WO2011108331A1 - ウエストゲートバルブ装置 - Google Patents
ウエストゲートバルブ装置 Download PDFInfo
- Publication number
- WO2011108331A1 WO2011108331A1 PCT/JP2011/052105 JP2011052105W WO2011108331A1 WO 2011108331 A1 WO2011108331 A1 WO 2011108331A1 JP 2011052105 W JP2011052105 W JP 2011052105W WO 2011108331 A1 WO2011108331 A1 WO 2011108331A1
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- WO
- WIPO (PCT)
- Prior art keywords
- valve body
- valve
- protrusion
- wastegate
- wastegate valve
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
- F02B37/183—Arrangements of bypass valves or actuators therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/105—Final actuators by passing part of the fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
- F02B37/183—Arrangements of bypass valves or actuators therefor
- F02B37/186—Arrangements of actuators or linkage for bypass valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to a wastegate valve device that opens and closes an exhaust bypass passage that bypasses the exhaust turbine and communicates with an exhaust gas outlet passage from an exhaust passage that is driven by exhaust gas from an engine.
- a relatively small exhaust turbocharger includes a wastegate valve that opens and closes an exhaust bypass passage that bypasses the exhaust turbine and leads to an exhaust gas outlet passage from the exhaust passage to the exhaust turbine driven by exhaust gas.
- the waste gate valve is opened to control a part of the exhaust gas to bypass the exhaust turbine and escape to the exhaust gas outlet passage, so that the exhaust gas flow rate is adjusted to an appropriate flow rate.
- the engine output is increased by raising the operating point of the exhaust gas flow rate at the time of low load.
- FIG. 18 shows an example of a structure around a wastegate valve in an exhaust turbine of a conventional exhaust turbocharger.
- FIG. 18A is a longitudinal sectional view of a wastegate valve drive unit, and FIG. It is AA sectional drawing.
- reference numeral 200 denotes an exhaust turbine configured as follows.
- Reference numeral 1 denotes a turbine casing provided with a turbine 2 (the contents are not shown).
- a waste gate valve 100 bypasses the turbine 2 by branching the exhaust gas supplied from the engine (not shown) through the exhaust gas passage 11 to the turbine 2 from the exhaust gas passage 11 upstream of the turbine 2. Then, it flows into the exhaust bypass passage 5 and communicates with the exhaust outlet passage 18s.
- Reference numeral 4 denotes an exhaust gas inlet flange from the engine.
- the valve body 01 of the wastegate valve 100 reciprocates to open and close the valve seat portion 12 of the exhaust bypass passage 5 and when the valve is opened, the exhaust bypass from the exhaust gas passage 11 as shown in FIG. 18B.
- the exhaust gas (bypass flow) in the passage 5 flows to the exhaust outlet passage 18s as indicated by the arrow.
- An end 8b of an L-shaped support shaft 8 is fixed to the valve body 01 of the waste gate valve 100 by a rivet 8c.
- the rotating portion of the support shaft 8 is rotatably fitted to a bush 7 fixed to the turbine casing 1.
- the valve 9 is an arm, which is fixed to the shaft end of the support shaft 8 by caulking 9a or the like.
- One end of the arm 9 is provided with a connecting portion 13 to an actuator (not shown). Therefore, the reciprocating movement of the connecting portion 13 by the actuator causes the support shaft 8 to rotate about its axis 8a, and the rotation of the support shaft 8 about the axis 8a causes the valve body 01 to move.
- the valve body 01 is opened and closed while being attached to and detached from the seat portion 12.
- Patent Document 1 Japanese Patent Laid-Open No. 2009-92026
- the wastegate valve 5 has a root portion on a support shaft 51 that is rotatable to a cylinder head. Is supported, and a flat valve body 54 s is supported at a free end portion of the arm 53 so as to be rotatable around an axis 52 of the support shaft 51. Then, the waste gate valve 5 is opened and closed by attaching and detaching the bottom surface 54d of the flat valve body 54s to the contact surface 56 of the valve seat portion 55 by turning around the axis 52 of the support shaft 51. ing.
- Reference numeral 103 denotes an exhaust gas bypass passage.
- Patent Document 1 In a wastegate valve having flat valve bodies 01 and 54s as shown in FIG. 18 and FIG. 19 (Patent Document 1), as shown in FIG. , (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) passing flow rate when fully open)): X (%) is the valve opening ( Ideally, the flow rate ratio: X (%) increases in proportion to the valve opening as the opening of the valve element increases.
- a flat valve body is provided around the axis of the support shaft at the free end of the arm that rotatably supports the support shaft.
- the valve opening is small (generally 0 to 20 °), as shown by line C in FIG. 20, the swingable valve body around the support shaft is supported.
- the flow rate ratio X increases rapidly.
- the wastegate valve having such a swinging valve body has an extremely small valve opening (generally 0 to 20 °), that is, even when the wastegate valve is almost fully closed, the wastegate valve passes through the wastegate valve. In such a flow characteristic of the waste gate valve, it becomes difficult to control the response of the exhaust turbine, and the response of the exhaust turbine cannot be controlled.
- the present invention has been made in view of the problems of the prior art, and in a wastegate valve having an oscillating valve body, the passage flow rate ratio is proportional to the valve opening, particularly in a portion where the valve opening is extremely small. It is an object of the present invention to provide a wastegate valve device that can be controlled so that the response of the exhaust turbine can be smoothly controlled at all opening degrees of the wastegate valve.
- An exhaust bypass passage that bypasses the exhaust turbine and communicates with an exhaust outlet passage from an exhaust passage connected to an exhaust turbine driven by exhaust gas from an engine, and a support shaft.
- a wastegate valve that is attached to a free end of a support arm that is pivotable and has a valve body that opens and closes between the exhaust bypass passage and the exhaust outlet passage by swinging of the support arm,
- the waste gate valve device configured to fully close the waste gate valve when the valve body of the waste gate valve comes into contact with the seat surface of the valve seat portion, the seat of the valve body of the waste gate valve
- a protrusion having a constant height is provided on the side in contact with the seating surface so as to reduce the passage area of the exhaust gas.
- the projection portion having a constant height so as to reduce the exhaust gas passage area on the side of the wastegate valve that contacts the seat seat surface of the valve body.
- the protrusion provided on the exhaust gas upstream side of the valve body.
- an increase in the exhaust gas flow rate can be suppressed at the portion of the wastegate valve where the valve opening is extremely small (generally 0 to 20 °), and a rapid increase in the exhaust gas flow rate can be suppressed.
- the wastegate valve having a swinging valve body, and the entire portion where the valve opening is increased from the portion where the valve opening is extremely small (approximately 0 to 20 °) due to the installation of the protrusion
- the flow rate ratio of the exhaust gas passing through the valve body can be increased approximately proportionally as the valve opening increases, so that the response of the exhaust turbine can be controlled smoothly at the full opening of the wastegate valve. . Therefore, even in a state where the valve opening is extremely small and the waste gate valve is almost fully closed, such as a waste gate valve having a conventional swinging valve body as shown in FIGS. 18 and 19 (Patent Document 1). , The flow rate may flow to the exhaust passage side through the wastegate valve. With such a flow rate characteristic, it becomes difficult to control the response of the exhaust turbine, and it is impossible to control the response of the exhaust turbine. I can stop.
- the protrusion connects the first cone having the angle ⁇ 1 between the outer line portion and the seat surface to the valve body, and the angle ⁇ 2 between the outer line portion and the seat surface is the first angle.
- a second cone smaller than one cone is connected to the end of the first cone to form a two-stage cone.
- the angle ⁇ 1 between the contour line portion of the projection of the cone and the sheet surface is set to 80 ° or less and 30 ° or more.
- the angle ⁇ can be in a range of 30 ° ⁇ ⁇ 90 °.
- Ratio of valve opening (valve opening) and (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) passing flow rate when fully opened) in the case of such an angle ⁇ range: X (%) is as indicated by line A in FIG. 2A, and approaches the ideal line B where the flow rate ratio: X (%) increases in proportion to the valve opening. Therefore, by combining the first cone and the second cone to form a projection, the flow rate adjustment effect of the projection is obtained with a wide valve opening, that is, 30 ° ⁇ ⁇ 90 °. be able to.
- the protrusion includes a distance (L1) between the swing center of the support arm and the tip of the protrusion, and a distance between the swing center of the support arm and the longest point of the protrusion ( L2) and the distance (L3) between the swing center of the support arm and the open end of the exhaust gas passage hole, L3> L1 and L3> L2, so that the protrusion is the exhaust gas passage hole. Contact with the opening edge of the part can be avoided.
