Compact spring return actuator

Abstract

This invention relates to a compact spring return actuator, and more particularly to an actuator for emergency reset of a valve in the event of an emergency such as a power outage. The actuator is equipped with differential planetary gear reducers in both the drive shaft (operated by a motor) and the working shaft (operated by an elastic body of the emergency reset assembly), and these differential planetary gear reducers are meshed together. This duality allows the power transmission of the motor and the elastic body to be independent of each other, thereby reducing motor capacity and miniaturizing the components of the power transmission system. Ultimately, this results in a compact spring return actuator that is lightweight and miniaturized as a whole. To achieve the objectives described above, the compact spring return actuator of the present invention is characterized by comprising: a drive shaft that receives power from a motor and rotates; a driven shaft that rotates by means of the drive shaft and opens and closes a valve; a reduction assembly that reduces the rotational force transmitted to the driven shaft, including a differential planetary gear reducer mounted on the drive shaft; and an emergency reset assembly equipped with an elastomer and a working shaft that converts the elastic force of the elastomer into a rotational force for transmission and engagement with the differential planetary gear reducer, for rotating and resetting the valve when the power is disconnected.

Description

Technical Field

[0001] This invention relates to a compact spring return actuator, and more particularly to an actuator for emergency reset of a valve in the event of an emergency such as a power outage. The actuator is equipped with differential planetary gear reducers in both the drive shaft (operated by a motor) and the working shaft (operated by an elastic body of the emergency reset assembly), and these differential planetary gear reducers are meshed together. This duality allows the power transmission of the motor and the elastic body to be independent of each other, thereby reducing motor capacity and miniaturizing the components of the power transmission system. Ultimately, this results in a compact spring return actuator that is lightweight and miniaturized as a whole. Background Technology

[0002] With the gradual advancement of industrial restructuring, traditional independent manned management systems are being integrated into unmanned integrated operating systems across all industrial sectors. Consequently, corresponding efficient integrated operating systems are being built. In particular, in the field of valves that control fluid flow, various automatic valves and automatic flow control devices that can be effectively controlled remotely have also become rapidly popular.

[0003] The electric actuator used in the automatic flow control device described above is a drive device necessary for automating valves and regulating dampers, etc., and consists of a control unit, an auxiliary gear unit, and a motor.

[0004] In simple terms, a typical structure of the electric actuator includes: a motor that rotates when powered; a drive shaft that rotates by means of the motor; and a driven shaft that receives rotational force from the drive shaft, decelerates its rotation, and thereby rotates to open or close the valve; thus, when the motor is working, the driven shaft rotates to one side and thereby opens or closes the valve.

[0005] However, in the existing electric actuators described above, when the valve is open, if the power supply to the drive motor is disconnected due to an emergency such as a power outage, the drive components, including the motor, will also stop, thus making it impossible to perform the opening and closing action of the valve.

[0006] In the circumstances described above, when a valve remains in a stopped state for an extended period of time, safety accidents such as fluid leakage and equipment damage may occur due to damage to the valve or the pipeline through which fluid can flow, or malfunctions of various components of the actuator, which may occur during operation (or after operation).

[0007] Therefore, in Korean Patent No. 10-1130983, a spring-reset valve actuator is used that can use the elastic force of a spring to make the valve work and reset to the state before it was initially working in an emergency situation such as a power outage when the motor cannot be controlled.

[0008] However, existing electric actuators have the following problems.

[0009] First, in existing electric actuators, helical springs or torsion springs are directly connected to the driven shaft that rotates the valve to open and close, i.e., the output shaft of the electric actuator. This forms a power transmission system of power supply connection - motor operation - gear operation of the reduction unit - spring compression - valve operation. Because the accumulation and release of the spring's elastic force are linked to the operation of the motor, the load on the motor becomes very large, requiring a high-power motor and further leading to the problem of actuators becoming larger.

[0010] Secondly, in the existing design structure of electric actuators, the elastic force of the spring will be directly transmitted to the driven shaft. Therefore, its reset impact will also be directly transmitted to the gear components, and the risk of failure is relatively high. This requires the use of high-strength materials to make gear components, which further leads to the problem of their increasing size.

