WO2016002599A1 - 二重偏心弁 - Google Patents
二重偏心弁 Download PDFInfo
- Publication number
- WO2016002599A1 WO2016002599A1 PCT/JP2015/068197 JP2015068197W WO2016002599A1 WO 2016002599 A1 WO2016002599 A1 WO 2016002599A1 JP 2015068197 W JP2015068197 W JP 2015068197W WO 2016002599 A1 WO2016002599 A1 WO 2016002599A1
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- WIPO (PCT)
- Prior art keywords
- valve
- force
- valve body
- rotating shaft
- double eccentric
- Prior art date
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- 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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
- F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
- F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
- F16K1/221—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves specially adapted operating means therefor
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- 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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
- F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
- F16K1/20—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member
- F16K1/2028—Details of bearings for the axis of rotation
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- 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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
- F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
- F16K1/20—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member
- F16K1/2007—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member specially adapted operating means therefor
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- 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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/24—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with valve members that, on opening of the valve, are initially lifted from the seat and next are turned around an axis parallel to the seat
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- 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
- F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
- F16K31/043—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
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- 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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
- F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
- F16K1/20—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member
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- 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
- F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
Definitions
- the present invention relates to a double eccentric valve in which the center of rotation (rotating shaft) of the valve body is arranged eccentrically from the center of the valve hole of the valve seat, and the sealing surface of the valve body is arranged eccentrically from the rotating shaft.
- Patent Document 1 in the exhaust gas recirculation device, when the rotary solenoid is de-energized, the valve body of the butterfly valve opens and stops by a predetermined opening from the fully closed position, so that the valve seat and the valve body by deposit are stopped. A technique for preventing sticking is disclosed.
- Patent Document 1 stops the butterfly valve at a position in the middle of the rotation range of the butterfly valve. Therefore, if the gap between the valve seat and the valve body is reduced to reduce the amount of leakage. There is a possibility that the valve seat and the valve body cannot be stably prevented from sticking due to galling between the valve seat and the valve body.
- the present invention has been made to solve the above-described problems, and an object thereof is to provide a double eccentric valve that can stably prevent the valve seat and the valve body from sticking to each other.
- a valve seat including a valve hole and a seat surface formed at an edge of the valve hole, and a seal surface corresponding to the seat surface are formed on the outer periphery.
- a rotary shaft that is provided integrally with the valve body and rotates the valve body, and a central axis of the rotary shaft extends in parallel with a radial direction of the valve body and the valve hole.
- a direction in which the central axis of the valve body extends from the center axis of the rotary shaft and the seal surface is eccentric from the center of the valve hole in the radial direction of the valve hole.
- a driving mechanism for generating a driving force for rotating the rotating shaft in the valve opening direction, and a driving force receiving portion that is provided integrally with the rotating shaft and receives the driving force And between the valve body and the driving force receiving portion in the central axis direction of the rotating shaft
- a bearing that supports the rotating shaft and a return spring that generates a return spring force that rotates the rotating shaft in a valve closing direction, and the return spring force is not driven when the drive mechanism is not driven.
- a force acting in a direction perpendicular to the central axis of the bearing, and the rotary shaft is tilted with the bearing as a fulcrum to remove the valve element from the valve seat.
- a counter-valve seat direction urging force that urges away is generated.
- the double eccentric valve when the double eccentric valve is closed when the engine is stopped and the drive mechanism is not driven, a minute gap is generated between the valve seat and the valve element. For this reason, even if deposits adhere to the valve seat and / or the valve body, the valve seat and the valve body are prevented from sticking to each other. Further, sticking between the valve seat and the valve body due to freezing is also prevented. Therefore, the opening / closing operation of the double eccentric valve is stabilized. In addition, since the valve body is moved away from the valve seat by the urging force in the counter valve seat direction, even if a foreign object is caught between the valve seat and the valve body during the valve closing operation, the foreign object will fall off. Thus, no galling or the like occurs between the valve seat and the valve body. Therefore, sticking of the valve seat and the valve body is prevented stably.
- a force generated due to the driving force when the driving mechanism is driven and a force acting in a direction perpendicular to the central axis of the bearing the bearing being It is preferable to generate a valve seat direction biasing force that tilts the rotating shaft as a fulcrum and biases the valve body in a direction toward the valve seat.
