WO2018216526A1 - Actionneur de soupape électrique et dispositif de type soupape - Google Patents

Actionneur de soupape électrique et dispositif de type soupape Download PDF

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Publication number
WO2018216526A1
WO2018216526A1 PCT/JP2018/018537 JP2018018537W WO2018216526A1 WO 2018216526 A1 WO2018216526 A1 WO 2018216526A1 JP 2018018537 W JP2018018537 W JP 2018018537W WO 2018216526 A1 WO2018216526 A1 WO 2018216526A1
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WO
WIPO (PCT)
Prior art keywords
valve
shaft
conversion mechanism
valve shaft
motion conversion
Prior art date
Application number
PCT/JP2018/018537
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English (en)
Japanese (ja)
Inventor
卓志 松任
山下　洋平
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2018216526A1 publication Critical patent/WO2018216526A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/45—Sensors specially adapted for EGR systems
    • F02M26/48—EGR valve position sensors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/53—Systems for actuating EGR valves using electric actuators, e.g. solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/66—Lift valves, e.g. poppet valves
    • F02M26/67—Pintles; Spindles; Springs; Bearings; Sealings; Connections to actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/70—Flap valves; Rotary valves; Sliding valves; Resilient valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/06—Means for converting reciprocating motion into rotary motion or vice versa

