of eccentric portions 37 in the axial direction that are eccentric with respect to the axis of the output shaft 27 by an eccentric amount e in FIG. 4. The eccentric body 30 is fixed integrally and coaxially with the input gear 24b, so that when the drive shaft 26 rotates, the two eccentric portions 37, 37 rotate eccentrically in conjunction with the rotation of the input gear 24b. It has become.

  The external gear 31 is attached to the eccentric part 37 of the eccentric body 30 via a bearing 38, and rotates eccentrically with the eccentric part 37 when the eccentric body 30 rotates. The external gear 31 has external teeth 31 a made of an epitrochoid parallel curve on the outer peripheral side, and a part of the external teeth 31 a meshes with the internal teeth 39 a of the internal gear 39 of the base body 22. .

On the other hand, the internal gear 39 is formed so as to be fixed to the base body 22. The inner teeth 39 a are provided by attaching the outer pins to the base body 22, but may be formed directly on 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 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 carrier portion 33 has a mounting hole 33a to which the inner pin 32 can be attached, and the lower end 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 is output as a rotation component to the carrier portion 33 via the inner pin 32. Further, a press-fitting hole 41 is formed on the upper surface side of the carrier part 33, and a reduced diameter press-fitting part 42 of the base shaft 35 described later can be press-fitted into the press-fitting hole 41.
An output shaft 27 that is interlocked with the carrier portion 33 is provided integrally with the lower portion of the carrier portion 33. A valve valve shaft 43 is connectable to the output shaft 27, and the valve shaft 43 rotates with the output shaft 27 when the carrier portion 33 rotates. In the present embodiment, the carrier portion 33 and the output shaft 27 are integrally formed, but they may be separate.

  On the other hand, the upper end side of the inner pin 32 is press-fitted and fixed in a loading hole 44 a of an auxiliary flange 44 provided coaxially with the base shaft 35. The auxiliary flange 44 is rotatably attached to the base body 22 via a bearing 45 on the upper surface side of the external gear 31 positioned on the upper side. With this configuration, the upper and lower ends of the inner pin 32 are both supported by the auxiliary flange 44 and the carrier portion 33.

  The through hole 36 is provided at a penetrating position that penetrates the eccentric body 30, and a base shaft 35 is provided in the through hole 36 via a bearing 46, and the base shaft 35 supports the eccentric body 30. . The base shaft 35 is formed with a reduced diameter press-fit portion 42 at a lower portion thereof, and the reduced diameter press-fit portion 42 is press-fitted and fixed in a press-fit hole 41 of the output shaft 27 (carrier portion 33). As a result, the base shaft 35 rotates integrally with the output shaft 27 and receives a reaction force due to the eccentric rocking rotation of the eccentric body 30. The reduced diameter press-fit portion 42 is set to have a smaller diameter than the output shaft 27, so that the force required for press-fitting is smaller. Further, a contact portion 47 capable of contacting the upper surface 33b of the carrier portion 33 is formed at the step portion of the reduced diameter press-fit portion 42. After the press-fit of the reduced diameter press-fit portion 42, the contact portion 47 is formed on the upper surface 33b. It will be in the state contact | abutted.

  The bearing 46 is preferably a needle roller bearing having a large load capacity capable of receiving a radial load generated between the base shaft 35 and the output shaft 27. In this case, the portion of the needle roller bearing 46 of the base shaft 35 where a needle roller (not shown) rolls needs to have sufficient hardness and surface roughness.

  The base shaft 35 is made of a high-hardness material to facilitate the press-fitting of the reduced-diameter press-fit portion 42 into the press-fit hole 41 and to make the rotation with respect to the eccentric body 30 smooth, and the carrier portion 33 ( Alternatively, it is required to provide a hardness difference with respect to the output shaft 27 or both. In this case, the HRC hardness of the base shaft 35 is set to about 50 to 65, and examples of the material of the base shaft 35 include chromium molybdenum steel (SCM435, SCM415), bearing steel (SUJ2), carbon tool steel (SK4), and alloys. There are tool steel (SKS3), martensitic stainless steel (SUS440C), and the like. Furthermore, these materials are preferably cured by heat treatment (quenching). On the other hand, the HRC hardness of the output shaft 27 is set to about 15 to 30, and the material of the output shaft 27 is carbon steel (S45C), spheroidal graphite cast iron (FCD450), austenitic stainless steel (SUS304, SUS316). , Ferritic stainless steel (SUS430), precipitation hardening stainless steel (SUS630), and the like.