[0011] Third, the preload and fully compressed elastic values ​​of the helical springs or torsion springs used in existing electric actuators differ significantly. Therefore, the force and strength of the motor and gears required for reduction need to be suitable for the fully compressed state of the spring, resulting in excessive weight and inconvenience for users. Furthermore, the large size of the electric actuator due to the high power of the motor and the large size of the gears used to ensure rigidity leads to an excessively large size.

[0012] Fourth, in existing electric actuators, the electronic brake, which limits the operation of the compressed spring, will always remain engaged and thus become magnetized, which may lead to problems such as the electronic brake failing to function properly in emergency situations.

[0013] Fifth, in existing electric actuators, the limit switch used to stop the valve after an emergency reset may be easily damaged by strong impacts. Summary of the Invention

[0014] The present invention aims to solve the existing problems as described above.

[0015] The purpose is to provide an actuator that automatically resets a valve to its original position in the event of an emergency such as a power outage. The actuator is equipped with a differential planetary gear reducer in both the drive shaft (operated by a motor) and the working shaft (operated by an elastic body of an emergency reset component). The differential planetary gear reducers are meshed together, thereby achieving a duality in the power transmission of the motor and the elastic body without interference between them. This reduces the motor capacity while miniaturizing the components of the power transmission system, ultimately resulting in a compact spring reset actuator that is lightweight and miniaturized as a whole.

[0016] To achieve the objectives described above, the compact spring return actuator of the present invention includes:

[0017] The drive shaft receives power from the motor and rotates.

[0018] The driven shaft rotates by means of the drive shaft and opens and closes the valve;

[0019] A reduction gear assembly for reducing the rotational force transmitted to the driven shaft includes a differential planetary gear reducer mounted on the drive shaft; and,

[0020] An emergency reset assembly is equipped with an elastomer and a working shaft that converts the elastic force of the elastomer into a rotational force for transmission and engagement with the differential planetary gear reducer, thereby rotating and resetting the valve when the power is disconnected.

[0021] Furthermore, the compact spring return actuator to which the present invention is applicable is characterized by comprising:

[0022] The braking assembly is equipped with two or more electronic brakes that limit the operation of the emergency reset assembly. Each electronic brake is configured to alternately turn on and off at regular intervals, such that when one electronic brake is turned on, the remaining electronic brakes are turned off.

[0023] Furthermore, the compact spring return actuator applicable to the present invention is characterized by:

[0024] The elastic body is composed of an S-shaped spiral spring.

[0025] Furthermore, the compact spring return actuator applicable to the present invention is characterized by:

[0026] The deceleration component includes:

[0027] A first differential planetary gear reducer is mounted on the drive shaft; and...

[0028] A second differential planetary gear reducer is mounted on the working shaft and is connected to the first differential planetary gear reducer by gear meshing.

[0029] Compact spring return actuator applicable to the present invention:

[0030] As an actuator that automatically resets the valve to its original position in emergency situations such as power outages, the power transmission between the motor and the elastic element is made independent, reducing the load on the motor. This ensures sufficient torque for opening and closing the valve even with a low-power, small motor, allowing for safe operation. Furthermore, the S-shaped spiral spring reduces the reset impact on the connected gear components, eliminating the need for high force and strength in the gear components and enabling their miniaturization. Therefore, the size of the actuator can be significantly reduced based on the existing torque, achieving miniaturization and weight reduction.

[0031] Because the emergency reset assembly is not directly connected to the driven shaft but to the middle part of the reduction assembly, i.e., the drive shaft, even with a low-power, small motor, the final torque output can be determined based on the reference torque design using the reduction ratio after the emergency reset assembly.

[0032] The problem of electronic brakes malfunctioning in emergency situations can be prevented by preventing the electronic brakes from becoming magnetized.

[0033] The hydraulic limiter can also eliminate the impact of the valve (turbine unit) rotating rapidly due to the emergency reset assembly, thereby achieving a safe stop. Attached Figure Description

[0034] Figure 1a as well as Figure 1b This is a perspective view of the compact spring reset actuator to which the present invention applies.

[0035] Figure 2a as well as Figure 2b This is a perspective view of the main parts of the compact spring return actuator to which the present invention applies.

[0036] Figure 3a , Figure 3b as well as Figure 3c yes Figure 2a The floor plan, front view, and bottom view.

[0037] Figure 4 yes Figure 2a Cross-sectional view of the main part.