- the opening area (gap between the valve seat and the valve body) at the initial stage of valve opening is reduced. Therefore, the flow rate at the time of low opening of the valve body can be reduced. Therefore, the accuracy of the flow rate control when the valve body is low is improved.
- valve body is seated on the valve seat by the urging force in the valve seat direction.
- the opening area at the initial stage of valve opening is further reduced. Therefore, the flow rate at the time of low opening of the valve body can be further reduced. Therefore, the accuracy of the flow control when the valve body is at a low opening degree is further improved.
- the opening degree of the valve body is controlled using the opening degree of the valve body when a fluid flows at a predetermined flow rate as a reference position.
- the opening degree of the valve body is controlled using the opening degree of the valve body when the valve is closed as a reference position.
- a drive transmission unit that is disposed between the driving mechanism and the driving force receiving unit and transmits the driving force from the driving mechanism to the driving force receiving unit.
- the drive force received from the drive mechanism by the drive transmission unit can be increased and transmitted, so that the drive force generated by the drive mechanism can be reduced. Therefore, the drive mechanism can be reduced in size.
- FIG. 6 is a cross-sectional view taken along line AA in FIG. 5.
- FIG. 3 is a cross-sectional view taken along the line BB in FIG. FIG.
- FIG. 2 is a cross-sectional view taken along the line CC of FIG. It is a front view which shows the state which removed the end frame from the valve housing.
- FIG. 5 is an enlarged view (partially sectional view) of the periphery of a main gear, a return spring, and an intermediate gear when the motor is not driven. It is the schematic diagram which showed the force which acts on a main gear at the time of the non-drive of a motor, and is the figure seen from the main gear side of the center axis direction of a rotating shaft.
- FIG. 12 is a diagram corresponding to the DD sectional view of FIG. 11, and is a schematic diagram illustrating a valve seat, a valve body, a rotating shaft, a bearing, and a main gear.
- FIG. 14 is a diagram corresponding to the EE cross-sectional view of FIG. 13, and is a schematic diagram illustrating a valve seat, a valve body, a rotating shaft, a bearing, and a main gear. It is a figure corresponding to FIG. 14, Comprising: It is a figure showing the time of making a motor drive force larger than the time of FIG.
- FIG. 4 is an enlarged view (partially sectional view) of the periphery of a main gear, a return spring, and an intermediate gear when the valve opening is ⁇ during driving of the motor.
- FIG. 16 is a diagram corresponding to FIG. 15, showing a case where the motor driving force is made larger than that in FIG. 15.
- FIG. 7 is an enlarged view (partially sectional view) of the periphery of the main gear, the return spring, and the intermediate gear when the valve opening is ⁇ when the motor is driven. It is a relationship figure of a valve opening degree and opening area. In a modification, it is a mimetic diagram showing a valve seat, a valve element, a rotating shaft, a bearing, and a main gear. In a modification, it is a related figure of valve opening and an opening area.
- the EGR valve 1 includes a valve portion 2 composed of a double eccentric valve and a drive mechanism portion 3.
- the valve section 2 includes a pipe section 12 (see FIG. 7) having a flow path 11 through which EGR gas as a fluid flows. Inside the flow path 11, a valve seat 13, a valve body 14, and a rotating shaft 15 (see FIG. 7 and FIG. 8) are arranged. A driving force (rotational force) is transmitted from the drive mechanism unit 3 to the rotary shaft 15.
- the drive mechanism unit 3 includes a motor 32 and a speed reduction mechanism 33 (see FIGS. 7 and 8).
- a step portion 10 is formed in the flow path 11, and a valve seat 13 is incorporated in the step portion 10.
- the valve seat 13 has an annular shape and has a valve hole 16 in the center.
- An annular seat surface 17 is formed at the edge of the valve hole 16.
- the valve body 14 has a disc shape, and an annular seal surface 18 corresponding to the seat surface 17 is formed on the outer periphery thereof.
- the valve body 14 is provided integrally with the rotary shaft 15 and rotates integrally with the rotary shaft 15. 3 and 4, the flow path 11 below the valve body 14 indicates the upstream side of the EGR gas flow, and the flow path 11 above the valve seat 13 indicates the downstream side of the EGR gas flow. That is, in the flow path 11, the valve body 14 is disposed upstream of the valve seat 13 in the flow of EGR gas.