Definitions

  • the present invention relates to an electric actuator for a valve and a valve device.
  • EGR devices exhaust gas recirculation devices
  • NOx nitrogen oxides
  • a part of the exhaust gas exhausted is recirculated to the intake side as recirculated exhaust gas (hereinafter also referred to as EGR gas).
  • EGR gas recirculated exhaust gas
  • a valve hereinafter referred to as an EGR valve
  • this opening / closing mechanism uses a feed screw device and does not use a speed reducer, a decrease in opening / closing accuracy due to backlash can be avoided.
  • this opening / closing mechanism has a structure in which a female screw member screwed into a screw shaft is press-fitted into the inner periphery of the hollow rod, and a link mechanism is connected to the tip of the hollow rod.
  • a link mechanism and a valve shaft are arranged in the screw shaft and in the region on the tip side of the hollow rod (region opposite to the motor coupling side), and the size of the drive mechanism is the direction in which the screw shaft extends. It is getting bigger.
  • an object of the present invention is to provide an electric actuator for a valve and a valve device that are compact and have high valve opening / closing accuracy.
  • the present invention includes a motor unit that generates a rotational driving force and a shaft-shaped rotating member that is rotationally driven by the motor unit, and the rotational motion of the rotating member is linearly moved.
  • a first motion conversion mechanism unit that converts to a valve shaft, and a second motion conversion mechanism unit that converts the linear motion output from the first motion conversion mechanism unit into a rotational motion of the valve shaft.
  • the rotating member is rotatably supported by a pair of bearings, and the valve shaft is disposed between the pair of bearings.
  • the length of the electric actuator for the valve in the extending direction of the rotating member is shortened to achieve compactness.
  • the load load to a rotating member is performed between a pair of bearings spaced apart in the direction where a rotating member extends among rotating members.
  • the deformation of the rotating member is less likely to occur compared to the configuration described in Patent Document 2 in which a load is applied to the cantilevered region. Therefore, it is possible to improve the opening / closing accuracy when the valve is opened / closed.
  • the first motion conversion mechanism portion and the second motion conversion mechanism portion constitute a link mechanism, and the movement trajectory of each link of the link mechanism is arranged between the pair of bearings. preferable. With this configuration, the same operational effects as described above can be obtained.
  • the angular velocity of the valve shaft can be expressed by a relatively simple expression using a trigonometric ratio, where the moving speed V of the slider on the driving side is a constant (constant). Therefore, it is easy to design such that the angular velocity of the valve shaft near the fully closed state of the valve is reduced, while the angular velocity of the valve shaft near the intermediate state is increased.
  • the rotational speed of the motor unit is changed if a difference is made in the angular velocity according to the open / close state of the valve. Inevitably, motor control becomes complicated.
  • the screw shaft is used as the rotating member of the first motion conversion mechanism, and this screw shaft is arranged in parallel with the pipe extending direction in the vicinity of the valve shaft, thereby effectively utilizing the excess space around the pipe.
  • An electric actuator for a valve can be provided.
  • the valve opening / closing accuracy near the fully closed state of the valve can be improved.
  • the opening / closing accuracy of the valve can be increased in the vicinity of a fully closed state that is important for the function of the EGR device.
  • the valve electric actuator includes an input unit that is driven by the first motion conversion mechanism unit to perform a linear motion, an output unit that performs a rotational motion around the valve shaft together with the valve shaft, and an input unit and an output unit. It is preferable to include a connecting portion that is provided on any one of them, engages with the other, and allows the input portion and the output portion to be connected to each other so as to allow sliding movement relative to the other. In such a configuration, if each link is designed so that the turning radius of the connecting portion is maximized when the valve is fully closed, the angular velocity of the valve shaft near the fully closed state is reduced and the opening and closing accuracy of the valve is increased. Can do.
  • a housing for accommodating the valve shaft is provided, and an elastic member that biases the valve shaft in a direction in which the valve is fully closed is disposed between the housing and the output portion of the second motion conversion mechanism, Even when an abnormality occurs in one conversion mechanism, the valve can be automatically shifted to the fully closed state, and the fail-safe function is enhanced.
  • the degree of opening and closing of the valve is detected. Can be controlled.
  • a valve device can be constituted by the electric actuator described above and a valve provided on the valve shaft.
  • an electric actuator for a valve and a valve device that are compact and have high valve opening / closing accuracy.
  • FIG. 2 is a cross-sectional view taken along line XX of FIG. It is a perspective view which expands and shows a valve shaft.