[0038] Figure 5a as well as Figure 5b This is a cross-sectional view of the main parts used to illustrate the hydraulic limiter of the present invention.

[0039] Figure 6a as well as Figure 6b This is a cross-sectional view of the main part used to illustrate the nut anti-loosening assembly of the present invention.

[0040] [Symbol Explanation]

[0041] M: Motor

[0042] 10: Drive shaft

[0043] 20: Driven shaft

[0044] 30: Emergency Reset Component

[0045] 40: Braking components

[0046] 50: Manual opening / closing component

[0047] 60: Hydraulic limit switch Detailed Implementation

[0048] This invention can be modified and implemented in various forms, and the implementation examples (aspects) will be described in detail in the text. However, this is not intended to limit the invention to a specific disclosed form, but should be understood to include all modifications, equivalents, and even substitutions contained within the concept and technical scope of this invention.

[0049] In the accompanying drawings, the same reference numerals, especially those with the same tens digit and units digit, or the same tens digit, units digit, and letter, represent components with the same or similar functions. Unless otherwise explicitly stated, the components referred to by the various reference numerals in the accompanying drawings shall be understood as components conforming to the stated standard.

[0050] Furthermore, the constituent elements in the various figures may be exaggerated (later thickened) or reduced (or thinned) in size or thickness for ease of understanding, or simplified in illustration, but this should not be construed as limiting the scope of protection of the present invention.

[0051] The terminology used in this specification is for illustrative purposes only and is not intended to limit the scope of the invention. Unless the context clearly indicates otherwise, singular statements also have plural meanings.

[0052] In this application, terms such as ~ include ~ or ~ constitute ~ are used only to indicate the presence of features, numbers, steps, actions, constituent elements, components or combinations thereof described in the specification, and should not be construed as excluding the possibility of the presence or addition of one or more other features, numbers, steps, actions, constituent elements, components or combinations thereof.

[0053] Unless otherwise defined, all terms used herein, including technical and scientific terms, have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. Terms that are commonly used and are defined in dictionaries should be interpreted as having the meaning consistent with their meaning in the context of the relevant art, and should not be interpreted as having an overly idealized or exaggerated meaning unless explicitly defined in this application.

[0054] The terms such as "first" and "second" used in this specification are merely for distinguishing different constituent elements and are not limited by the manufacturing order. Furthermore, their names may not be consistent in the detailed description and claims of this invention.

[0055] In describing the compact spring return actuator to which the present invention applies, references may be made for ease of explanation. Figure 1a as well as Figure 1b By roughly defining its directional reference, the direction of gravity can be used as the bottom to define its up, down, left, and right sides. In the detailed description of the invention and the claims related to other figures, the direction will also be defined with the aforementioned reference unless otherwise explicitly mentioned.

[0056] The compact spring reset actuator to which the present invention is applied will now be described in detail with reference to the accompanying drawings.

[0057] The present invention is as follows Figures 1a to 5b As shown, a compact spring reset actuator is disclosed that can automatically reset a valve to its original position in emergency situations such as power outages. It generally includes a drive shaft 10 that operates by means of a motor M, a driven shaft 20 that opens and closes a valve (not shown), a deceleration assembly that reduces the rotational force of the motor M or the emergency reset assembly 30, an emergency reset assembly 30 that rotates the valve back to its initial working position, a braking assembly 40 of the emergency reset assembly 30, and a manual opening and closing assembly 50.

[0058] Specifically, the present invention includes:

[0059] The drive shaft 10 receives power from the motor M and rotates;

[0060] Driven shaft 20 rotates by means of drive shaft 10 and opens and closes valve (not shown);

[0061] The speed reduction assembly reduces the rotational force transmitted to the driven shaft 20; and,

[0062] The emergency reset assembly 30 is equipped with an elastomer and a working shaft 321 that converts the elastic force of the elastomer into a rotational force for transmission, and rotates the valve to reset when the power is disconnected.

[0063] The deceleration component includes:

[0064] A first differential planetary gear reducer 11 is mounted on the drive shaft 10; and...

[0065] The second differential planetary gear reducer 34 is mounted on the working shaft 321 and is connected to the first differential planetary gear reducer 11 by gear meshing.