  Further, as shown in FIG. 1, an attachment portion 35a for attaching the control shaft 48 is provided on the upper portion of the base shaft 35, and the control shaft 48 is attached to the attachment portion 35a. A cam member 50 is attached to the control shaft 48. When the cam member 50 rotates, the valve shaft 43 can be rotationally controlled 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.

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 is rotated by this transmission, the external gear 31 swings and rotates while being inscribed in the internal gear 39 by this rotation.

  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 rotates integrally with the carrier portion 33, and the valve shaft 43 connected to the output shaft 27 rotates.

  At that time, transmission of meshing power between the internal gear 39 and the external gear 31 generates a force vector in the direction of the center of rotation of the meshing load due to a pressure angle (not shown) between the meshing internal teeth 39a and the external teeth 31a. However, a radial load is generated in the eccentric body 30 by this vector.

  Due to this load, the output shaft 27 tends to be shaken. The actuator body 20 is provided with a base shaft 35 that supports the eccentric body 30 via a bearing 46 at a penetrating position that penetrates the eccentric body 30. Since the lower portion of the base shaft 35 is formed integrally with the carrier portion 33, the base shaft 35 can prevent the eccentric body 30 from swinging due to the radial load, and the shaft swing of the output shaft 27 can be prevented.

Further, the base shaft 35 is formed of a high hardness material, and the base shaft 35 has a hardness difference with respect to the output shaft 27 (carrier portion 33). Therefore, the reduced diameter press-fit portion 42 can be easily press-fitted into the carrier portion 33. Therefore, it is possible to prevent the occurrence of a galling phenomenon between the two parts and to perform press-fitting with high accuracy. Therefore, while the base shaft 35 and the output shaft 27 can be easily formed separately, the eccentric body 30 is supported in a state in which the swing of the base shaft 35 is prevented with respect to the output shaft 27 after the integration of both. In addition, the output shaft 27, the carrier portion 33, and the base shaft 35 as a whole can suppress vibration during operation of the reduction gear mechanism 25.
At this time, in particular, the radial load is applied to the reduced diameter press-fit portion 42 by receiving the radial load accompanying the swinging rotation of the eccentric body 30 by the contact portion 47 formed in the step portion of the reduced diameter press-fit portion 42. Can be reduced.

  Moreover, since the carrier part 33 and the output shaft 27 are provided integrally, they do not shift in the rotation direction, and the rotation component extracted via the inner pin 32 is transferred from the output shaft 27 via the carrier part 33. It is transmitted as it is. Therefore, the allowable transmission torque of the reduction gear mechanism 25 can be determined from these material strengths and shape dimensions, and this allowable transmission torque can be set large. In addition, a decrease in transmission torque during operation is suppressed as much as possible, and deceleration rotation is accurately transmitted. Furthermore, since the allowable transmission torque can be improved while suppressing the dimensions in the height direction and the radial direction, the actuator body 20 can be made compact.

  Further, the integration of the carrier portion 33 and the output shaft 27 enables easy formation and processing of this part without performing quenching or the like, and the power of the carrier portion 33 and the output shaft 27 is transmitted from the inner pin 32. The strength of the route to be performed can be increased. At this time, since the entire carrier portion 33 may have a low hardness, the carrier portion 33 can be formed of stainless steel or the like having excellent corrosion resistance, and can exhibit excellent corrosion resistance.

  In addition, since the control shaft 48 for controlling the valve opening degree detection member 49 is attached to the upper portion of the base shaft 35, the rotation with little shake by the base shaft 35 can be accurately transmitted to the control shaft 48. The valve opening degree detection member 49 can be accurately turned on / off by the attached cam member 50. In this case, a large torque is not required to operate the valve opening degree detection member 49, and the valve opening degree detection member 49 can be sufficiently operated by the rotational torque of the control shaft 48. As described above, since it is not necessary to transmit a large torque to the control shaft 48, the above-described press-fit reduced diameter portion 42 can be formed with a small diameter.

FIG. 5 shows another embodiment of the valve actuator according to the present invention. In this embodiment, the same parts as those in the above embodiment are represented by the same reference numerals, and the description thereof is omitted.
The reduction gear mechanism 51 in this embodiment is obtained by dividing the carrier portion 52 and providing an upper carrier portion 53 and a lower carrier portion 54.
The upper carrier portion 53 has a substantially disk shape, and the upper carrier portion 53 has a mounting hole 53a. The lower part of the inner pin 32 is press-fitted and fixed in the mounting hole 53a. Further, a press-fit hole 55 is formed through the central portion of the upper carrier portion 53, and the lower portion of the base shaft 57 is press-fitted and fixed to the press-fit hole 55. The lower portion of the base shaft 57 may be a press-fit portion having a reduced diameter as in the above embodiment.

