WO2016031565A1 - 流量可変バルブ機構及び過給機 - Google Patents
流量可変バルブ機構及び過給機 Download PDFInfo
- Publication number
- WO2016031565A1 WO2016031565A1 PCT/JP2015/072777 JP2015072777W WO2016031565A1 WO 2016031565 A1 WO2016031565 A1 WO 2016031565A1 JP 2015072777 W JP2015072777 W JP 2015072777W WO 2016031565 A1 WO2016031565 A1 WO 2016031565A1
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- WIPO (PCT)
- Prior art keywords
- tip
- link member
- actuating rod
- valve mechanism
- flow rate
- Prior art date
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Classifications
-
- 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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- 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 flow rate variable valve mechanism for opening and closing an opening of a gas flow rate variable passage for adjusting the flow rate of exhaust gas supplied to a turbine impeller side in a turbocharger such as a vehicle turbocharger and a turbocharger .
- a bypass passage is usually formed inside the turbine housing of the vehicular turbocharger. A portion of the exhaust gas flows through this bypass passage to bypass the turbine impeller.
- waste gate valves are provided at appropriate positions of the turbine housing for opening and closing the opening of the bypass passage.
- the bypass passage is one of the gas flow rate variable passages for adjusting the flow rate of the exhaust gas supplied to the turbine impeller side, and the waste gate valve is a flow rate variable valve for opening and closing the opening of the gas flow rate variable passage. It is one of the mechanisms.
- the waste gate valve includes a stem (rotary shaft) rotatably supported by the turbine housing, a valve that can be abutted on and separated from the valve seat on the opening side of the bypass passage, and a mounting member that connects the stem and the valve Equipped with
- the stem is rotatably supported in forward and reverse directions in a support hole formed through the outer wall of the turbine housing.
- the proximal end (one end) of the stem projects out of the turbine housing.
- the proximal end of the mounting member is integrally connected to the distal end of the stem.
- a valve is provided at the tip of the mounting member. The valve can be abutted on and separated from the valve seat on the opening side of the bypass passage.
- the proximal end (one end) of the link member is integrally connected to the proximal end of the stem.
- the valve swings in the forward or reverse direction (opening direction or closing direction) via the stem and the mounting member.
- An actuator is disposed on the outer wall of the compressor housing in the vehicle turbocharger.
- the actuator swings the link member about the axis of the stem.
- the actuator is provided with an actuating rod movable in its axial direction (the axial direction of the actuating rod, in other words, the axial direction of the actuator).
- the tip of the actuating rod is rotatably connected to the tip (the other end) of the link member.
- Patent Literature 1 and Patent Literature 2 show techniques related to the present invention.
- an object of the present invention is to provide a flow rate variable valve mechanism and a supercharger which can solve the above-mentioned problem.
- a gas flow rate variable passage for adjusting the flow rate of exhaust gas supplied to the turbine impeller side is included in a turbine housing or a connection body connected in communication with the turbine housing.
- a variable flow valve mechanism used in a supercharger to open and close an opening of the variable gas flow passage, wherein a stem supported on the outer wall of the turbine housing or the connection body, and a base end are integrated with the stem
- a valve provided at the tip of the mounting member for opening and closing the opening of the gas flow rate variable passage, and a base end integrally connected to the base end of the stem
- a link member, and an operating rod rotatably connected to a distal end of the link member and swinging the link member in the forward and reverse directions about the axis of the stem;
- the gist of the present invention is to
- turbocharger is intended to include not only a single-stage turbocharger but also multiple-stage (low-pressure and high-pressure) turbochargers.
- a connected body connected in communication with the turbine housing is meant to include a pipe, a manifold, a casing, etc. connected in a state of being communicated with the gas inlet or the gas outlet of the turbine housing.
- variable gas flow rate passage is meant to include a bypass passage or the like for bypassing a part of exhaust gas to the turbine impeller, and “variable flow rate valve mechanism” refers to opening and closing the opening of the bypass passage. Includes waste gate valves, etc.
- “provided” means that it was indirectly provided via another member other than directly provided.