[0066] The speed reduction assembly includes gear portions 111a and 342a, which are formed on the outer peripheral surfaces of the fixed ring gear 111 of the first differential planetary gear reducer 11 and the differential ring gear 342 of the second differential planetary gear reducer 34 and mesh with each other.

[0067] The speed reduction assembly includes a spur gear reduction section R1, which is geared and connected between the rotating shaft M1 of the motor M and the drive shaft 10.

[0068] Furthermore, the present invention includes: a braking assembly 40 equipped with two or more electronic brakes that limit the operation of the emergency reset assembly 30, each electronic brake being configured to alternately turn on / off at regular intervals, such that when one electronic brake is turned on, the remaining electronic brakes are turned off.

[0069] The electronic brake includes a linkage gear 412, which can rotate together with the working shaft 321 in the disengaged state.

[0070] The braking assembly 40 is connected to the connecting gears 412 and 422 of each electronic brake by meshing with each other, and the working shaft 321 is connected to one of the connecting gears 412 of the electronic brake.

[0071] The speed reduction assembly includes a spur gear reduction section R1, which is geared and connected between the rotating shaft M1 of the motor M and the drive shaft 10.

[0072] The elastic body is composed of an S-shaped spiral spring 33.

[0073] The emergency reset component 30 includes:

[0074] The first rotating body 31 is pivotally mounted on one side of the housing 30a; and,

[0075] The second rotating body 32 is axially located on the other side of the housing 30a and is equipped with a working shaft 321 for transmitting rotational power to the valve.

[0076] One end of the S-shaped spiral spring 33 is connected to and wound around the first rotating body 31 to accumulate elastic force, and the other end is connected to the second rotating body 32.

[0077] The working shaft 321 is meshed with the fixed ring gear 111 of the differential planetary gear reducer 11.

[0078] First, the end gear on the input side of the drive shaft 10 is connected to the spur gear reduction section R1 of the reduction assembly, which includes a first differential planetary gear reducer 11 on the input side and a worm shaft section 12 on the output side.

[0079] The first differential planetary gear reducer 11 and the second differential planetary gear reducer 34, which is mounted on the working shaft 321 of the emergency reset assembly 30, together form a differential planetary gear reduction section R2, and the worm shaft section 12 and the turbine section 21 of the driven shaft 20 together form a worm gear reduction section R3.

[0080] The driven shaft 20 is connected to the drive shaft 10 along a perpendicularly intersecting direction, and includes a turbine part 21 meshing with the input side of the worm shaft part 12 and an opening / closing body 22 connected to the output side of the valve.

[0081] At this time, the turbine section 21 is not a circular ring shape formed along the outer periphery of the driven shaft 20, but an arc shape, because most valves are opened and closed by rotating 90 degrees.

[0082] In addition, the reduction assembly includes a spur gear reduction section R1, a differential planetary gear reduction section R2, and a worm gear reduction section R3.

[0083] The spur gear reduction section R1 is formed by multiple spur gears with different diameters meshing in a multi-stage manner between the rotating shaft M1 of the motor M and the drive shaft 10.

[0084] In this way, the spur gear reduction unit R1 can reduce the rotational force of the motor M for the first time and transmit it to the input side of the drive shaft 10.

[0085] The first differential planetary gear reducer 11 and the second differential planetary gear reducer 34 have a sun gear (not shown) connected to the input shaft arranged in the center and planetary gears arranged along the outer periphery of the sun gear, so that the sun gear and the planetary gears mesh with each other. They are composed of fixed ring gears 111 and 341 on the input side that mesh with the outer side of the planetary gears and are arranged in front and behind but do not rotate, and differential ring gears 112 and 342 on the output side that are connected to the output side (i.e., worm shaft 12) of the drive shaft 10 and are rotatable.

[0086] Furthermore, the fixed ring gear 111 of the first differential planetary gear reducer 11 and the differential ring gear 342 of the second differential planetary gear reducer 34 mesh with each other through gear portions 111a and 342a formed on their respective outer peripheral surfaces.

[0087] As described above, the differential planetary gear reducer R2 reduces the rotational force transmitted to the input side and transmits it to the output side. However, thanks to the self-locking function of the differential planetary gear reducer, it does not transmit the rotational force transmitted to the output side to the input side in the opposite way.