  • FIG. 2 is a cross-sectional view taken along line YY in FIG.
  • FIG. 6 is a sectional view taken along line XX when the valve is in a fully closed state.
  • FIG. 6 is a sectional view taken along line XX when the valve is in an intermediate state.
  • FIG. 6 is a sectional view taken along line XX when the valve is fully opened.
  • FIG. 1 is a perspective view of an electric actuator for a valve according to an embodiment of the present invention
  • FIG. 2 is a sectional view taken along line XX of FIG.
  • FIG. 3 is an enlarged perspective view showing the valve shaft
  • FIG. 4 is a cross-sectional view taken along line YY of FIG.
  • the XX line coincides with a center line O1 of a screw shaft 31 described later
  • the YY line coincides with a center line O2 of a valve shaft 4 described later.
  • the electric actuator 1 for valves in this embodiment is used for, for example, an EGR device of a car. As shown in FIGS. 1 and 2, the electric actuator 1 for a valve receives a supply of electric power to generate a rotational driving force, and converts a rotational motion obtained by the motor portion 2 into a linear motion.
  • the motor unit 2 is composed of, for example, a radial gap type motor (for example, a three-phase brushless motor) provided with a stator and a rotor.
  • the output shaft 21 of the motor unit 2 has a solid shape, and both axial ends thereof are a bearing 23 fixed to the inner peripheral surface of the motor housing 22 and a bearing (not shown) disposed inside the motor. It is supported rotatably.
  • Reference numeral 25 denotes a terminal portion that accommodates a bus bar, a substrate, etc. (not shown).
  • the first motion conversion mechanism unit 3 of the present embodiment is composed of a ball screw device.
  • the ball screw device 3 includes a screw shaft 31 as a shaft-like rotating member, and a nut member 32 fitted to the outer periphery of the screw shaft 31 via a plurality of balls.
  • the screw shaft 31 is arranged coaxially with the output shaft 21 of the motor unit 2, and its base end (end on the motor unit 3 side) is directly connected to the output shaft 21 of the motor unit 2 without interposing a reduction gear or the like.
  • Ends on both axial sides of the screw shaft 31 are rotatably supported with respect to the housing (valve housing 42) by bearings 33 and 34 such as rolling bearings, respectively.
  • a plurality of balls are incorporated between the spiral groove formed on the outer peripheral surface of the screw shaft and the spiral groove formed on the inner peripheral surface of the nut member 32.
  • the nut member 32 By rotating the screw shaft 31, the nut member 32 performs a linear motion along the direction in which the screw shaft 31 extends, and the ball circulates between both spiral grooves.
  • the circulation of the ball can be performed by providing a top (not shown) as a circulation member on the nut member 32, for example.
  • the second motion conversion mechanism unit 5 includes an input unit 51, an output unit 52, and a connection unit 53 that connects the input unit 51 and the output unit 52.
  • the input part 51 is a cylindrical member, and is fixed to the outer peripheral surface of the nut member 32 by means such as press fitting. Therefore, the input part 51 extends the screw shaft 31 in conjunction with the linear motion of the nut member 32. Make a linear motion in the direction.
  • the input portion 51 is formed with a through hole that is separated from the center line O1 of the screw shaft 31 and extends in a direction orthogonal to the screw shaft 31.
  • a pin having a cylindrical outer peripheral surface as the connecting portion 53 is formed in the through hole. Is press-fitted and fixed. One end of the pin 53 protrudes toward the output unit 52 from the end surface of the input unit 51 (see FIG. 4).
  • the output portion 52 of the present embodiment is formed integrally with the valve shaft 4 at one end portion (end portion on the screw shaft 31 side) of the valve shaft 4 and extends in the radial direction of the valve shaft 4. It has a flat form.
  • a groove portion 52a is formed in the output portion 52 along the radial direction of the valve shaft 4, and a pin 53 is fitted in the groove portion 52a to allow sliding movement in the extending direction of the groove portion 52a (FIG. 5A).
  • FIG. 5C In the present embodiment, one end of the groove part 52a is opened at the tip of the output part 52, but it may be closed without opening one end of the groove part 52a.
  • a locking portion 52 b for locking an end portion 44 b of a torsion coil spring 44 described later is provided at the tip of the output portion 52.
  • the output portion 52 and the valve shaft 4 may be separate parts, and the output portion 52 may be fixed to the valve shaft 4 by means such as press fitting. .
  • a slit 4b is formed in the main body of the valve shaft 4 along the direction in which the valve shaft 4 extends.
  • a disc-shaped valve 41 (butterfly valve) is inserted into the slit 4b.
  • the valve 41 is fixed to the valve shaft 4 by screwing a screw or the like into a screw hole 4 c provided in the main body of the valve shaft 4.
  • the valve shaft 4 is rotatably supported by a bearing 43 fixed to the valve housing 42.
  • a bearing 43 in this embodiment, for example, a case where two rolling bearings 43 are arranged in a state where the inner rings and the outer rings are in contact with each other is illustrated.
  • Each outer ring of the rolling bearing 43 is provided with a seal member 45 and a retaining ring 46 attached to the valve housing 42, and each inner ring of the rolling bearings 42 and 43 is provided with a shoulder 4 a of the valve shaft 4 and a retaining ring 47 attached to the valve shaft 4.