- the following five cases are formed so that the protrusions are parallel to the exhaust gas passage hole according to the opening even if the angle changes. For example, even when the valve body moves in an arc shape, it is easy to obtain an arbitrary exhaust gas passage area.
- the protrusion is connected to the valve body by a plurality of cylindrical bodies whose thickness changes linearly in the radial direction so that the cylindrical body does not cushion the valve hole when the valve body is opened.
- the protrusion is connected to the valve body by a plurality of cylindrical bodies whose thickness changes in a straight line in a radial direction, and the cylindrical body does not buffer the valve hole when the valve body is opened. The body is tilted and placed one above the other.
- the protruding portion is formed in a hemispherical shape and fixes the root portion to the valve body.
- the protrusion is formed in a truncated cone shape with a sharp tip, and fixes the fundamental large diameter portion to the valve body.
- the projecting portion is formed in a truncated cone shape having a smooth end surface, and fixes the fundamental large diameter portion to the valve body.
- the protrusion is formed on a hemispherical strain surface and fixes the root to the valve body.
- the inside of the protrusion is formed in a hollow shape, the combined weight of the protrusion and the valve body is reduced. As a result, the responsiveness is improved and the inside is hollowed to reduce the weight, so that it is difficult to break. Further, the driving force between the protrusion and the valve body can be reduced. In addition, only the protruding portion can be detached from the valve body and can be attached and disassembled, and the disassembling and replacing of the protruding portion and the valve body is easy.
- valve body and the projecting portion are integrally formed of sheet metal, the weight of the valve body and the projecting portion is reduced as compared with the case where the protrusion is simply created and attached separately. As a result, the responsiveness is improved and damage is less likely to occur due to the integral formation. In addition, the driving force can be reduced and the manufacturing cost is low.
- the joint between the projection and the valve body and the exhaust gas passage hole so that the joint between the projection and the valve body does not come into contact with the exhaust gas passage hole even if the valve body undergoes thermal expansion.
- a gap is formed between the outer diameter of the protrusion and the inner diameter of the exhaust gas passage hole by increasing the amount corresponding to the thermal expansion, thereby increasing the protrusion due to the thermal expansion. It is possible to avoid contact between the part outer diameter and the exhaust gas passage hole.
- a protruding portion is installed on the valve body by decentering in advance in a direction opposite to the heat expansion direction by the amount of thermal elongation of the valve body.
- the coupling portion with the valve body is shifted in the direction opposite to the thermal elongation direction in advance and coupled eccentrically with respect to the valve body center. It is possible to avoid contact between the protrusion outer diameter and the exhaust gas passage hole due to thermal elongation.
- the open end of the exhaust gas passage hole of the valve seat portion corresponding to the joint portion between the root portion of the protrusion and the valve body is chamfered over the entire circumference, the fixed object is removed by the chamfering. By releasing the pinching force, it is possible to prevent sticking matter from adhering.
- valve body repeatedly collides with the seat seat surface of the valve seat portion, the outer peripheral portion of the valve body and the inner peripheral portion of the seat seat surface of the valve seat portion make impulsive contact.
- the following means are used.
- an outer cover that covers the entire circumference of the valve body is provided on the upper part of the valve body that includes the protruding portion, and the outer cover and the valve body are fixed and integrated into a valve body with an outer cover.
- the support arm is attached to the outer lid.
- an outer lid that extends in the radial direction of the valve body and is fixed at both ends in the radial direction is provided on the upper part of the valve body that includes the protrusion, and the support arm is attached to the outer lid. It is characterized by that.
- an outer cover that extends in the radial direction of the valve body and is fixed at both ends in the radial direction is provided on the upper part of the valve body that has the protrusion, and the support arm is attached to the outer cover.
- the opening and closing force from the support arm that supports the valve body can be distributed not at the center of the valve body but at the positions at both ends in the radial direction, improving the bending strength of the valve body and deforming, that is, opening the periphery of the valve body It is possible to prevent various deformations and improve the sealing performance.
- an outer lid is provided on the upper part of the valve body provided with the projections, extending in four directions in the radial direction of the valve body and fixed at four locations on the periphery, and the support is supported on the outer lid.
- the arm is attached.
- a wastegate valve having an oscillating valve body having a constant height so as to reduce the passage area of the exhaust gas on the side of the wastegate valve that contacts the seat seat surface of the valve body.
- FIG. 1 It is a longitudinal cross-sectional view of the wastegate valve in 1st Embodiment of this invention.
- (A) is a relationship diagram of the ratio between the valve opening degree and the (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) full opening flow rate) in the first embodiment.
- (B) is a longitudinal cross-sectional view which shows two examples of a wastegate valve. It is a longitudinal cross-sectional view of the wastegate valve in 2nd Embodiment of this invention.
- (A) is a longitudinal cross-sectional view of the wastegate valve in 3rd Embodiment of this invention.
- (B) is a relationship diagram of the ratio between the valve opening degree and the (W / G (waist gate valve) passage flow rate and W / G (waist gate valve) passage flow rate) in the third embodiment).
- (A) is a longitudinal cross-sectional view of the wastegate valve in 4th Embodiment of this invention.
- (B) is a relational diagram of the ratio between the valve opening degree and the (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) passing flow rate) in the fourth embodiment) in the fourth embodiment.
- (A) is a longitudinal cross-sectional view of the wastegate valve in 5th Embodiment of this invention.
- (B) is a relationship diagram of the ratio between the valve opening degree and the (W / G (waist gate valve) passing flow rate and the W / G (waist gate valve) fully opening flow rate) in the fifth embodiment.
- (A) is a longitudinal cross-sectional view of the wastegate valve in 6th Embodiment of this invention.
- (B) is a relationship diagram of the ratio between the valve opening degree and the (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) full opening flow rate) in the sixth embodiment.
- (A) is a longitudinal cross-sectional view of the wastegate valve in 7th Embodiment of this invention.
- (B) is a relationship diagram of the ratio between the valve opening degree and the (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) fully opening flow rate) in the seventh embodiment. It is a longitudinal cross-sectional view of the wastegate valve in 8th Embodiment of this invention. It is a longitudinal cross-sectional view of the wastegate valve in 9th Embodiment of this invention.
- (A) is a front view of the wastegate valve attachment part in 10th, 11th embodiment of this invention.
- (B) is a longitudinal sectional view of the waste gate valve of the tenth embodiment
- (C) is a longitudinal sectional view of the waste gate valve of the eleventh embodiment.
- FIG. 16 is a longitudinal sectional view of a waste gate valve for explaining the thirteenth to sixteenth embodiments of the present invention. It is a longitudinal cross-sectional view of the wastegate valve in 13th Embodiment of this invention.
- A) is a front view of the wastegate valve attachment part in 14th Embodiment of this invention.
- B) is a YY sectional view of (A).
- A) is a front view of the wastegate valve attachment part in 15th Embodiment of this invention.
- FIG. 5 is a general relationship diagram of a ratio between a valve opening and (a W / G (waist gate valve) passing flow rate and a W / G (waist gate valve) passing flow rate when fully opened)).
- FIG. 1 is a longitudinal sectional view of a wastegate valve according to a first embodiment of the present invention.
- FIG. 2A is a relationship diagram of the ratio between the valve opening degree and the (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) full opening flow rate) in the first embodiment.
- FIG. 2B and 2C are longitudinal sectional views showing two examples of the wastegate valve.
- the waste gate valve 100 allows exhaust gas supplied from the engine (not shown) to the turbine 2 through the exhaust gas passage 11 from the exhaust gas passage 11 upstream of the turbine 2. It branches, flows through the exhaust bypass passage 5 by bypassing the turbine 2, and further communicates with the exhaust outlet passage 18 s through the waste gate valve 100.
- the valve body 1 reciprocates to open and close the valve seat portion 12 of the exhaust bypass passage 5, and when the valve is opened, as shown in FIG.
- the exhaust gas branched from 11 to the exhaust bypass passage 5 flows from the exhaust bypass passage 5 to the exhaust gas outlet passage 18 as indicated by an arrow S in FIG.
- the waste gate valve 100 includes a support shaft 14 connected via a connecting arm 16 to a connecting pin 15 connected to a drive unit having an actuator.
- the valve body 1 is fixed to a free end of a support arm 3 that rotates in an arc around the support shaft 14, and the exhaust bypass passage 5 and the exhaust outlet passage 18 s are moved by the swinging of the support arm 3. It opens and closes between.
- the waste gate valve 100 is fully closed.
- a protrusion 2 configured as a two-stage truncated cone is fixed to the lower surface (seat surface 1 a) of the valve body 1.
- the protrusion 2 connects a first cone 2a having an inclination angle ⁇ 1 between the outer line portion and the seat surface 1a to the lower surface of the valve body 1, that is, the seat surface 1a, and the outer line portion and the seat surface 1a.