  The lower carrier portion 54 is integrally provided with an output shaft 56 at a lower portion thereof, and the valve valve shaft 43 can be attached to the output shaft 56. Further, a fitting hole 54a is formed in a position corresponding to the mounting hole 53a of the upper carrier portion 53, and the lower portion of the inner pin 32 is detachably fitted into the fitting hole 54a. Yes. With this configuration, the actuator body 51 can transmit the rotation component of the external gear 31 from the carrier portion 52 to the output shaft 56 via the inner pin 32.

  Therefore, when the lower carrier portion 54 is detachably fitted to the inner pin 32 in a state where the reduction gear mechanism 51 is detachably provided from the base body 22 in advance, the lower carrier portion 54 (output shaft 56) Exchange etc. become possible. Accordingly, for example, the lower carrier portion 54 is formed of stainless steel having excellent corrosion resistance, or the attachment / detachment portion of the valve shaft 43 of the lower carrier portion 54 is provided in a convex shape other than the concave shape as shown in FIG. It becomes possible to rearrange 54 easily.

Here, the external gear 31 and the internal gear 39 theoretically have about half of the total teeth when the difference in the number of teeth is 1, and the strength is ensured. Compared to this, the contact portion between the inner pin 32 and the inner pin hole 40 is that the number of the inner pins 32 is small and the distance between the inner pin 32 and the output shaft 27 is closer. Insufficient strength.
In particular, in this embodiment, since the thickness of the lower carrier portion 54 is about half that of the entire carrier portion 52, the press-fit depth of the inner pin 32 into the lower carrier portion 54 becomes shallow, and the power There will be a lack of strength during transmission.

  However, since the lower end side of the inner pin 32 is press-fitted and fixed to the carrier portion 33, the upper end side of the inner pin 32 is press-fitted and fixed to the auxiliary flange 44, and the upper and lower ends of the inner pin 32 are supported at both ends. Works effectively, and the reaction force at the time of rocking rotation is suppressed, and rigidity and strength are secured. For this reason, the load capability as a reduction gear improves, while the whole compactness is maintained.

1 is a partially cutaway front view showing an embodiment of a valve actuator of the present invention. It is principal part sectional drawing in FIG. It is a separation perspective view of a reduction gear mechanism. It is AA sectional drawing of FIG. It is the partially notched front view which showed other embodiment of the actuator for valves of this invention. It is principal part sectional drawing which showed the conventional actuator for valves.

Explanation of symbols

20 Actuator body 23 Motor (Rotation drive source)
25 Reduction gear mechanism 27 Output shaft 30 Eccentric body 31 External gear 32 Internal pin 33 Carrier portion 35 Base shaft 40 Inner pin hole 42 Press-fit portion 44 Auxiliary flange 46 Bearing 47 Contact portion 48 Control shaft 49 Limit switch (valve opening degree detection member) )
52 Carrier part 53 Upper carrier part 54 Lower carrier part

Claims (4)

The rotational component of the external gear which swings rotated by the eccentric rotation of the eccentric body rotates eccentrically in conjunction with the rotation drive source of the motor, from the carrier unit via the pin within which is loosely fitted in the external gear In an actuator using a reduction gear mechanism that can output to an output shaft, a base shaft that receives a reaction force due to eccentric oscillating rotation through a bearing is provided at a penetrating position that penetrates the eccentric body , and a valve opening is provided above the base shaft. An attachment portion for control attachment for controlling the degree detection member is provided, and a lower portion of the base shaft is press-fitted and fixed to the carrier portion provided integrally with the output shaft, and the material of the base shaft is made of a material harder than the carrier portion. An actuator for a valve formed by providing a difference in hardness between the base shaft and the carrier portion . 2. The valve actuator according to claim 1 , wherein the carrier portion is divided into upper and lower carrier portions, the lower carrier portion and the output shaft are integrally provided, and the lower portion of the base shaft is press-fitted and fixed to the upper carrier portion. . The reduced径圧join the club to form the bottom of the base shaft, the valve actuator of claim 2 which is press fitted before SL on the carrier portion of this condensed径圧join the club. 3. The valve actuator according to claim 2 , wherein a middle part of the lower part of the inner pin is press-fitted and fixed to the upper carrier part, and a lower part of the inner pin is detachably fitted to the lower carrier part.

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