- "Supported” is meant to include indirectly supported via another member, in addition to directly supported.
- the term “connected” is meant to include, in addition to being directly connected, indirectly connected via another member.
- biasing member is meant to include spring members such as disc springs, wave washers, coil springs, rubber members made of heat resistant rubber, damping alloy members made of damping alloy, and the like.
- a second aspect of the present invention is a supercharger for supercharging air supplied to an engine using energy of exhaust gas from the engine, wherein the flow rate variable valve mechanism according to the first aspect Make it a summary.
- the present invention it is possible to suppress the vibration of the link member and the operating rod due to the pulsation of the exhaust gas from the engine side. Therefore, chattering noise from the flow rate variable valve mechanism can be reduced, and the quietness of the flow rate variable valve mechanism can be improved.
- FIG. 1 is a front view of a turbocharger according to an embodiment of the present invention.
- FIG. 2 is a cross-sectional view taken along the line II-II in FIG.
- FIG. 3 is a cross-sectional view of the diaphragm actuator.
- FIG. 3 also shows the link member.
- FIG. 4 (a) shows a disc spring provided between the tip of the link member and the tip of the actuating rod
- FIG. 4 (b) shows the IVB-IVB line in FIG. 4 (a).
- FIG. 5 (a) is a view showing another aspect in which a disc spring is provided between the tip of the link member and the tip of the actuating rod
- FIG. 5 (b) is a diagram showing VB- in FIG. 5 (a).
- FIG. 6 (a) is a cross-sectional view showing how a wave washer is provided between the tip of the link member and the tip of the actuating rod
- FIG. 6 (b) shows the tip of the link member and the actuating rod.
- FIG. 7 (a) is a cross-sectional view showing how a rubber member is provided between the tip of the link member and the tip of the actuating rod
- FIG. 7 (b) shows the tip of the link member and the actuating rod.
- FIG. 8 (a) is a view showing a spring clip provided between the tip of the link member and the tip of the actuating rod
- FIG. 8 (b) is a line VIIIB-VIIIB in FIG. 8 (a). It is sectional drawing along.
- FIG. 9 is a perspective view of the leaf spring shown in FIGS. 8 (a) and 8 (b).
- 10 (a) and 10 (b) are cross-sectional views showing another aspect in which a disc spring is provided between the tip of the link member and the tip of the actuating rod.
- 11 (a) and 11 (b) are cross-sectional views showing how a leaf spring is provided between the tip of the link member and the tip of the actuating rod.
- FIG. 12 (a) and 12 (b) are figures which show a mode that the torsion spring was provided between the front-end
- FIG. 13 is a front sectional view of a turbocharger according to an embodiment of the present invention.
- FIGS. 1 to 13 In the drawings, “L” indicates the left direction, and “R” indicates the right direction.
- the turbocharger 1 according to the embodiment of the present invention is, for example, for a vehicle. As shown in FIGS. 1 and 13, the supercharger 1 supercharges (compresses) air supplied to the engine using energy of exhaust gas from the engine (not shown).
- the turbocharger 1 includes a bearing housing 3.
- a pair of radial bearings 5, 5 and a pair of thrust bearings 7, 7 are provided. These bearings rotatably support a rotor shaft (turbine shaft) 9 extending in the left-right direction.
- the rotor shaft 9 is rotatably provided via the plurality of bearings 5 and 7.
- a compressor housing 11 is provided on the right side of the bearing housing 3.
- a compressor impeller 13 is rotatably provided.
- the compressor impeller 13 is concentrically and integrally connected to the right end portion of the rotor shaft 9, and compresses air using centrifugal force.
- An air inlet (air introduction passage) 15 for introducing air is formed on the inlet side (upstream side in the main flow direction of the air) of the compressor impeller 13 in the compressor housing 11.
- the air inlet 15 is connected to an air cleaner (not shown) for purifying the air.
- a diffuser flow path 17 is provided on the outlet side (downstream side in the main flow direction of the air) of the compressor impeller 13 between the bearing housing 3 and the compressor housing 11.
- the diffuser flow path 17 is annularly formed, and pressurizes the compressed air.