  • a return spring 44 is disposed as an elastic member on the outer periphery of the rolling bearings 42 and 43.
  • the torsion coil spring 44 is used as a return spring is illustrated.
  • one end 44a of the torsion coil spring 44 is attached to the valve housing 42, and the other end 44b is locked to a locking portion 52b provided at the tip of the output portion 52 (see FIG. 5A).
  • the torsion coil spring 44 constantly biases the valve shaft 4 in the direction in which the valve 41 is fully closed (counterclockwise in FIG. 5A).
  • valve 41 When the valve 41 is in the fully closed state, the valve 41 receives a rotational moment due to the pressure of the exhaust gas flowing through the piping, but is twisted so that the valve 41 is maintained in the fully closed state against the pressure of the exhaust gas.
  • the elastic force of the coil spring 44 is set.
  • FIG. 6 is a plan view of the valve device.
  • the valve electric actuator 1 and the valve 41 are formed by covering an opening formed between the motor housing 22 and the valve housing 42 with a valve cover 60. Is completed.
  • the motor housing 22, the valve housing 42 and the valve cover 60 function as a housing for the valve electric actuator 1 as a whole.
  • the division mode and the number of divisions of the housing are not limited to the above example, and can be arbitrarily adopted.
  • the completed valve device is disposed in the engine room of the automobile, and the exhaust passage pipe 49 (shown by a two-dot chain line) is provided at both end openings 42 a (see FIG. 1) of the valve housing 42. Is attached.
  • the valve electric actuator 1 is attached so that the center line O1 (XX line in FIG. 6) of the screw shaft 31 is parallel to the extending direction of the pipe 49 in the vicinity of the valve shaft 4.
  • the center line O2 (YY line in FIG. 6) of the valve shaft 4 has a shape extending in a direction orthogonal to the extending direction of the pipe 49.
  • FIGS. 5A to 5C are illustrations in which the motor unit 2 and the first motion conversion mechanism unit 3 are not shown in the cross-sectional view shown in FIG.
  • FIG. 5A shows a fully closed state of the valve 41 (see FIG. 1).
  • the connecting portion 53 of the second motion conversion mechanism 5 is located at the outer diameter end of the groove portion 52a, and the distance (rotation radius) from the center O2 of the valve shaft 4 is maximum.
  • the motor unit 2 is driven in the forward direction
  • the screw shaft 31 rotates and the nut member 32 and the input unit 51 are in the direction of the screw shaft 31 and away from the motor unit 2 (left direction in FIG. 2).
  • the output portion 52 engaged with the connecting portion 53 in the rotation direction rotates in the clockwise direction (forward rotation) in FIG. 5A, and this rotation is transmitted to the valve shaft 4, thereby opening the valve 41. start.
  • the connecting portion 53 When the output portion 52 is further rotated in the forward direction, as shown in FIG. 5B, the connecting portion 53 reaches the inner diameter end of the groove portion 52a, the rotation radius thereof is minimized (intermediate state), and then the connecting portion 53 is connected to the valve shaft. 4 reversely moves toward the outer diameter direction.
  • the valve 41 shown in FIG. 5C is in a fully opened state (a state rotated by 90 ° from the fully closed state). In this fully opened state, the connecting portion 53 is in the groove 52a as in the fully closed state. Located at the outer diameter end, the turning radius is maximum.
  • the motor unit 2 When the motor unit 2 is driven in the reverse direction, the operation opposite to the above operation is performed, the output unit 52 rotates counterclockwise (reverse rotation), and the valve 41 is closed. Depending on the driving state of the vehicle and the like, the motor unit 2 is driven forward / reversely to control the opening / closing of the valve 41 so that optimum exhaust gas recirculation is performed.
  • the elastic force is accumulated in the torsion coil spring 44 as described above.
  • the valve 41 is automatically switched to the fully closed state by this elastic force.
  • the torsion coil spring 44 basically functions as a fail safe when the motor is abnormal. Therefore, the valve 41 is normally opened and closed by forward and reverse driving of the motor unit 2. Note that when the transition from the fully open state to the fully closed state is performed, the elastic force accumulated in the torsion coil spring 44 is superimposed on the driving force of the motor unit. Thus, the power consumption of the motor unit 2 is reduced.
  • a sensing device for detecting the degree of valve opening / closing inside the valve electric actuator 1.
  • a stroke sensor 61 is attached to the inner surface of the valve cover 60, and a magnet 62 is attached to the input unit 51 of the second motion conversion mechanism 5 so as to face this. It is possible to wear it. If the stroke sensor 61 is used in this manner, the position of the input portion 51 in the direction of the screw shaft 31 can be detected, and the open / closed state of the valve 41 can be recognized from the detected value.
  • the configuration of the sensing device is arbitrary as long as the degree of opening and closing of the valve 41 can be detected.
  • the output unit 52 using a rotation angle sensor. It is also possible to directly detect the rotation phase. Further, the rotational phase of the motor unit 2 and the screw shaft 31 may be detected, or the movement amount of the nut member 32 may be detected.