- a second cone 2b having an inclination angle ⁇ 2 smaller than that of the first cone 2a is connected to the end of the first cone 2a, and the tip 2y is cut flat to form a two-stage cone. It consists of a trapezoid.
- the inclination angle ⁇ 1 of the first cone 2a and the inclination angle ⁇ 2 of the second cone 2b are set as follows.
- the angle between the outer line portion of the projecting portion 2 and the seat surface 1a of the valve body 1 is used for fine flow rate adjustment.
- ⁇ 1 and ⁇ 2 must be increased, the end of the protrusion 2 draws an arc-shaped locus as shown in FIG. 1, and therefore the height of the protrusion 2 is limited due to the interference with the exhaust gas passage hole 5s. Is done.
- the flow rate can be finely adjusted by increasing the angle between the contour line portion of the projection portion 2 and the sheet surface 1a.
- the angle between the contour line portion of the projection portion 2 and the sheet surface 1a is increased, it is shown in FIG. In order to draw such a locus, the height of the protrusion 2 is reduced. Therefore, as shown in FIG. 2 (C), when the angle ⁇ 3 between the contour line portion of the projection 2 and the seat surface 1a exceeds 80 °, the flow rate adjustment effect of the projection 2 when the valve opening ⁇ 5 opens 17 °. Disappears.
- the angle ⁇ 1 between the contour line portion of the projection 2 of the cone and the sheet surface is set to 80 ° or less and 30 ° or more.
- valve opening (valve opening), (W / G (waist gate valve) passing flow rate, and W / G (waist gate valve) passing flow rate when the angle ⁇ ( ⁇ 1, ⁇ 2) is in the range).
- W / G waist gate valve
- W / G waist gate valve
- the wide valve opening that is, the inclination angles ⁇ 1 and ⁇ 2 are 30 ° ( ⁇ 2) ⁇ ⁇ . If the angle is limited to 90 ° ( ⁇ 1), the effect of adjusting the flow rate of the protrusion 2 can be obtained.
- a wastegate valve 100 including a valve body 1 having a projection 2 composed of a two-stage truncated cone obtained by coupling a first cone 2a and a second cone 2b is in its fully closed position.
- the seat surface 1a of the valve body 1 and the seat seat surface 12a of the valve seat 12 are opened by the swinging of the support arm 3 in the Q direction.
- the exhaust gas in the exhaust bypass passage 5 flows to the exhaust outlet passage 18s as shown by the streamline S in FIG.
- the first cone is formed on the exhaust bypass passage 5 side, that is, the upstream side of the valve body 1.
- the valve body 1 is provided with the projection 2 composed of a two-stage truncated cone that combines the second cone 2b.
- X (%) is as indicated by line A in FIG.
- the passing flow ratio: X (%) can almost approach the ideal line B that increases in proportion to the valve opening. That is, by providing the valve body 1 to which the projecting portion 2 composed of a two-stage truncated cone body in which the first cone 2a and the second cone 2b are joined, a portion having a very small valve opening (generally 0). The increase in the exhaust gas flow rate can be suppressed at ⁇ 20 °), and the rapid increase in the exhaust gas flow rate can be suppressed.
- the wastegate valve 100 is provided with the swinging valve body 1, and the projection portion 2 composed of a two-stage truncated cone body in which the first cone body 2 a and the second cone body 2 b are coupled is coupled.
- the exhaust flow rate ratio X (%) of the exhaust gas passing through the valve body 1 from the part where the valve opening degree is extremely small (approximately 0 to 20 °) to the part where the valve opening degree is large due to the installation of the valve body 1 Can be increased in proportion to the increase in the valve opening, and the response of the exhaust turbine can be controlled smoothly at the full opening of the wastegate valve 100.
- FIG. 3 is a longitudinal sectional view of a waste gate valve according to the second embodiment of the present invention.
- the protrusion 2 includes the distance L1 between the swing center 14e of the support arm 3 and the tip A of the protrusion 2, and the swing center 14e of the support arm 3 and the protrusion.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- the protrusion 2 is an exhaust gas passage hole according to the opening degree. It is formed so as to be parallel to the portion 5s, and if formed in this way, it is easy to obtain an arbitrary exhaust gas passage area even when the valve body 1 moves in an arc shape.
- FIG. 4A is a longitudinal sectional view of a wastegate valve in the third embodiment of the present invention.
- (B) is a relationship diagram of the ratio between the valve opening degree and the (W / G (waist gate valve) passage flow rate and W / G (waist gate valve) passage flow rate) in the third embodiment).
- the protrusion 2 changes in a straight manner in the radial direction on the valve body 1 such that the thickness is t1 to t2, the thickness is t3 to t4, and the thickness is t5 to t6.
- Cylinders 2e, 2f, 2g to be connected (three in this example), and the cylinders 2e, 2f, 2g are prevented from interfering with the exhaust gas passage hole 5s when the valve body 1 is opened.
- the body is tilted and placed one above the other.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- FIG. 4B shows the ratio X (%) between the valve opening degree and the (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) passing flow rate) when the third embodiment is fully opened).
- the X (%) is as indicated by the A line, and the flow rate ratio: X (%) can be brought close to the ideal line B that increases in proportion to the valve opening.
- the ideal line B is not a type in which the valve body 1 is swung (swinged) by the support arm 3 as in the embodiment, but a valve body that slides in the axial direction, that is, in the axial direction of the exhaust gas passage hole 5s.
- the currency flow rate ratio is shown (the same applies to the seventh embodiment in FIG. 8).
- FIG. 5A is a longitudinal sectional view of a wastegate valve in the fourth embodiment of the present invention.
- B is a relationship diagram of the ratio X of the valve opening degree (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) passing flow rate when fully opened)) in the fourth embodiment.
- the protruding portion 2 is formed in a hemispherical shape, and the base portion is fixed to the seat surface 1 a of the valve body 1.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- FIG. 5B shows the ratio X (%) between the valve opening degree and the (W / G (waist gate valve) passage flow rate and W / G (waist gate valve) passage flow rate) in the fourth embodiment) in the fourth embodiment. Shown in As shown in FIG. 5B, the X (%) is as indicated by the A line, and the passing flow rate ratio: X (%) can be brought close to the ideal line B that increases in proportion to the valve opening.
- FIG. 6A is a longitudinal sectional view of a wastegate valve in the fifth embodiment of the present invention.
- B is a relationship diagram of the ratio X of the valve opening degree (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) fully opening flow rate) in the fifth embodiment).
- the protrusion 2 is formed in a truncated cone shape with a pointed tip 2t, and a large root diameter portion is fixed to the seat surface 1a of the valve body 1.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- FIG. 6B shows a ratio X (%) between the valve opening degree and the (W / G (waist gate valve) passage flow rate and W / G (waist gate valve) passage flow rate) in the fifth embodiment). Shown in As shown in FIG. 6B, the X (%) is as indicated by the A line, and the flow rate ratio: X (%) can be brought close to the ideal line B that increases in proportion to the valve opening.
- FIG. 7A is a longitudinal sectional view of a wastegate valve in the sixth embodiment of the present invention.
- (B) is a relationship diagram of the ratio X of the valve opening degree (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) fully opening flow rate) in the sixth embodiment).
- the protrusion 2 is formed in a truncated cone shape having a tip portion formed on a smooth surface 2p, and the fundamental large diameter portion is a seat surface of the valve body 1. It is fixed to 1a.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- FIG. 7B shows the ratio X (%) between the valve opening degree and the (W / G (waist gate valve) passage flow rate and W / G (waist gate valve) passage flow rate) in the sixth embodiment). Shown in As shown in FIG. 7B, the X (%) is as indicated by the A line, and the flow rate ratio: X (%) can be brought close to the ideal line B that increases in proportion to the valve opening.
- FIG. 8A is a longitudinal sectional view of a wastegate valve in the seventh embodiment of the present invention.
- (B) is a relationship diagram of the ratio X of the valve opening degree (W / G (waist gate valve) passing flow rate and W / G (waist gate valve) passing flow rate when fully opened)) in the seventh embodiment.
- the projecting portion 2 is formed on a hemispherical distorted surface 2q, and the root portion is fixed to the seat surface 1a of the valve body 1.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- FIG. 8B shows the ratio X (%) between the valve opening degree and the (W / G (waist gate valve) passage flow rate and W / G (waist gate valve) passage flow rate) in the seventh embodiment). Shown in As shown in FIG. 8B, the X (%) is as indicated by the A line, and the flow rate ratio: X (%) can be brought close to the ideal line B that increases in proportion to the valve opening.
- FIG. 9 is a longitudinal sectional view of a wastegate valve according to an eighth embodiment of the present invention.