[0088] Therefore, regarding the first differential planetary gear reducer 11,

[0089] The rotational force input to the drive shaft 10 will be reduced a second time and transmitted to the driven shaft 20.

[0090] However, the rotational force applied to the valve by the pressure of the fluid and transmitted to the driven shaft 20 will not be transmitted to the spur gear reduction unit R1 connected to the input side of the drive shaft 10, thereby preventing unintended closing action when the valve is open, and also preventing the transmitted reset impact from being transmitted to the spur gear reduction unit R1 and the motor M.

[0091] Furthermore, regarding the second differential planetary gear reducer 34, since it does not receive rotational force from the first differential planetary gear reducer 11, it is not affected by the operation of the motor M or the manual opening / closing assembly 50. Instead, it only performs the first deceleration on the rotational force generated in the emergency reset assembly 30 and transmits it to the first differential planetary gear reducer 11 on the drive shaft 10.

[0092] Therefore, when the rotating shaft M1 of the motor M rotates to one side, the S-shaped spiral spring 33 of the emergency reset assembly 30 will not be compressed, so the load on the motor M will also be reduced, thereby allowing the use of a small motor with a smaller capacity and a small spur gear, thereby reducing the size (volume) of the actuator itself and achieving weight reduction.

[0093] At this time, a differential planetary gear reducer mounted on a separate connecting shaft can be added between the first differential planetary gear reducer 11 and the second differential planetary gear reducer 34 to increase its reduction ratio.

[0094] Furthermore, the worm gear reduction unit R3 reduces the rotational force transmitted to the motor M or emergency reset assembly 30 on the drive shaft 10 for the third time and transmits it to the driven shaft 20, in the same manner as known worm gears.

[0095] That is, in the deceleration assembly of the present invention,

[0096] The rotational force of the motor M will be reduced in three stages through the spur gear reduction unit R1, the first differential planetary gear reducer 11, and the worm gear reduction unit R3, and then transmitted to the driven shaft 20.

[0097] The rotational force (elastic force) of the emergency reset assembly 30 will be reduced in three stages through the second differential planetary gear reducer 34, the first differential planetary gear reducer 11, and the worm gear reducer R3, and then transmitted to the driven shaft 20.

[0098] The rotational force of the manual opening and closing assembly 50 will be reduced in two stages through the first differential planetary gear reducer 11 and the worm gear reducer R3 and then transmitted to the driven shaft 20.

[0099] Furthermore, the emergency reset component 30 is housed within a housing 30a that is separately attached to one side of the housing C.

[0100] The elastic body installed inside the housing 30a is composed of an S-shaped spiral spring 33 that can rotate the valve to reset.

[0101] Specifically, the emergency reset component 30 includes:

[0102] The first rotating body 31 is pivotally mounted on one side of the housing 30a; and,

[0103] The second rotating body 32 is mounted on the other side of the housing 30a and is equipped with a working shaft 321;

[0104] One end of the S-shaped spiral spring 33 is connected to and wound around the first rotating body 31 to accumulate elastic force, and the other end is connected to the second rotating body 32.

[0105] The first rotating body 31 and the second rotating body 32 are in the shape of a disc, and the elastic force is accumulated by winding the S-shaped spiral spring 33 around the first rotating body 31.

[0106] At this time, the first rotating body 31 is simply axially mounted in the outer casing 30a.

[0107] The working shaft 321 protrudes along the axial direction and is connected to the second rotating body 32. The second differential planetary gear reducer 34, which is equipped on the output side of the working shaft 321, is meshed with the first differential planetary gear reducer 11, thereby converting the rotational force of the first rotating body 31, i.e. the elastic force of the S-shaped spiral spring 33, into rotational force and decelerating it to the drive shaft 10.

[0108] Furthermore, the two ends of the S-shaped spiral spring 33 are respectively connected to the first rotating body 31 and the second rotating body 32, and the two ends exert elastic force in opposite directions.

[0109] That is, an elastic force is generated in the first elastic body 31 in the direction of unwinding the S-shaped spiral spring 33, while an elastic force is generated in the second elastic body 32 in the direction of winding the S-shaped spiral spring 33.