  • the sensing device is configured to open and close the valve 41 from any movement (linear movement or rotational movement, or both) of the first movement conversion mechanism section 3, the second conversion mechanism section 5, or the valve shaft 4. It is set as the structure which detects.
  • the valve shaft 4 is disposed between a pair of bearings 33 and 34 that support the screw shaft 31 as shown in FIGS. Further, the movement trajectories of the input portion 51, the output portion 52, and the nut member 32 accompanying the opening and closing of the valve 41 are all in the region between the pair of bearings 33 and 34. Therefore, the length in the direction of the screw shaft 31 of the valve electric actuator 1 can be shortened as compared with the configuration in which the valve shaft and the link mechanism are arranged in the region closer to the screw shaft tip side than the screw shaft as in Patent Document 2. The area where the exhaust gas recirculation flow path can be installed in the engine room is limited.
  • the valve device is installed in the engine room even if the thickness in the direction of the valve shaft 4 slightly increases. It becomes easy.
  • the load applied to the screw shaft 31 is performed in a region between the pair of bearings 33 and 34 in the screw shaft 31. Since the screw shaft 31 is supported at both ends by the bearings 33 and 34 in this region, the deformation of the screw shaft 31 is less than that of the configuration of Patent Document 2 in which a load is applied to the cantilevered region of the hollow rod. It becomes difficult to occur. Therefore, it is possible to improve the opening / closing accuracy and stability when the valve is opened / closed.
  • the torsion coil spring 44 as a return spring is disposed between the housing (valve housing 42) that accommodates the valve shaft 4 and the output portion 52. That is, the torsion coil spring 44 is disposed downstream of the ball screw device 3 in the motor driving force transmission path. Therefore, even if some abnormality occurs in the ball screw device 3, the valve 41 can be automatically returned to the fully closed state, and the fail-safe function can be further improved.
  • the EGR device due to the characteristics of the EGR device, it is necessary to control the opening / closing amount of the valve 41 more severely in the vicinity of the fully closed state than in the intermediate state of the valve 41 (the state of FIG. 5B). This is because the amount of recirculated EGR gas is generally small.
  • the rotation radius of the connecting portion 53 is maximized when the valve is fully closed (see FIG. 5A). In this state, even if the sliding speed of the input portion 51 is constant, FIG. The angular speed of the output unit 52, that is, the opening / closing speed of the valve 41 is minimized compared to the intermediate state shown in FIG. Therefore, the valve 41 can be accurately controlled in the vicinity of the fully closed state, and the valve opening / closing characteristics required for the EGR device are met.
  • FIG. 7A shows a simplified link mechanism including the first motion conversion mechanism 3 and the second motion conversion mechanism 5 described above.
  • the 1st motion conversion mechanism 3 and the 2nd motion conversion mechanism 5 comprise the link mechanism which has two sliders S1 and S2.
  • the first slider S ⁇ b> 1 is configured by the nut member 32 (or the input unit 51)
  • the second slider S ⁇ b> 2 is configured by the connecting unit 53.
  • the link mechanism has two sliders as described above
  • the angular velocity of the valve shaft 4 is a comparison using a trigonometric ratio with the moving velocity V of the first slider S1 as a constant (constant). Can be expressed by a simple formula.
  • the link mechanism described in Patent Document 2 is a so-called reciprocating slider crank mechanism in which only one of the four links 81 to 84 is a slider S3 (female screw member 82) as shown in FIG. 7B.
  • the equation for obtaining the angular velocity of the valve shaft (angular velocity of the link 84) is complicated, and even if simplified, only an approximate equation can be obtained. Therefore, a design for reducing the angular velocity of the valve shaft 4 near the fully closed state while increasing the angular velocity of the valve shaft 4 in the intermediate state cannot be easily realized.
  • the opening / closing accuracy of the valve 41 near the fully closed state is inferior.
  • the EGR device is illustrated as an application of the electric actuator for the valve.
  • the electric actuator for the valve according to the present invention is not limited to the EGR device, but can be used to open and close valves mounted on other in-vehicle devices and industrial devices.
  • the butterfly valve is exemplified as a valve that is opened and closed by the electric actuator for the valve, but the applicable valve type is not limited to the butterfly valve, as long as the valve opening and closing amount is controlled by forward and reverse rotation of the valve shaft,
  • the electric actuator for valves of the present invention can be used for other valve devices (for example, ball valves).
  • Second motion conversion mechanism 22 Housing (motor housing) 31 Rotating member (screw shaft) 32 Nut member 33 Bearing (Rolling bearing) 34 Bearing (Rolling bearing) 41 Valve 42 Housing (Valve Housing) 44 Elastic member (screw recoil spring) 49 Piping 51 Input Portion 52 Output Portion 53 Connecting Portion O1 Screw Shaft Centerline O2 Valve Shaft Centerline S1 First Slider S2 Second Slider