- the central axis Ls of the rotary shaft 15 extends parallel to the radial direction of the valve body 14 and the valve hole 16, and is eccentric from the center P1 of the valve hole 16 to the radial direction of the valve hole 16.
- the seal surface 18 of the valve body 14 is arranged eccentrically in the direction in which the central axis Lv of the valve body 14 extends from the central axis Ls of the rotary shaft 15. Further, by rotating the valve body 14 about the central axis Ls of the rotary shaft 15, a fully closed position where the seal surface 18 of the valve body 14 is in surface contact with the seat surface 17 of the valve seat 13 (see FIG. 3). And a fully open position (see FIG. 4) farthest away from the seat surface 17.
- the valve housing 35 made of metal or synthetic resin includes a flow path 11 and a pipe portion 12.
- the end frame 36 made of metal or synthetic resin closes the open end of the valve housing 35.
- the valve body 14 and the rotating shaft 15 are provided in the valve housing 35.
- the rotating shaft 15 includes a pin 15a that protrudes from the tip.
- the pin 15a is provided at one end (on the valve body 14 side) of the rotation shaft 15 in the direction of the central axis Ls (see FIG. 8).
- a base end portion 15b is provided at the other end portion (on the main gear 41 side) of the rotation shaft 15 in the direction of the central axis Ls.
- the rotary shaft 15 is arranged such that the distal end side with the pin 15 a is a free end, and the distal end portion is inserted into the flow path 11 of the tube portion 12.
- the rotating shaft 15 is cantilevered so as to be rotatable with respect to the valve housing 35 via a first bearing 37 and a second bearing 38 which are two bearings arranged apart from each other. Both the first bearing 37 and the second bearing 38 are ball bearings.
- the 1st bearing 37 and the 2nd bearing 38 are arrange
- the valve body 14 is fixed by welding to a pin 15 a formed at the distal end portion of the rotating shaft 15 and is disposed in the flow path 11.
- the end frame 36 is fixed to the valve housing 35 by a plurality of clips 39 (see FIGS. 1 and 2).
- a main gear 41 including a sector gear is fixed to the base end portion 15 b of the rotating shaft 15.
- a return spring 40 that generates a return spring force Fs1 is provided between the valve housing 35 and the main gear 41.
- the return spring force Fs1 is a force that rotates the rotary shaft 15 in the valve closing direction, and is a force that biases the valve body 14 in the closing direction.
- the return spring 40 is an elastic body formed by winding a wire in a coil shape, and includes a back side hook 40a and a front side hook 40b at both ends thereof. As shown in FIG. 10, the back side hook 40 a and the near side hook 40 b are arranged at positions separated by about 180 ° in the circumferential direction of the return spring 40.
- the back side hook 40a is disposed on the valve housing 35 side (the back side in FIG. 10), and abuts against a spring hook portion 35c (see FIG. 18) of the valve housing 35.
- the front side hook 40b is disposed on the main gear 41 side (the front side in FIG. 10) and is in contact with the spring hook portion 41c of the main gear 41.
- the main gear 41 includes a fully closed stopper portion 41a, a gear portion 41b, a spring hook portion 41c, a spring guide portion 41d, and the like.
- a fully closed stopper portion 41a, a gear portion 41b, and a spring hook portion 41c are sequentially formed.
- the main gear 41 is provided integrally with the rotary shaft 15 and receives a driving force generated by the motor 32.
- the fully closed stopper portion 41a is a portion that comes into contact with the fully closed stopper portion 35b of the valve housing 35 when the valve opening degree ⁇ is “0”.
- the valve opening ⁇ is the rotation angle of the rotation shaft 15 when the rotation shaft 15 rotates about the central axis Ls, and corresponds to the rotation angle of the main gear 41, the opening of the valve body 14, and the EGR valve opening. To do.
- the valve opening ⁇ is “0”, in other words, when the rotation angle of the rotating shaft 15 is the minimum angle within the rotation range of the rotating shaft 15. 7 to 10 show the case where the valve opening degree ⁇ is “0”.
- the gear portion 41b meshes with the small-diameter gear 42b of the intermediate gear 42.
- the spring hook portion 41c is in contact with the near side hook 40b of the return spring 40, and a return spring force Fs1 is applied from the near side hook 40b (see FIG. 11).