- the projecting portion 2 is provided with a projecting portion 2h from the valve body 1 to the exhaust bypass passage 5 side, and a hollow portion 2s is formed inside the projecting portion 2h.
- the base 2m of the protruding portion 2h is screwed to the lower surface of the valve body 1 (may be integrated with the valve body 1 or may be brazed).
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- the eighth embodiment by forming the cavity 2s inside the protrusion 2h, the combined weight of the protrusion 2 and the valve body 1 is reduced. As a result, the responsiveness is improved, and the inside is made light, so that the damage is hardly caused. Further, the driving force between the protrusion 2 and the valve body 1 can be reduced. Further, only the protrusion 2 can be detached from the valve body 1 and can be attached and disassembled, and the disassembly and assembly and replacement of the protrusion 2 and the valve body 1 are easy.
- FIG. 10 is a longitudinal sectional view of a waste gate valve according to the ninth embodiment of the present invention.
- the protrusion 2 is formed integrally with the valve body 1 and a protruding portion 2r protruding from the valve body 1 toward the exhaust bypass passage 5, that is, the protrusion 2 is made of sheet metal.
- a reinforcing plate 3 s is provided on the back side of the protrusion 2.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- the projecting portion 2r that projects from the valve body 1 toward the exhaust bypass passage 5 is formed integrally with the sheet metal, so that the projecting portion 2 and the projecting body 1 project more than the case where the projection 2 is simply provided.
- the weight of the part 2r is reduced.
- the responsiveness is improved, and the valve body 1 and the protruding portion 2r are integrally formed of sheet metal, so that damage is less likely to occur.
- the driving force with the valve body 1 can be reduced, and the manufacturing cost is also low because the valve body 1 and the protruding portion 2r are integrally formed of sheet metal.
- FIG. 11A is a front view of a wastegate valve mounting portion in the tenth and eleventh embodiments of the present invention.
- (B) is a longitudinal cross-sectional view of the wastegate valve of 10th Embodiment.
- the protrusion 2 and the valve body 1 are arranged so that the joint between the protrusion 2 and the valve body 1 does not come into contact with the exhaust gas passage hole 52s even if the valve body 1 undergoes thermal expansion.
- the gap is formed between the coupling portion and the inner diameter of the exhaust gas passage hole 52s, that is, the outer diameter f of the projection 2 and the inner diameter of the exhaust gas passage hole 52s are increased by the amount of thermal expansion.
- a gap e is set between Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- the tenth embodiment by taking the gap e between the outer diameter f of the protrusion 2 and the inner diameter of the exhaust gas passage hole 5s by the amount of thermal elongation in the thermal elongation direction X or Y, It can avoid that the projection part 2 and exhaust gas passage hole part 5 by thermal elongation contact.
- FIG. 11A is a front view of a wastegate valve mounting portion in the tenth and eleventh embodiments of the present invention.
- (C) is a longitudinal cross-sectional view of the wastegate valve of the eleventh embodiment.
- the protrusion 2 causes the joint between the protrusion 2 and the valve body 1 in the heat extension direction X of the valve body 1 to be in a direction opposite to the heat extension direction X or Y in advance. It is shifted and is eccentrically coupled with the center of the valve body 1 by e (20 is the center of the protrusion 2 and 30 is the center of the valve body 1). Thereby, the outer peripheral side of the projection part 2 becomes a gap with different g1 and g2.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- the joint between the valve body 1 and the protrusion 2 is shifted in advance in the direction opposite to the heat elongation direction X or Y before the heat elongation. If the protrusion 2 is eccentrically coupled to the center of the body 1 by e, it is possible to avoid contact between the outer diameter of the protrusion 2 and the exhaust gas passage hole 52 s which are eccentric due to thermal expansion X or Y.
- FIG. 12 is a longitudinal sectional view of a wastegate valve according to a twelfth embodiment of the present invention.
- (B1), (B2), (C1), (C2) are enlarged views of the W portion in (A).
- the open end of the exhaust gas passage hole 52s of the seat seat surface 12a of the valve seat portion 12 corresponding to the joint portion between the root portion of the projection portion 2 and the valve body 1 is formed on the entire circumference.
- a chamfer 12t is formed over the entire surface.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- the valve body 1 moves in an arc.
- the force F acts in the direction of sandwiching the fixed object K at the intersection of the root portion of the protrusion 2 and the exhaust gas passage hole 5s of the valve seat portion 12 (FIG. 12 (B2)).
- the chamfer 12t is formed over the entire circumference of the seat seat surface 12a of the valve seat portion 12 as shown in FIG. 12C1, the force for sandwiching the fixed object K by the chamfer 12t as shown in FIG. 12C2.
- F1 can be opened to prevent the sticking matter K from adhering.
- FIG. 14 is a longitudinal sectional view of a wastegate valve according to a thirteenth embodiment of the present invention.
- the entire seat seat surface 12a of the valve seat portion 12 corresponds to the joint portion between the root portion of the protrusion 2 and the valve body 1.
- a chamfer 12t is formed, and an outer lid 49 that covers the valve body 1 is installed on the back of the valve body 1.
- a load F2 acts on the central support point.
- the chamfer 12t can reduce the surface pressure applied to the contact portion 2z between the corner portion of the valve seat portion 12 and the lower surface of the valve body 1.
- FIG. 15A is a front view of a wastegate valve mounting portion according to the fourteenth embodiment of the present invention.
- FIG. 15B is a YY sectional view of FIG.
- an outer lid 50 that covers the entire circumference of the valve body 1 is provided on the upper portion of the valve body 1 that includes the protrusion 2, and the outer lid 50 and the valve body 1 are integrated together. It is comprised in the valve body 60 with a lid
- the outer lid 50 and the valve body 1 are coupled by four screws 50a.
- the outer lid 50 has an air vent hole 50b.
- a load F2 acts on the central support point.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- the outer lid 50 that covers the entire circumference of the valve body 1 is provided on the upper portion of the valve body 1 having the protrusions 2, and the valve body 60 with an outer lid is formed by integrating the two.
- the strength of the valve body 1 is improved, and the force is distributed to the upper portion of the contact surface of the valve body 60 with the outer lid at the point of supporting the valve body 1 instead of the center of the valve body 1 (the force F1 is 4).
- the valve body 60 with the outer lid can be received by the uniform force F1 near the outer periphery. Therefore, deformation of the valve body can be prevented and sealing performance can be improved.
- FIG. 16A is a front view of a waste gate valve mounting portion in the fifteenth embodiment of the present invention.
- FIG. 16B is a sectional view taken along the line U-U in FIG.
- an outer lid 51 extending in the radial direction of the valve body 1 and fixed at two ends in the radial direction is provided on the upper part of the valve body 1 provided with the protrusions 2,
- the support arm 3 is attached to the outer lid 51, and the outer lid 51 and the valve body 1 are integrated into a valve body 61 with an outer lid.
- the outer lid 51 and the valve body 1 are coupled by two screws 50a.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- the outer lid 51 that extends in the radial direction of the valve body 1 and covers the radial direction is provided on the upper portion of the valve body 1 having the protrusions 2, and the outer lid 51 and the valve body 1 are connected to each other. Since the valve body 61 with the outer cover is integrated and the force is distributed to the outer periphery of the contact surface of the valve body 61 with the outer cover (the force F1 is distributed in two places), the opening and closing from the support arm 3 The force can be distributed not at the center of the valve body but at the positions at both ends in the radial direction, and the deformation is improved by improving the bending strength of the valve body. While preventing the deformation
- FIG. 17A is a front view of a wastegate valve mounting portion according to the sixteenth embodiment of the present invention.
- FIG. 17B is a sectional view taken along line VV in FIG.
- an outer lid 52 is provided on the upper part of the valve body 1 provided with the protrusion 2 and extends in the radial direction of the valve body 1 and is fixed at four locations on the periphery.
- the support arm 3 is attached to the outer lid 52, and the outer lid 52 and the valve body 1 are integrated into a valve body 62 with an outer lid.
- the outer lid 52 and the valve body 1 are coupled by four screws 50a.
- Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals.
- the four-sided outer lid 52 that covers the outer peripheral portion of the valve body 1 is provided on the upper portion of the valve body 1 having the protrusions 2, and the outer lid 52 and the valve body 1 are connected to each other. Since the valve body 62 with the outer lid is integrated and the force is distributed to the outer periphery of the contact surface of the valve body 62 with the outer lid (the force F1 is distributed to four locations), the opening and closing from the support arm 3 The force extends not in the center of the valve body but in four directions in the radial direction of the valve body 1 so that the force can be distributed at four locations on the peripheral portion. While preventing the deformation
- the exhaust flow turbine ratio is made close to the valve opening in proportion to the valve opening, particularly in a portion where the valve opening is extremely small. It is possible to provide a wastegate valve that can smoothly control the responsiveness of the wastegate valve at all opening degrees of the wastegate valve.