[0110] Therefore, after the S-shaped spiral spring 33 is wound around the first rotating body 31, and the second rotating body 32 has stopped rotating by means of the braking assembly 40, if the braking assembly 40 is disengaged due to reasons such as a power outage,

[0111] One end of the S-shaped spiral spring 33 will unwind from the first rotating body 31 by means of elastic force, while the other end of the S-shaped spiral spring 33 will be wound around the second rotating body 32 and drive the working shaft 321 of the second rotating body 32 to rotate.

[0112] The rotational force of the working shaft 321 will be transmitted sequentially to the drive shaft 10 and the driven shaft 20, thereby causing the valve to rotate and reset in the opposite direction to its initial working direction (i.e., the valve will be closed when it is in the open state due to electric drive, and conversely, the valve will be opened when it is in the closed state) and thus achieve opening and closing.

[0113] As described above, the S-type spiral spring 33 differs from conventional helical springs or torsion springs in that the difference between the preload and the pressure during compression is not significant. Therefore, the strength and size of the gear components that operate by means of the elastic force of the S-type spiral spring 33 do not need to be too large. This allows for the use of a small, low-power motor to achieve electric drive, thereby significantly reducing the overall size (volume) of the actuator.

[0114] Furthermore, because the present invention can reduce the rotational force generated in the S-shaped spiral spring 33 through three stages and transmit it to the driven shaft 20 through the reduction assembly, even when using a small motor with low power, the final torque of the driven shaft 20 can be easily designed based on the original reference torque, thereby achieving miniaturization of the actuator.

[0115] Furthermore, the braking assembly 40 is equipped with an electronic brake for limiting the operation of the emergency reset assembly 30.

[0116] In particular, the braking assembly 40 is equipped with two or more electronic brakes for limiting the operation of the emergency reset assembly 30, and each electronic brake is configured to alternately turn on / off at regular intervals.

[0117] The electronic brake can use magnets to restrict the rotation of brake rings 411 and 421 inserted into the shaft of the second rotating body 32.

[0118] When power is supplied, the second rotating body 32 can be fixed by the brake rings 411 and 421 so that it cannot rotate. When the power is disconnected, the restriction on the brake rings 411 and 421 can be released, so that the second rotating body 32 can rotate.

[0119] At this time, multiple electronic brakes can be arranged in multiple rows along the axial direction of the second rotating body 32 on the outer side of the housing 30a, so that each electronic brake restricts the axial portion of the second rotating body 32.

[0120] However, preferably, while one electronic brake is fixing the shaft of the second rotating body 32, the remaining electronic brakes can be configured along the outer circumferential direction to engage them.

[0121] Therefore, the electronic brake includes a linkage gear 412, which can rotate together with the working shaft 321 in the disengaged state.

[0122] The connecting gears 412 and 422 protrude along the outer periphery of the brake rings 411 and 421.

[0123] Furthermore, the braking assembly 40 is connected to the linkage gears 412 and 422 of each electronic brake by meshing with each other, and the working shaft 321 is connected to one of the linkage gears 412 of the electronic brake.

[0124] That is, after using an electronic brake to fix the shaft of the second rotating body 32 as the main electronic brake 41, the remaining electronic brakes can function as auxiliary electronic brakes 42 that are linked and meshed with the main electronic brake 41.

[0125] Therefore, when power is supplied to one of the electronic brakes 41 and 42, the brake rings 411 and 421 of all electronic brakes 41 and 42 can be locked and prevented from rotating by means of the meshing structure of the linkage gears 412 and 422, thereby preventing the emergency reset assembly 30 from operating, that is, preventing the working shaft 321 from rotating.

[0126] By repeatedly switching each electronic brake 41 and 42 on and off periodically with the anti-magnetization limit time as the cycle, the electronic brakes 41 and 42 will not be magnetized when the emergency reset component 30 is not in operation. Therefore, in the event of an emergency, the electronic brakes can be kept in normal operation and the lock on the second rotating body 32 can be released, thereby allowing the valve to be safely reset and rotated by means of the emergency reset component 30.

[0127] In addition, the manual opening and closing assembly 50 includes a shaft 41 that is geared to the drive shaft 10, a manual operation part 52 that rotatably connects the shaft 51, and a clutch control lever 53 that selectively connects the shaft 51 to the manual operation part 52.

[0128] The gear at one end of the shaft 51 will be meshed with the input spur gear of the drive shaft 10.