- the spring guide portion 41 d is disposed inside the coiled return spring 40 and supports the return spring 40. Further, the spring guide portion 41 d is provided integrally with the rotary shaft 15 at a portion on the base end portion 15 b side of the rotary shaft 15.
- the main gear 41 includes a recess 41e, and a magnet 46 having a substantially disk shape is accommodated in the recess 41e. Therefore, when the main gear 41 rotates integrally with the valve body 14 and the rotating shaft 15, the magnet 46 rotates and the magnetic field of the magnet 46 changes. The change in the magnetic field of the magnet 46 is detected by a rotation angle sensor (not shown), so that the rotation angle of the main gear 41 is detected as the opening degree of the valve body 14, that is, the EGR valve opening degree.
- the motor 32 is housed and fixed in a housing recess 35 a formed in the valve housing 35.
- the motor 32 is drivingly connected to the rotary shaft 15 via the speed reduction mechanism 33 in order to open and close the valve body 14. That is, the motor gear 43 is fixed to the output shaft 32a (see FIG. 9) of the motor 32.
- the motor gear 43 is drivingly connected to the main gear 41 via the intermediate gear 42.
- the motor 32 generates a driving force that rotates the rotating shaft 15 in the valve opening and closing directions.
- the intermediate gear 42 is a two-stage gear having a large-diameter gear 42a and a small-diameter gear 42b, and is rotatably supported by the valve housing 35 via a pin shaft 44.
- a motor gear 43 is drivingly connected to the large diameter gear 42a, and a main gear 41 is drivingly connected to the small diameter gear 42b.
- resin gears made of a resin material are used as the gears 41 to 43 constituting the speed reduction mechanism 33 in order to reduce the weight.
- the motor 32 is an example of the “drive mechanism” in the present invention.
- the intermediate gear 42 transmits the driving force of the motor 32 to the rotary shaft 15 and is an example of the “drive transmitting portion” in the present invention.
- the valve element 14 is opened and the flow path 11 is opened against the return spring force Fs1 that is generated by the return spring 40 and is urged in the valve closing direction. Thereafter, when the driving voltage applied to the motor 32 is maintained constant while the valve body 14 is opened, the motor driving force Fm1 and the return spring force Fs1 are balanced by the opening of the valve body 14 at that time. Thus, the valve body 14 is held at a predetermined opening.
- the operation of the EGR valve 1 in this embodiment will be described in detail.
- the valve opening ⁇ is “0” (the rotary shaft 15 is closed).
- the fully closed stopper portion 41 a of the main gear 41 is in contact with the fully closed stopper portion 35 b of the valve housing 35.
- the engine is stopped.
- the return spring force Fs 1 is applied to the spring hook portion 41 c of the main gear 41 from the front side hook 40 b of the return spring 40.
- the x axis is the horizontal direction
- the y axis is the vertical direction
- the + x direction and the + y direction are in the first quadrant
- ⁇ The x direction and the + y direction are the second quadrant
- the ⁇ x direction and the ⁇ y direction are the third quadrant
- the + x direction and the ⁇ y direction are the fourth quadrant.
- the rear side hook 40a and the fully closed stopper part 41a are arranged so as to be located in the first quadrant
- the front side hook 40b and the spring hook part 41c are arranged so as to be located in the third quadrant.
- a fulcrum is set for the fully closed stopper portion 41a
- a force point is set for the spring hook portion 41c
- an action point is set at the central portion between the fully closed stopper portion 41a and the spring hook portion 41c.
- the force Fs2 acts on the central portion between the fully closed stopper portion 41a and the spring hook portion 41c by the return spring force Fs1 applied to the spring hook portion 41c.
- (force Fs2) 2 ⁇ (return spring force Fs1).
- the distance between the fully closed stopper portion 41a and the spring hook portion 41c is “2R”.
- the + y direction component of the force Fs2 is a component force Fs3 as shown in FIG.
- the + y direction is a direction perpendicular to the central axis Lj direction (x direction) of the first bearing 37 and the second bearing 38 and is a direction in which the valve seat 13 is disposed with respect to the valve body 14 ( 11 and FIG. 12).
- (component force Fs3) (force Fs2) ⁇ (sin ⁇ 1).