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Abstract
Description
図18(A)、(B)において、200は排気タービンで次のように構成されている。
1はタービンケーシングで内部にタービン(内容は図示省略)2を備えている。
100はウエストゲートバルブで、図示を省略したエンジンから排気ガス通路11を通って前記タービン2に供給される排気ガスを、前記タービン2の上流の排気ガス通路11から分岐し、前記タービン2をバイパスして排気バイパス通路5に流し、排気出口通路18sに連通させている。4はエンジンからの排気ガス入口フランジである。
前記ウエストゲートバルブ100の弁体01には、L字状の支軸8の端部8bがリベット8cにより固定されている。前記支軸8の回動部は、前記タービンケーシング1に固定されたブッシュ7に回動自在に嵌合されている。
そして、前記扁平状の弁体54sの底面54dを、支持軸51の軸心52回りの回動によって弁座部55の当接面56に着脱することにより、該ウエストゲートバルブ5の開閉を行っている。103は排気ガスバイパス通路である。
つまり、かかる揺動式の弁体を備えたウエストゲートバルブは、バルブ開度が極めて小さい(概ね0~20°)、つまりウエストゲートバルブが全閉に近い状態でも、ウエストゲートバルブを通して排気通路側に流れる可能性があり、かかるウエストゲートバルブの流量特性では、排気タービンの応答性をコントロールすることが困難となり、排気タービンの応答性の制御ができない。
よって、図18及び図19(特許文献1)に示すような従来の揺動式の弁体を備えたウエストゲートバルブのように、バルブ開度が極めて小さくウエストゲートバルブが全閉に近い状態でも、ウエストゲートバルブを通して排気通路側に流れる可能性があり、このような流量特性では、排気タービンの応答性をコントロールすることが困難となり、排気タービンの応答性の制御ができない、という問題の発生を阻止できる。
このような構成において、微細な流量調整を行うためには、突起部の外郭線部とシート面との角度θ1、θ2を大きくしなければならないが、突起部の端部が図1のような軌跡を描くため、突起部の高さは排ガス通路穴部との干渉の関係から制限される。
従って、円錐体の突起部の外郭線部とシート面との角度θ1は80°以下、30°以上とする。
かかる角度θ範囲の場合の、バルブ開度(弁体の開度)と、(W/G(ウエストゲートバルブ)通過流量とW/G(ウエストゲートバルブ)全開時の通過流量)との比:X(%)は、図2(A)のA線のとおりで、前記通過流量比:X(%)がバルブ開度に比例的に増加する理想線Bに近づく。
従って、前記の第1の円錐体と第2の円錐体とを結合して突起部を形成することにより、広いバルブ開度つまり30°<θ<90°で、突起部の流量調整効果を得ることができる。
(1)前記突起部は、前記弁体に、厚さが半径方向に直状に変化する円柱体を複数個連結して、且つ弁体の開放時に前記円柱体が弁穴部と緩衝しないように前記突起部は、前記弁体に、厚さが半径方向に直状に変化する円柱体を複数個連結して、且つ弁体の開放時に前記円柱体が弁穴部と緩衝しないように円柱体を傾斜させて重ね合わせて配置する。
(2)前記突起部は、半球状に形成され根本部を前記弁体に固定する。
(3)前記突起部は、先端部が尖った円錐台状に形成され根本大径部を前記弁体に固定する。
(4)前記突起部は、先端部を平滑面に形成した円錐台状に形成され根本大径部を前記弁体に固定する。
(5)前記突起部は、半球状の歪面に形成されて根本部を前記弁体に固定する。
また、突起部のみを弁体から外して取付け、分解可能であり、突起部及び弁体の分解組立及び交換が容易である。
これにより、排気タービンの応答性の制御をウエストゲートバルブの全開度においてスムーズになし得るようにできる。
図1は本発明の第1実施形態におけるウエストゲートバルブの縦断面図である。図2の(A)は前記第1実施形態におけるバルブ開度と(W/G(ウエストゲートバルブ)通過流量とW/G(ウエストゲートバルブ)全開時の通過流量)との比の関係線図である。図2の(B)、(C)はウエストゲートバルブの2つの例を示す縦断面図である。
このウエストゲートバルブ100については、図18に示すように、図示を省略したエンジンから排気ガス通路11を通って前記タービン2に供給される排気ガスを、前記タービン2の上流の排気ガス通路11から分岐し、前記タービン2をバイパスして排気バイパス通路5に流し、さらに該ウエストゲートバルブ100を介して、排気出口通路18sに連通している。
前記弁体1は、前記支持軸14の回りに円弧状に回動する支持アーム3の自由端部に固定されて、該支持アーム3の揺動により前記排気バイパス通路5と排気出口通路18sとの間を開閉している。そして、前記支持アーム3の揺動により、排気バイパス通路5の周囲に形成された弁座部12のシート座面12aに、弁体1のシート面1aが当接したときに、前記ウエストゲートバルブ100は全閉となる。
前記のような、2段の円錐台体からなる突起部2を備えた構成において、微細な流量調整を行うためには、突起部2の外郭線部と弁体1のシート面1aとの角度θ1、θ2を大きくしなければならないが、突起部2の端部が図1のような円弧状の軌跡を描くため、突起部2の高さは排ガス通路穴部5sとの干渉の関係から制限される。
従って、円錐体の突起部2の外郭線部とシート面との角度θ1は80°以下、30°以上とする。
かかる角度θ(θ1、θ2)範囲の場合の、バルブ開度(弁体の開度)と、(W/G(ウエストゲートバルブ)通過流量とW/G(ウエストゲートバルブ)全開時の通過流量)との比:X(%)は、図2(A)のA線のとおりであり、前記通過流量比:X(%)がバルブ開度に比例的に増加する理想線Bにほぼ近づく。
従って、前記第1の円錐体2aと第2の円錐体2bとを結合して突起部2を形成することにより、広いバルブ開度つまり、傾斜角度θ1、θ2は30°(θ2)<θ<90°(θ1)に限定すれば、突起部2の流量調整効果を得ることができる。
かかる、揺動式の弁体1を備えたウエストゲートバルブ100においては、ウエストゲートバルブ100のバルブ開度の小さいときには、弁体1の排気バイパス通路5側つまり上流側に、第1の円錐体2aと第2の円錐体2bを結合した2段の円錐台体からなる突起部2を結合した弁体1を設けたので、図2(A)のように、バルブ開度(弁体の開度)と、(W/G(ウエストゲートバルブ)通過流量とW/G(ウエストゲートバルブ)全開時の通過流量)との比:X(%)が、図2(A)のA線の通りとなり、前記通過流量比:X(%)がバルブ開度に比例的に増加する理想線Bにほぼ近づくことができる。
即ち、第1の円錐体2aと第2の円錐体2bを結合した2段の円錐台体からなる突起部2を結合した弁体1を設けることにより、バルブ開度が極めて小さい部分(概ね0~20°)で排ガス流量の増加を抑制できて、排ガス流量の通過流量の急激な増加を抑えることができる。
図3は本発明の第2実施形態におけるウエストゲートバルブの縦断面図である。
この第2実施形態においては、前記突起部2は、前記支持アーム3の揺動中心14eと前記突起部2の先端A間の距離L1と、前記支持アーム3の揺動中心14eと前記突起部2の最長点C間の距離L2と、前記支持アーム3の揺動中心14eと排ガス通路穴部5sの開口端間の距離L3としたとき、L3>L1で且つL3>L2のように構成する。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図4(A)は本発明の第3実施形態におけるウエストゲートバルブの縦断面図である。(B)は第3実施形態におけるバルブ開度と(W/G(ウエストゲートバルブ)通過流量とW/G(ウエストゲートバルブ)全開時の通過流量)との比の関係線図である。
この第3実施形態においては、前記突起部2は、前記弁体1に、厚さがt1~t2、厚さがt3~t4、厚さがt5~t6のように半径方向に直状に変化する円柱体2e、2f、2gを複数個(この例では3個)連結して、且つ弁体1の開放時に前記各円柱体2e、2f、2gが排ガス通路穴部5sと干渉しないように円柱体を傾斜させて重ね合わせて配置している。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図5(A)は本発明の第4実施形態におけるウエストゲートバルブの縦断面図である。(B)は第4実施形態におけるバルブ開度と(W/G(ウエストゲートバルブ)通過流量とW/G(ウエストゲートバルブ)全開時の通過流量)との比Xの関係線図である。
この第4実施形態においては、前記突起部2は、半球状に形成され根本部を前記弁体1のシート面1aに固定している。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図6(A)は本発明の第5実施形態におけるウエストゲートバルブの縦断面図である。(B)は第5実施形態におけるバルブ開度と(W/G(ウエストゲートバルブ)通過流量とW/G(ウエストゲートバルブ)全開時の通過流量)との比Xの関係線図である。
この第5実施形態においては、前記突起部2は、先端部2tが尖った円錐台状に形成され根本大径部を前記弁体1のシート面1aに固定している。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図7(A)は本発明の第6実施形態におけるウエストゲートバルブの縦断面図である。(B)は第6実施形態におけるバルブ開度と(W/G(ウエストゲートバルブ)通過流量とW/G(ウエストゲートバルブ)全開時の通過流量)との比Xの関係線図である。
この第6実施形態においては、図7(A)のように、前記突起部2は、先端部を平滑面2pに形成した円錐台状に形成され根本大径部を前記弁体1のシート面1aに固定している。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図8(A)は本発明の第7実施形態におけるウエストゲートバルブの縦断面図である。(B)は第7実施形態におけるバルブ開度と(W/G(ウエストゲートバルブ)通過流量とW/G(ウエストゲートバルブ)全開時の通過流量)との比Xの関係線図である。
この第7実施形態においては、前記突起部2は、半球状の歪面2qに形成されて根本部を前記弁体1のシート面1aに固定している。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図9は本発明の第8実施形態におけるウエストゲートバルブの縦断面図である。
この第8実施形態においては、前記突起部2は、前記弁体1から前記排気バイパス通路5側への突出部2hを設け、該突出部2hの内部に空洞部2sを形成している。そして、前記突出部2hの根本部2mは前記弁体1の下面に螺合(該弁体1と一体でも良く、あるいはロウ付けでもよい)している。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
また、突起部2のみを弁体1から外して取付け、分解可能であり、突起部2及び弁体1の分解組立及び交換が容易である。
図10は本発明の第9実施形態におけるウエストゲートバルブの縦断面図である。
この第9実施形態においては、前記突起部2は、前記弁体1と、該弁体1から排気バイパス通路5側へ突出する突出部位2r、つまり突起部2を板金で一体に形成している。該突起部2の裏側には補強の板3sが設けられている。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
これにより、応答性が向上するとともに、弁体1と突出部位2rを板金で一体に形成したので破損も起こりにくい。また、弁体1との駆動力を低減できるとともに、弁体1と突出部位2rを板金で一体に形成したので、製作コストも安価である。
図11(A)は本発明の第10、11実施形態におけるウエストゲートバルブ取付け部の正面図である。(B)は第10実施形態のウエストゲートバルブの縦断面図である。