Abstract

La présente invention concerne un actionneur de soupape électrique qui permet d'ouvrir et de fermer une soupape avec une précision élevée avec une structure compacte. Un actionneur de soupape électrique 1 comprend : un moteur 2 qui reçoit une alimentation en énergie électrique et génère une force d'entraînement rotative ; un dispositif de type vis à billes 3 ; un arbre de soupape 4 ; et un mécanisme de conversion de mouvement 5 qui convertit le mouvement linéaire d'un élément écrou 32 du dispositif de type vis à billes 3 en un mouvement de rotation de l'arbre de soupape 4. Dans cet actionneur de soupape électrique 1, un arbre de vis 31 du dispositif de type vis à billes 3 est supporté rotatif par une paire de paliers 33, 34, et l'arbre de soupape 4 est disposé entre les paliers 33, 34.
PCT/JP2018/018537 2017-05-23 2018-05-14 Actionneur de soupape électrique et dispositif de type soupape WO2018216526A1 (fr)

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JP2017-101623 2017-05-23
JP2017101623A JP2018197566A (ja) 2017-05-23 2017-05-23 バルブ用電動アクチュエータおよびバルブ装置

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Cited By (2)

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Publication number Priority date Publication date Assignee Title
EP4008940A1 (fr) * 2020-12-01 2022-06-08 NTF Korfhage Maschinenbau GmbH Entraînement de soupape de charge lourde pourvu de servomoteur
US11933412B2 (en) 2021-07-16 2024-03-19 Engineered Controls International, Llc Actuating assembly for an internal valve

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JP7393601B2 (ja) 2018-10-19 2023-12-07 Ａｇｃ株式会社 イオン交換膜、レドックスフロー電池

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Publication number Priority date Publication date Assignee Title
JP2521278B2 (ja) * 1986-05-06 1996-08-07 フリツツ ミユラ− 遮断弁等の開閉装置
JP2017009032A (ja) * 2015-06-22 2017-01-12 株式会社三五 バルブ装置

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Publication number Priority date Publication date Assignee Title
JP2521278B2 (ja) * 1986-05-06 1996-08-07 フリツツ ミユラ− 遮断弁等の開閉装置
JP2017009032A (ja) * 2015-06-22 2017-01-12 株式会社三五 バルブ装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4008940A1 (fr) * 2020-12-01 2022-06-08 NTF Korfhage Maschinenbau GmbH Entraînement de soupape de charge lourde pourvu de servomoteur
US11933412B2 (en) 2021-07-16 2024-03-19 Engineered Controls International, Llc Actuating assembly for an internal valve

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