- the angle ⁇ 1 is an angle formed by the arrangement direction of the fully closed stopper portion 41a and the spring hook portion 41c with respect to the x direction.
- the force Fs4 (counter valve seat direction biasing force) acts in the + y direction.
- (force Fs4) (component force Fs3) ⁇ Lb / La.
- the force Fs4 is a force generated due to the return spring force Fs1 and is a force acting in a direction perpendicular to the central axis Lj of the first bearing 37 and the second bearing 38.
- the distance La is the distance from the position where the first bearing 37 is arranged in the x direction to the position where the force Fs4 acts.
- the distance Lb is a distance from the position where the first bearing 37 is disposed in the x direction to the position where the component force Fs3 acts.
- FIG. 19 which shows the relationship between valve opening degree (theta) and opening area S, it exists in the position of the point P1a.
- “when the rotating shaft 15 is in the closed state” means when the valve opening degree ⁇ (the opening degree of the valve body 14) is “0”, in other words, the rotation angle of the rotating shaft 15 is closed. This is when the angle is the valve angle (minimum angle within the rotation range of the rotary shaft 15).
- the main gear 41 is rotated from the small-diameter gear 42b of the intermediate gear 42 (see FIG. 10) to the gear portion 41b (see FIG. 10) of the main gear 41.
- the motor driving force Fm1 is applied.
- the motor driving force Fm1 acts in the -y direction as shown in FIG.
- the ⁇ y direction is a direction perpendicular to the central axis Lj direction (x direction) of the first bearing 37 and the second bearing 38, and is a direction in which the valve body 14 is disposed with respect to the valve seat 13. (Downward direction of FIG. 11 and FIG. 12).
- This force Fm3 is a force generated due to the motor driving force Fm1, and is a force acting in a direction perpendicular to the central axis Lj of the first bearing 37 and the second bearing 38. Then, the force Fm3 rotates and tilts the rotary shaft 15 with the first bearing 37 as a fulcrum, and biases the valve body 14 in a direction toward the valve seat 13.
- the fully closed stopper portion 41 a of the main gear 41 is separated from the fully closed stopper portion 35 b of the valve housing 35. Further, at this time, in FIG. 19 showing the relationship between the valve opening degree ⁇ and the opening area S, it exists at the position of the point P1c.
- the EGR valve 1 has two bearings of the first bearing 37 and the second bearing 38, but has one bearing instead of the first bearing 37 and the second bearing 38. It may also have three or more bearings.
- the EGR valve 1 of the present embodiment as described above generates the force Fs4 when the motor 32 is not driven.
- the force Fs4 is a force generated due to the return spring force Fs1 and is a force acting in a direction perpendicular to the central axis Lj of the first bearing 37. Then, the force Fs4 rotates and tilts the rotary shaft 15 with the first bearing 37 as a fulcrum, and biases the valve body 14 in a direction away from the valve seat 13.
- the EGR valve 1 when the engine is stopped and the motor 32 is not driven, the EGR valve 1 is in a closed state, so that a minute gap is generated between the valve seat 13 and the valve body 14. Therefore, even if deposits adhere to the valve seat 13 and / or the valve body 14, the valve seat 13 and the valve body 14 are prevented from sticking to each other. Moreover, sticking of the valve seat 13 and the valve body 14 due to freezing is also prevented. Therefore, the opening / closing operation of the EGR valve 1 is stabilized. Further, since the valve element 14 is moved away from the valve seat 13 by the force Fs4, even if a foreign object is caught between the valve seat 13 and the valve element 14 during the valve closing operation, the foreign object is dropped off. Thus, no galling or the like occurs between the valve seat 13 and the valve body 14. Therefore, sticking of the valve seat 13 and the valve body 14 is prevented stably.
- the force Fs4 is generated when the motor 32 is not driven and when the rotating shaft 15 is in a closed state.
- “when the rotating shaft 15 is in the closed state” means when the valve opening degree ⁇ is “0”.
- the force Fm3 is generated when the motor 32 is driven.
- the force Fm3 is a force generated due to the motor driving force Fm1 and is a force acting in a direction perpendicular to the central axis Lj of the first bearing 37. Then, the force Fm3 rotates and tilts the rotary shaft 15 with the first bearing 37 as a fulcrum, and biases the valve body 14 in a direction toward the valve seat 13.