この第10実施形態においては、弁体1が熱伸びを生じても突起部2と弁体1との結合部が、排ガス通路穴部52sに接触しないように、突起部2と弁体1との結合部と排ガス通路穴部52sの内径との間に隙間が大きく形成されることにより、すなわち、熱伸びの分だけ上乗せして、突起部2の外径fと排ガス通路穴部52sの内径との間に隙間eが設定されている。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図11(A)は本発明の第10、11実施形態におけるウエストゲートバルブ取付け部の正面図である。(C)は第11実施形態のウエストゲートバルブの縦断面図である。
この第11実施形態においては、前記突起部2は、弁体1の熱伸び方向Xにおける該突起部2と前記弁体1との結合部を、予め熱伸び方向XまたはYとは反対方向にずらして弁体1中心に対してeだけ偏心して結合する(20は突起部2の中心、30は弁体1の中心)。これにより、突起部2の外周側は、g1、g2の異なる隙間となる。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図12は本発明の第12実施形態におけるウエストゲートバルブの縦断面図である。(B1)、(B2)、(C1)、(C2)は(A)におけるW部拡大図である。
この第12実施形態においては、前記突起部2の根本部と弁体1との結合部に対応する、前記弁座部12のシート座面12aの排ガス通路穴部52sの開口端を全周に亘って面取り12tを形成する。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図14は本発明の第13実施形態におけるウエストゲートバルブの縦断面図である。
この第13実施形態においては、第12実施形態と同じく、前記突起部2の根本部と弁体1との結合部に対応する、前記弁座部12のシート座面12aの全周に亘って面取り12tを形成し、さらに該弁体1の背部に該弁体1を覆う外蓋49を設置している。中央の支持点には、荷重F2が作用している。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
かかる第13実施形態によれば、前記面取り12tにより、弁座部12の角部と弁体1の下面との接触部2zにかかる面圧を低減できる。
図15(A)は本発明の第14実施形態におけるウエストゲートバルブ取付け部の正面図である。(B)は図15(A)のY-Y断面図である。
この第14実施形態においては、前記突起部2を備えた弁体1の上部に、該弁体1の全周を覆う外蓋50を設け、外蓋50と弁体1とを一体にした外蓋付き弁体60に構成している。かかる外蓋50と弁体1とは、4箇所のねじ50aで結合している。また、前記外蓋50には、空気抜き用の穴50bが開口している。中央の支持点には、荷重F2が作用している。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図16(A)は本発明の第15実施形態におけるウエストゲートバルブ取付け部の正面図である。(B)は図16(A)のU-U断面図である。
この第15実施形態においては、前記突起部2を備えた弁体1の上部に、該弁体1の径方向に伸びて径方向の両端部2箇所で固定された外蓋51を設け、該外蓋51に前記支持アーム3が取り付けられ、該外蓋51と弁体1とを一体にした外蓋付き弁体61に構成している。かかる外蓋51と弁体1とは、2箇所のねじ50aで結合している。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
図17(A)は本発明の第16実施形態におけるウエストゲートバルブ取付け部の正面図である。(B)は図17(A)のV-V断面図である。
この第16実施形態においては、前記突起部2を備えた弁体1の上部に、該弁体1の径方向に4方に伸びて周部の4箇所で固定された外蓋52を設け、該外蓋52に前記支持アーム3が取り付けられ、該外蓋52と弁体1とを一体にした外蓋付き弁体62に構成している。かかる外蓋52と弁体1とは、4箇所のねじ50aで結合している。
その他の構成は、前記第1実施形態と同一であり、これと同一の部材は同一の符号で示す。
Claims (16)
- エンジンからの排気ガスにより駆動される排気タービンに接続される排気通路から、前記排気タービンをバイパスさせて排気出口通路に通ずる排気バイパス通路と、支持軸回りに回動可能にされた支持アームの自由端部に取り付けられて該支持アームの揺動により前記排気バイパス通路と排気出口通路との間を開閉する弁体を有するウエストゲートバルブとを備え、前記ウエストゲートバルブの弁体が弁座部のシート座面に当接したときに前記ウエストゲートバルブを全閉とするように構成されたウエストゲートバルブ装置において、
前記ウエストゲートバルブの弁体の前記シート座面に当接する側に、排ガスの通路面積を縮小するように一定高さの突起部が設けられたことを特徴とするウエストゲートバルブ装置。 - 前記突起部は、外郭線部とシート面との角度θ1を有する第1の円錐体を前記弁体に接続し、外郭線部と前記シート面との角度θ2が前記第1の円錐体よりも小さい第2の円錐体を前記第1の円錐体の端部に接続して、2段の円錐状体に構成されたことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記突起部は、前記支持アームの揺動中心と前記突起部の先端間の距離(L1)と、前記支持アームの揺動中心と前記突起部の最長点間の距離(L2)と、前記支持アームの揺動中心と排ガス通路穴部の開口端間の距離(L3)としたとき、
L3>L1で且つL3>L2のように構成したことを特徴とする請求項1記載のウエストゲートバルブ装置。 - 前記突起部は、前記弁体に、厚さが半径方向に直状に変化する円柱体を複数個連結して、且つ弁体の開放時に前記円柱体が弁穴部と緩衝しないように円柱体を傾斜させて重ね合わせて配置したことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記突起部は、半球状に形成され根本部を前記弁体に固定したことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記突起部は、先端部が尖った円錐台状に形成され根本大径部を前記弁体に固定したことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記突起部は、先端部を平滑面に形成した円錐台状に形成され根本大径部を前記弁体に固定したことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記突起部は、半球状の歪面に形成されて根本部を前記弁体に固定したことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記突起部は、内部が空洞状に形成されたことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記弁体と突出部とを板金で一体に形成したことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記弁体が熱伸びを生じても突起部と弁体との結合部が排ガス通路穴部に接触しないように、突起部と弁体との結合部と排ガス通路穴部との間に隙間が設定されることを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記弁体の熱伸び量分、予め熱伸び方向と反対方向に偏心させて前記弁体に対して突起部を設置したことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記突起部の根本部と弁体との結合部に対応する、前記弁座部の排ガス通路穴部の開口端を全周に亘って面取りしたことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記突起部を備えた弁体の上部に、該弁体の全周を覆う外蓋を設け、外蓋と弁体とを固定して一体にした外蓋付き弁体に構成し、該外蓋に前記支持アームが取り付けられたことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記突起部を備えた弁体の上部に、該弁体の径方向に伸びて径方向両端部で固定された外蓋を設け、該外蓋に前記支持アームが取り付けられたことを特徴とする請求項1記載のウエストゲートバルブ装置。
- 前記突起部を備えた弁体の上部に、該弁体の径方向に4方に伸びて周部の4箇所で固定された外蓋を設け、該外蓋に前記支持アームが取り付けられたことを特徴とする請求項1記載のウエストゲートバルブ装置。
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Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20140108654A (ko) * | 2012-01-03 | 2014-09-12 | 콘티넨탈 오토모티브 게엠베하 | 자동차용 밸브 장치 |
US8904785B2 (en) * | 2012-09-13 | 2014-12-09 | Honeywell International Inc. | Turbine wastegate |
US9010109B2 (en) | 2012-09-13 | 2015-04-21 | Honeywell International Inc. | Turbine wastegate |
CN104884760A (zh) * | 2013-04-15 | 2015-09-02 | 株式会社Ihi | 流量可变阀机构以及增压器 |
EP2821614A4 (en) * | 2012-02-28 | 2015-11-11 | Mitsubishi Heavy Ind Ltd | VALVE |
JP2018162771A (ja) * | 2017-03-27 | 2018-10-18 | 三菱重工業株式会社 | 弁装置、タービンハウジング、排気タービン過給機及びエンジン |
Families Citing this family (62)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE202009018979U1 (de) * | 2008-10-01 | 2015-02-09 | Borgwarner Inc. | Wastegate mit variabler Strömung |
US8459022B2 (en) | 2011-02-17 | 2013-06-11 | Honeywell International Inc. | Wastegate plug |
DE102011083369A1 (de) * | 2011-09-26 | 2013-03-28 | Bayerische Motoren Werke Aktiengesellschaft | Klappenvorrichtung für ein Turbolader-Wastegateventil |
DE102012207464A1 (de) * | 2012-05-04 | 2013-11-07 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Abgasturbolader für eine Brennkraftmaschine |
JP6277183B2 (ja) * | 2012-06-21 | 2018-02-07 | ボーグワーナー インコーポレーテッド | 排気ガスターボチャージャ |
US9200532B2 (en) | 2012-09-13 | 2015-12-01 | Honeywell International Inc. | Turbine wastegate |