[0129] The manual operation part 52 is in the form of a handle or lever, and is installed at certain intervals on the same straight line as the shaft 51.

[0130] The clutch control lever 53 is used to connect or disconnect the shaft 51 from the manual operation unit 52, and can employ a known clutch structure.

[0131] In this way, the shaft 51 and the manual operation unit 52 can be prevented from moving together by disengaging the clutch part 531 of the clutch control lever 53 during normal operation, thereby preventing the manual operation unit 52 from rotating together during electric operation.

[0132] Furthermore, when inspecting equipment or in case of an emergency, the operator can use the clutch part 531 of the clutch control lever 53 to connect the shaft 51 with the manual operation part 52. When the shaft 51 is rotated by the manual operation part 52, the rotational force can be transmitted to the driven shaft 20 through the drive shaft 10 and the valve can be manually opened and closed.

[0133] Furthermore, the present invention also includes a hydraulic limiter 60 that eliminates the shock of the turbine section 21 while stopping the rotation of the valve.

[0134] The hydraulic limiter 60 includes:

[0135] The support tube 61 is joined and fixed at a position that is a certain distance away from both ends of the turbine 21;

[0136] A buffer cylinder 62 is inserted and attached to the front end of the support tube 61 in an insertable manner to form a buffer part 621 filled with hydraulic oil.

[0137] A buffer pin 63, which is incorporated into the interior of the support tube, is equipped with a piston portion 631 embedded in the buffer portion 621; and,

[0138] The compression spring 64 is supported by the bottom surface of the piston part 631 and moves forward by providing elastic support to the buffer cylinder 62.

[0139] The buffer cylinder 62 is equipped with a contact portion 622 supported by a flexible material such as rubber and attached to the front end, and the buffer portion 621 is sealed by an O-ring attached to the cap 623 at the rear end, and the buffer portion 621 is filled with hydraulic oil.

[0140] The buffer pin 63 is inserted through the cap 623, and the piston portion 631 divides the buffer portion 621 into front and rear spaces.

[0141] At this time, an orifice structure is formed in the buffer cylinder 62 or the piston part 631 or both, allowing hydraulic oil to move in the space before and after the piston part 631.

[0142] The compression spring 64 supports the buffer cylinder 62, thereby causing it to advance relative to the piston portion 631 and causing the contact portion 622 to protrude outward toward the front end side of the support tube 61.

[0143] In this way, when the driven shaft 20 rotates, one end of the turbine section 21 contacts the contact portion 622 of the buffer cylinder 62 located on the rotation path, thereby subjecting the buffer cylinder 62 to a pressure that is inserted into the support tube 61.

[0144] As described above, when the buffer cylinder 62 is inserted, the piston 631 pushes the hydraulic oil in the buffer section 621, so that the hydraulic oil flows through the orifice structure to the rear end of the piston section 631. At this time, the buffer cylinder 62 can be inserted slowly by means of the rebound pressure of the hydraulic oil, thereby relieving and eliminating the impact applied to the buffer cylinder 62.

[0145] Furthermore, when the external force applied to the buffer cylinder 62 disappears, the buffer cylinder 62 will advance and return to its original position by means of the elastic force of the compression spring 64. At this time, the hydraulic part at the rear end will flow back into and fill the front end space of the piston part 631 by means of the piston part 631.

[0146] As described above, the hydraulic limiter 60 can buffer the impact generated when the valve stops after rapid rotation, especially when it operates via the emergency reset assembly 30, and prevent damage to the actuator components.

[0147] That is, although the motor M or the manual opening / closing assembly 50 can easily control the rotation angle and speed of the valve,

[0148] However, due to the strong elastic force of the S-shaped spiral spring 33, the emergency reset assembly 30 will still allow the driven shaft 20 to rotate relatively quickly even during deceleration.

[0149] At this point, a limiter is needed to stop the rotation of the driven shaft 20. However, conventional limiters often break because they cannot eliminate the impact on the turbine 21 when it rotates rapidly. But the present invention can prevent the component from breaking by introducing a hydraulic limiter 60 with the structure described above.

[0150] Furthermore, the outer shell C is assembled from upper and lower outer shells C1 and C2 via bolts B and nuts N. The nuts N may loosen due to vibrations during operation. This invention can address this by including... Figure 6a as well as Figure 6b The nut anti-loosening component shown provides a more robust fixation to the bolt B, thereby enhancing its bonding strength.