- the opening area S (gap between the valve seat 13 and the valve body 14) at the initial stage of valve opening becomes small. Therefore, the flow rate when the valve body 14 is at a low opening (when the valve opening ⁇ is small) can be reduced. Therefore, the accuracy of the flow rate control when the valve body 14 is low is improved.
- valve element 14 is seated on the valve seat 13 by the force Fm3.
- the EGR valve 1 is opened after the valve element 14 is once seated on the valve seat 13 by the force Fm3.
- the opening degree of the valve body 14 may be controlled by using the opening degree of the valve body 14 when the fluid flows at a predetermined flow rate as a reference position.
- the flow rate is controlled by controlling the valve opening degree ⁇ based on ⁇ (see FIG. 19).
- the control unit 50 (see FIG. 1) that performs the control is provided in the EGR valve 1 or provided separately from the EGR valve 1.
- the opening degree of the valve body 14 may be controlled by using the opening degree of the valve body 14 when the EGR valve 1 is closed as a reference position.
- the flow rate is controlled by controlling the valve opening degree ⁇ with “0” as a reference.
- the control unit 50 that performs the control is provided in the EGR valve 1 or provided separately from the EGR valve 1. Thereby, since the reference position of the flow rate control is uniquely determined, the accuracy of the flow rate with respect to the valve opening degree ⁇ is improved.
- the EGR valve 1 has an intermediate gear 42 disposed between the motor 32 and the main gear 41.
- the intermediate gear 42 transmits the driving force of the motor 32 from the motor 32 to the main gear 41.
- the driving force received from the motor 32 by the intermediate gear 42 can be increased and transmitted, so that the driving force generated by the motor 32 can be reduced. Therefore, the motor 32 can be downsized.
- the rotary shaft 15 may be supported at both ends by a first bearing 37 and a bearing (not shown) separately provided on the opposite side of the valve body 14.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Electrically Driven Valve-Operating Means (AREA)
- Exhaust-Gas Circulating Devices (AREA)
- Lift Valve (AREA)
Abstract
Description
2 弁部
3 駆動機構部
11 流路
13 弁座
14 弁体
15 回転軸
15a ピン
15b 基端部
16 弁孔
17 シート面
18 シール面
32 モータ
33 減速機構
35 弁ハウジング
35b 全閉ストッパ部
35c スプリングフック部
37 第1軸受
38 第2軸受
40 リターンスプリング
40a 奥側フック
40b 手前側フック
41 メインギヤ
41a 全閉ストッパ部
41b 歯車部
41c スプリングフック部
41d スプリングガイド部
Ls (回転軸の)中心軸
Lv (弁体の)中心軸
Lj (軸受の)中心軸
Fs1 リターンスプリング力
Fs4 力
Fm1 モータ駆動力
Fm3 力
θ 弁開度
Claims (6)
- 弁孔と前記弁孔の縁部に形成されたシート面を含む弁座と、
前記シート面に対応するシール面が外周に形成された弁体と、
前記弁体が一体的に設けられ前記弁体を回動させる回転軸と、を有し、
前記回転軸の中心軸が前記弁体及び前記弁孔の径方向と平行に伸びており、前記回転軸の中心軸が前記弁孔の中心から前記弁孔の径方向へ偏心して配置されると共に、前記シール面が前記回転軸の中心軸から前記弁体の中心軸が伸びる方向へ偏心して配置される二重偏心弁において、
前記回転軸を開弁方向に回転させる駆動力を発生させる駆動機構と、
前記回転軸と一体的に設けられ前記駆動力を受給する駆動力受給部と、
前記回転軸の中心軸方向について前記弁体と前記駆動力受給部との間の位置に配置され前記回転軸を支持する軸受と、
前記回転軸を閉弁方向に回転させるリターンスプリング力を発生させるリターンスプリングと、を有し、
前記駆動機構の非駆動時に、前記リターンスプリング力に起因して発生する力であり、かつ、前記軸受の中心軸に対して垂直な方向に作用する力であって、前記軸受を支点として前記回転軸を傾けて前記弁体を前記弁座から離れる方向に付勢する反弁座方向付勢力を発生させること、
を特徴とする二重偏心弁。 - 請求項1の二重偏心弁において、