US8984880B2 (en) * | 2012-09-13 | 2015-03-24 | Honeywell International Inc. | Turbine wastegate |
FR2998616B1 (fr) * | 2012-11-23 | 2018-01-12 | Psa Automobiles Sa. | Soupape de regulation d'un systeme de suralimentation par turbocompresseur |
JP6117532B2 (ja) * | 2012-11-29 | 2017-04-19 | ダイハツ工業株式会社 | 排気ターボ過給機付き内燃機関 |
DE102012111558A1 (de) * | 2012-11-29 | 2014-06-05 | Firma IHI Charging Systems International GmbH | Regelvorrichtung für einen Abgasführungsabschnitt einer Turbine |
WO2014099328A1 (en) * | 2012-12-19 | 2014-06-26 | Borgwarner Inc. | Methods and structure for reducing losses in 90 degree waste gates for turbochargers |
JP6075923B2 (ja) * | 2013-03-28 | 2017-02-08 | 株式会社オティックス | ターボチャージャ |
US9169771B2 (en) * | 2013-09-20 | 2015-10-27 | Ford Global Technologies, Llc | Wastegate valve position correction |
US9988974B2 (en) | 2013-10-09 | 2018-06-05 | Borgwarner Inc. | Method of controlling wastegate flow using port side wall contour |
US9376930B2 (en) * | 2013-10-30 | 2016-06-28 | Hyundai Motor Company | Waste gate valve |
WO2015097786A1 (ja) * | 2013-12-25 | 2015-07-02 | 三菱重工業株式会社 | ウェイストゲートバルブ装置 |
JP5929889B2 (ja) * | 2013-12-26 | 2016-06-08 | トヨタ自動車株式会社 | 過給機 |
EP2915977B1 (en) * | 2014-03-06 | 2018-10-10 | Honeywell International Inc. | Turbine wastegate |
FR3018852B1 (fr) * | 2014-03-20 | 2018-04-27 | Renault S.A.S | Deflecteur pour ameliorer l'arrosage d'un catalyseur |
CN106662006B (zh) * | 2014-08-29 | 2019-03-29 | 株式会社Ihi | 增压器 |
US10344666B2 (en) * | 2014-09-01 | 2019-07-09 | Garrett Transportation I Inc. | Turbine wastegate |
JP6458676B2 (ja) | 2014-09-12 | 2019-01-30 | 株式会社デンソー | バルブ装置 |
NL1040955B1 (en) * | 2014-09-18 | 2016-09-29 | Mitsubishi Turbocharger And Engine Europe B V | Waste gate valve. |
US9657636B2 (en) | 2014-10-31 | 2017-05-23 | Ford Global Technologies, Llc | Wastegate assembly in a turbine |
US10047760B2 (en) | 2014-11-26 | 2018-08-14 | Honeywell International Inc. | Turbine wastegate plug |
KR101655616B1 (ko) * | 2014-12-15 | 2016-09-08 | 현대자동차주식회사 | 웨이스트 게이트 모듈 지지 장치 |
KR20160078019A (ko) * | 2014-12-24 | 2016-07-04 | 현대자동차주식회사 | 2단 터보 차저 시스템 및 2단 터보 차저 시스템의 제어방법 |
DE102015001763A1 (de) * | 2015-02-11 | 2016-08-11 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Wastegateventil-Stellglied |
DE202015101102U1 (de) | 2015-03-02 | 2015-03-24 | Ford Global Technologies, Llc | Bypassventil |
DE102015203678B3 (de) * | 2015-03-02 | 2016-06-16 | Ford Global Technologies, Llc | Bypassventil |
DE102015203679A1 (de) | 2015-03-02 | 2016-09-08 | Ford Global Technologies, Llc | Bypassventil |
DE102015209044A1 (de) * | 2015-05-18 | 2016-11-24 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Abgasturbolader |
DE102016204077A1 (de) * | 2015-05-18 | 2016-11-24 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Abgasturbolader |
US9856787B2 (en) | 2015-07-22 | 2018-01-02 | Hyundai Motor Company | Valve device of turbocharger |
JP6337872B2 (ja) * | 2015-11-24 | 2018-06-06 | トヨタ自動車株式会社 | 内燃機関の制御装置 |
CN105545383A (zh) * | 2015-12-14 | 2016-05-04 | 中国北方发动机研究所(天津) | 一种带有偏置异形调节阀的涡轮箱 |
DE102015122355A1 (de) * | 2015-12-21 | 2017-06-22 | Ihi Charging Systems International Gmbh | Abgasführungsabschnitt für einen Abgasturbolader und Verfahren zum Betreiben eines Abgasturboladers |
DE102015122351A1 (de) * | 2015-12-21 | 2017-06-22 | Ihi Charging Systems International Gmbh | Abgasführungsabschnitt für einen Abgasturbolader und Verfahren zum Betreiben eines Abgasturboladers |
EP3417159A1 (en) * | 2016-02-18 | 2018-12-26 | Borgwarner Inc. | Wastegate mechanism and method of making and using the same |
DE102016103145A1 (de) * | 2016-02-23 | 2017-08-24 | Ihi Charging Systems International Gmbh | Regelvorrichtung für einen Abgasturbolader |
DE102016112523A1 (de) * | 2016-07-07 | 2018-01-11 | Ihi Charging Systems International Gmbh | Regelvorrichtung für einen Abgasturbolader |
JP6827476B2 (ja) * | 2016-02-23 | 2021-02-10 | アイ・エイチ・アイ チャージング システムズ インターナショナル ゲーエムベーハー | 排気タービン式過給機のための制御装置 |
DE102016214840B4 (de) | 2016-08-10 | 2021-07-15 | Vitesco Technologies GmbH | Bypass-Ventil mit Ventilsitzschürze für einen Abgasturbolader und Abgasturbolader mit einem solchen Bypass-Ventil |
DE102016214843B4 (de) * | 2016-08-10 | 2020-06-18 | Continental Automotive Gmbh | Bypass-Ventil mit Klappenschürze für einen Abgasturbolader und Abgasturbolader mit einem solchen Bypass-Ventil |
CN110741144A (zh) * | 2017-07-21 | 2020-01-31 | Ihi供应系统国际有限责任公司 | 用于废气涡轮增压机的调节设备 |
KR101952032B1 (ko) * | 2017-09-27 | 2019-05-08 | 현대위아 주식회사 | 웨이스트 게이트 밸브장치 |
DE102017009452A1 (de) * | 2017-10-11 | 2019-04-11 | Daimler Ag | Verbrennungskraftmaschine für ein Kraftfahrzeug und Kraftfahrzeug mit einer solchen Verbrennungskraftmaschine |
KR102463202B1 (ko) * | 2017-11-29 | 2022-11-03 | 현대자동차 주식회사 | 냉각수 제어밸브 유닛, 및 이를 구비한 엔진 냉각 시스템 |
US11325104B2 (en) | 2017-12-07 | 2022-05-10 | Emp Biotech Gmbh | System and method of applied radial technology chromatography |
CN108561568A (zh) * | 2018-04-10 | 2018-09-21 | 中国北方发动机研究所(天津) | 一种多截面混合调节阀阀芯结构 |
CN108548005A (zh) * | 2018-04-10 | 2018-09-18 | 中国北方发动机研究所(天津) | 一种直旋转体调节阀阀芯结构 |
CN108591494B (zh) * | 2018-04-10 | 2020-04-10 | 中国北方发动机研究所(天津) | 一种多截面混合调节阀阀芯设计方法 |