[0151] The nut anti-loosening assembly includes:

[0152] The ratchet portion C31 is formed along the outer periphery of the outer side of the screw hole C3 of the housing C;

[0153] The ratchet lever N1 comprises a binding portion N11 that is elastically supported from the inside of the nut N toward the ratchet portion C31 and enters and exits toward the front side of the nut N in a manner that can be blocked by the ratchet portion C31, and a pushed portion N13 that extends rearward and is connected to the binding portion N11 and is provided with a cam groove N12 that is inclined upward from the inside to the outside on one side; and...

[0154] The pressing rod N2 is composed of a pressing part N21 that is elastically supported from the inside of the nut N towards one of the hexagonal surfaces of the nut N and extends into and out of the hexagonal surface, and a pressing part N23 that extends and connects to the lower part of the pressing part N21, contacts one side of the pushing part N13 along a perpendicularly intersecting direction, and is equipped with a pressing protrusion N22 embedded in the cam groove N12 on the other side.

[0155] In the ratchet portion C31, ratchet teeth are arranged in a circular pattern along the outer periphery of the screw hole C3 and protrude to the rear side, forming an inclined surface that is inclined upward in the tightening direction of the nut N.

[0156] The ratchet N1 is embedded in the slot formed on the front of the nut N, and the rear end of the pushed part N13 is supported by the first spring N3, so that the binding part N11 protrudes towards the front side of the nut N.

[0157] The pressing rod N2 is embedded in one of the slots formed in the hexagonal surface of the nut N, and the lower end of the pressing part N23 is supported by the second spring N4, so that the pressed part N21 protrudes into the hexagonal surface of the nut N, and the pressed part N21 is formed in a hemispherical shape.

[0158] Therefore, when the nut N is tightened to the screw portion 152 so that the binding portion N11 contacts the ratchet portion C31, the ratchet bar N1 will move back and forth, and after the binding portion N11 is completely tightened by passing through the ratchet portion C31, the binding portion N11 is blocked by one of the ratchet teeth of the ratchet portion C31, thereby preventing the nut N from loosening due to vibration or the like.

[0159] Furthermore, when the wrench is aligned and inserted into the hexagonal surface where the pressing rod N2 is formed in order to loosen the nut N, the pressed part N21 will be pressed down and the pressing rod N2 will be inserted. At this time, as the pressing part N23 descends vertically, the pressing protrusion N22 will also descend, thereby pushing the inclined surface of the cam groove N12 and pushing the pushed part N13 to the rear side. As a result, the ratchet rod N1 will retract and the binding part N11 will be introduced into the nut N and disengage from the ratchet part C31, so that the nut N can be easily loosened with the wrench.

[0160] In the above description of the present invention, the description mainly focuses on the compact spring return actuator with reference to the accompanying drawings. However, those skilled in the art can make various modifications, alterations, and substitutions to the present invention, and such modifications, alterations, and substitutions should be interpreted as being included within the scope of protection of the present invention.

Claims

1. A compact spring-reset actuator, characterized in that, include: The drive shaft receives power from the motor and rotates. The driven shaft rotates by means of the drive shaft and opens and closes the valve; A speed reduction assembly for reducing the rotational force transmitted to the driven shaft, including a differential planetary gear reducer mounted on the drive shaft; An emergency reset assembly is equipped with an elastomer and a working shaft that converts the elastic force of the elastomer into a rotational force for transmission and engagement with the differential planetary gear reducer, thereby rotating and resetting the valve when the power is disconnected. as well as The braking assembly is equipped with two or more electronic brakes that limit the operation of the emergency reset assembly. Each electronic brake is configured to alternately turn on and off at regular intervals, such that when one electronic brake is turned on, the remaining electronic brakes are turned off.

2. The compact spring return actuator according to claim 1, characterized in that: The elastic body is composed of an S-shaped spiral spring.

3. The compact spring return actuator according to claim 1, characterized in that: The deceleration component includes: A first differential planetary gear reducer is mounted on the drive shaft; and... A second differential planetary gear reducer is mounted on the working shaft and is connected to the first differential planetary gear reducer by gear meshing.

Images