前記駆動機構の駆動時に、前記駆動力に起因して発生する力であり、かつ、前記軸受の中心軸に対して垂直な方向に作用する力であって、前記軸受を支点として前記回転軸を傾けて前記弁体を前記弁座に向かう方向に付勢する弁座方向付勢力を発生させること、
を特徴とする二重偏心弁。 - 請求項2の二重偏心弁において、
前記弁座方向付勢力により前記弁体が前記弁座に着座すること、
を特徴とする二重偏心弁。 - 請求項2または3の二重偏心弁において、
流体が所定流量流れるときの前記弁体の開度を基準位置として、前記弁体の開度の制御が行われること、
を特徴とする二重偏心弁。 - 請求項2または3の二重偏心弁において、
閉弁時の前記弁体の開度を基準位置として、前記弁体の開度の制御が行われること、
を特徴とする二重偏心弁。 - 請求項1乃至5のいずれか1つの二重偏心弁において、
前記駆動機構と前記駆動力受給部との間に配置され、前記駆動力を前記駆動機構から前記駆動力受給部へ伝達する駆動伝達部を有すること、
を特徴とする二重偏心弁。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/301,777 US10024438B2 (en) | 2014-06-30 | 2015-06-24 | Double eccentric valve |
JP2016531297A JP6248196B2 (ja) | 2014-06-30 | 2015-06-24 | 二重偏心弁 |
CN201580009865.7A CN106030089B (zh) | 2014-06-30 | 2015-06-24 | 双偏心阀 |
DE112015003071.9T DE112015003071T5 (de) | 2014-06-30 | 2015-06-24 | Doppel-Exzenter-Ventil |
US15/949,366 US10260637B2 (en) | 2014-06-30 | 2018-04-10 | Double eccentric valve |
Applications Claiming Priority (2)
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---|---|---|---|
JP2014134268 | 2014-06-30 | ||
JP2014-134268 | 2014-06-30 |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/301,777 A-371-Of-International US10024438B2 (en) | 2014-06-30 | 2015-06-24 | Double eccentric valve |
US15/949,366 Division US10260637B2 (en) | 2014-06-30 | 2018-04-10 | Double eccentric valve |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016002599A1 true WO2016002599A1 (ja) | 2016-01-07 |
Family
ID=55019141
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2015/068197 WO2016002599A1 (ja) | 2014-06-30 | 2015-06-24 | 二重偏心弁 |
Country Status (5)
Country | Link |
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US (2) | US10024438B2 (ja) |
JP (2) | JP6248196B2 (ja) |
CN (1) | CN106030089B (ja) |
DE (1) | DE112015003071T5 (ja) |
WO (1) | WO2016002599A1 (ja) |
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JP2017210978A (ja) * | 2016-05-23 | 2017-11-30 | 愛三工業株式会社 | 二重偏心弁 |
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JP2018066386A (ja) * | 2016-10-17 | 2018-04-26 | 愛三工業株式会社 | 二重偏心弁 |
CN108071526A (zh) * | 2016-11-14 | 2018-05-25 | 爱三工业株式会社 | 排气回流阀 |
DE112017002771T5 (de) | 2016-06-01 | 2019-02-28 | Aisan Kogyo Kabushiki Kaisha | Doppelexzentrisches Ventil |
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US11274750B2 (en) | 2017-07-11 | 2022-03-15 | Aisan Kogyo Kabushiki Kaisha | Double eccentric valve |
DE102019119836B4 (de) | 2018-08-29 | 2022-03-31 | Denso Corporation | Maschinensteuerungssystem |
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KR102565392B1 (ko) * | 2021-08-20 | 2023-08-09 | 엘지전자 주식회사 | 밸브 액츄에이터 |
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Also Published As
Publication number | Publication date |
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US20170152953A1 (en) | 2017-06-01 |
US10260637B2 (en) | 2019-04-16 |
US10024438B2 (en) | 2018-07-17 |
JP6248196B2 (ja) | 2017-12-13 |
CN106030089A (zh) | 2016-10-12 |
CN106030089B (zh) | 2018-09-11 |
JPWO2016002599A1 (ja) | 2017-04-27 |
US20180224000A1 (en) | 2018-08-09 |
DE112015003071T5 (de) | 2017-03-23 |
JP6490180B2 (ja) | 2019-03-27 |
JP2018080834A (ja) | 2018-05-24 |
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