CN108591604A (zh) * | 2018-04-10 | 2018-09-28 | 中国北方发动机研究所(天津) | 一种直旋转体调节阀阀芯设计方法 |
US10598082B2 (en) | 2018-08-25 | 2020-03-24 | Garrett Transportation I Inc. | Turbine wastegate |
JP7135787B2 (ja) * | 2018-11-29 | 2022-09-13 | トヨタ自動車株式会社 | ターボチャージャ |
EP3696387B1 (en) | 2019-02-15 | 2021-09-29 | Borgwarner Inc. | Dual volute turbocharger and system including the same |
US11408333B2 (en) | 2019-02-15 | 2022-08-09 | Borgwarner Inc. | Valve assembly for a dual volute turbocharger and dual volute turbocharger including the same |
US11047294B2 (en) | 2019-02-15 | 2021-06-29 | Borgwarner Inc. | Method of controlling a valve of a dual volute turbocharger |
CN111577446A (zh) * | 2020-06-08 | 2020-08-25 | 常州环能涡轮动力股份有限公司 | 涡轮增压器 |
CN111927963B (zh) * | 2020-10-16 | 2020-12-22 | 宁波丰沃涡轮增压系统有限公司 | 一种增压器线性流量控制阀 |
KR20220061682A (ko) | 2020-11-06 | 2022-05-13 | 현대위아 주식회사 | 터보차저용 액츄에이터 작동 로드 |
JP7396254B2 (ja) | 2020-11-18 | 2023-12-12 | トヨタ自動車株式会社 | ターボチャージャ |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02131032U (ja) * | 1989-04-05 | 1990-10-30 | ||
JPH0590057U (ja) * | 1992-05-19 | 1993-12-07 | 日電工業株式会社 | ポペット弁 |
JP2009092026A (ja) | 2007-10-11 | 2009-04-30 | Mitsubishi Heavy Ind Ltd | 流体切換弁装置とこれを備えた排気ガス制御バルブ及びウェストゲートバルブ |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1650271B1 (de) * | 1966-11-25 | 1970-04-23 | Oederlin Cie Ag | Drosselventil mit einer Dichtung |
JPS5866115U (ja) * | 1981-10-30 | 1983-05-06 | 三菱自動車工業株式会社 | 過給機付エンジンの過給圧制御装置 |
JPS5962233U (ja) * | 1982-10-19 | 1984-04-24 | 日産ディーゼル工業株式会社 | 内燃機関の排気タ−ボチヤ−ジヤ装置 |
JPS6069331U (ja) * | 1983-10-20 | 1985-05-16 | トヨタ自動車株式会社 | タ−ボチヤ−ジヤ |
WO1993013304A1 (en) * | 1984-03-15 | 1993-07-08 | Norio Nakazawa | Variable capacity turbo-supercharger |
DE3435701A1 (de) * | 1984-09-28 | 1986-04-10 | Vdo Adolf Schindling Ag, 6000 Frankfurt | Vorrichtung zur regelung der leerlaufdrehzahl |
US5018495A (en) * | 1988-08-17 | 1991-05-28 | Colt Industries, Inc. | Automatic idle speed circuitry |
US5044604A (en) * | 1990-08-31 | 1991-09-03 | Topham Fred A | Valve plug having fluid directing grooves |
FR2736431B1 (fr) * | 1995-07-05 | 1997-10-03 | Schlumberger Ind Sa | Organe de coupure a clapet anti-feu pour compteur de gaz et compteur de gaz equipe d'un tel organe de coupure |
JP2000193007A (ja) * | 1998-12-22 | 2000-07-14 | Fukoku Co Ltd | 板バネ一体型コアおよびその製造方法 |
US6969048B2 (en) * | 2003-06-17 | 2005-11-29 | Siemens Aktiengesellschaft | Valve element for supplementary control valve device |
FR2892793B1 (fr) * | 2005-10-28 | 2008-02-08 | Valeo Sys Controle Moteur Sas | Vanne a clapet s'etendant en position d'ouverture au voisinage d'une paroi de conduit |
US7360362B2 (en) * | 2006-01-20 | 2008-04-22 | Honeywell International, Inc. | Two-stage turbocharger system with integrated exhaust manifold and bypass assembly |
-
2010
- 2010-03-01 JP JP2010044356A patent/JP2011179401A/ja active Pending
-
2011
- 2011-02-02 WO PCT/JP2011/052105 patent/WO2011108331A1/ja active Application Filing
- 2011-02-02 CN CN2011800026735A patent/CN102472159A/zh active Pending
- 2011-02-02 KR KR1020117031102A patent/KR20120014934A/ko not_active Application Discontinuation
- 2011-02-02 EP EP11750444A patent/EP2444626A1/en not_active Withdrawn
- 2011-02-02 US US13/384,773 patent/US20120312010A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02131032U (ja) * | 1989-04-05 | 1990-10-30 | ||
JPH0590057U (ja) * | 1992-05-19 | 1993-12-07 | 日電工業株式会社 | ポペット弁 |
JP2009092026A (ja) | 2007-10-11 | 2009-04-30 | Mitsubishi Heavy Ind Ltd | 流体切換弁装置とこれを備えた排気ガス制御バルブ及びウェストゲートバルブ |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20140108654A (ko) * | 2012-01-03 | 2014-09-12 | 콘티넨탈 오토모티브 게엠베하 | 자동차용 밸브 장치 |
EP2800887B1 (de) * | 2012-01-03 | 2018-04-18 | Continental Automotive GmbH | Ventilvorrichtung für ein kraftfahrzeug |
KR102030204B1 (ko) | 2012-01-03 | 2019-10-08 | 콘티넨탈 오토모티브 게엠베하 | 자동차용 밸브 장치 |
US10358986B2 (en) | 2012-01-03 | 2019-07-23 | Continental Automotive Gmbh | Valve device for a motor vehicle |
US10234038B2 (en) | 2012-02-28 | 2019-03-19 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Valve |
EP2821614A4 (en) * | 2012-02-28 | 2015-11-11 | Mitsubishi Heavy Ind Ltd | VALVE |
US8904785B2 (en) * | 2012-09-13 | 2014-12-09 | Honeywell International Inc. | Turbine wastegate |
US9010109B2 (en) | 2012-09-13 | 2015-04-21 | Honeywell International Inc. | Turbine wastegate |
CN104884760A (zh) * | 2013-04-15 | 2015-09-02 | 株式会社Ihi | 流量可变阀机构以及增压器 |
US10024229B2 (en) | 2013-04-15 | 2018-07-17 | Ihi Corporation | Variable-flow-rate valve mechanism and turbocharger |
US10851703B2 (en) | 2013-04-15 | 2020-12-01 | Ihi Corporation | Variable-flow-rate valve mechanism and turbocharger |
US11352944B2 (en) | 2013-04-15 | 2022-06-07 | Ihi Corporation | Variable-flow-rate valve mechanism and turbocharger |
JP2018162771A (ja) * | 2017-03-27 | 2018-10-18 | 三菱重工業株式会社 | 弁装置、タービンハウジング、排気タービン過給機及びエンジン |
Also Published As
Publication number | Publication date |
---|---|
US20120312010A1 (en) | 2012-12-13 |
CN102472159A (zh) | 2012-05-23 |
EP2444626A1 (en) | 2012-04-25 |
KR20120014934A (ko) | 2012-02-20 |
JP2011179401A (ja) | 2011-09-15 |
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