- a compressor scroll channel 19 is provided inside the compressor housing 11.
- the compressor scroll passage 19 is formed in a spiral shape so as to surround the compressor impeller 13 and is in communication with the diffuser passage 17.
- an air exhaust port (air exhaust passage) 21 for exhausting the compressed air is formed.
- the air discharge port 21 communicates with the compressor scroll flow path 19 and is connected to an air supply manifold (not shown) of the engine.
- a turbine housing 23 is provided on the left side of the bearing housing 3. Further, a turbine impeller 25 is rotatably provided in the turbine housing 23. The turbine impeller 25 is concentrically and integrally connected to the left end portion of the rotor shaft 9, and generates rotational force (rotational torque) using pressure energy of exhaust gas.
- a gas inlet (gas introduction passage) 27 for introducing exhaust gas is formed at an appropriate position on the outer wall of the turbine housing 23.
- the gas inlet 27 is connected to an exhaust manifold (not shown) of the engine.
- a turbine scroll flow passage 29 is formed in a spiral shape on the inlet side (upstream side in the main flow direction of the exhaust gas) of the turbine impeller 25 inside the turbine housing 23.
- a gas discharge port (gas discharge passage) 31 for discharging the exhaust gas is formed on the outlet side (downstream side in the main flow direction of the exhaust gas) of the turbine impeller 25 in the turbine housing 23.
- the gas discharge port 31 is connected to an exhaust gas purification device (not shown) using a catalyst via a connection pipe (not shown) or the like.
- a bypass passage 33 is formed in the turbine housing 23. A part of the exhaust gas introduced from the gas inlet 27 flows through the bypass passage 33 and is led out to the gas outlet 31 side. That is, part of the exhaust gas bypasses the turbine impeller 25 by the bypass passage 33.
- the bypass passage 33 is a so-called variable gas flow passage for adjusting the flow rate of the exhaust gas supplied to the turbine impeller 25 side, and has the same configuration as a known bypass passage shown in, for example, JP 2013-185552A. doing.
- a waste gate valve 35 is provided at an appropriate position of the turbine housing 23.
- the waste gate valve 35 is configured to open and close the opening of the bypass passage 33. That is, the waste gate valve 35 is a so-called variable flow valve mechanism.
- the waste gate valve 35 connects a stem (rotational shaft) 39 rotatably supported by the turbine housing 23, a valve 45 for opening and closing the opening (valve seat 47) of the bypass passage 33, the stem 39 and the valve 45 And a mounting member 43.
- the stem 39 is rotatably provided in a forward direction and a reverse direction in a support hole 37 formed in the outer wall of the turbine housing 23 through a bush 41.
- a proximal end (one end, a first end) of the stem 39 protrudes to the outside of the turbine housing 23.
- the proximal end of the mounting member 43 is integrally connected to the distal end (the other end, the second end) of the stem 39.
- a mounting hole (not shown) having a shape having a width across flats or a circular shape is formed at the tip of the mounting member 43 so as to penetrate the tip.
- the proximal end of the attachment member 43 is integrally connected to the distal end of the stem 39 by, for example, fillet welding, TIG welding, laser beam welding, caulking, or the like.
- a valve 45 is fitted in the mounting hole of the mounting member 43.
- the valve 45 is allowed to play with the mounting member 43 (including tilting and fine movement).
- the valve 45 is integrally formed at the central portion of the valve main body 49 and the valve main body 49 that can be abutted on and separated from the valve seat 47 on the opening side of the bypass passage 33 and fitted in the mounting hole of the mounting member 43
- the valve shaft 51 is provided. As described above, since the play (back) of the valve 45 with respect to the mounting member 43 is allowed, the adhesion of the valve main body 49 to the valve seat 47 is secured. Further, an annular stopper (washer) 53 is integrally provided at the tip of the valve shaft 51.
- the clasp (washer) 53 prevents the valve 45 from coming off with respect to the mounting member 43.
- the stopper 53 is integrally provided at the tip of the valve shaft 51 by, for example, fillet welding, TIG welding, laser beam welding, caulking or the like.
- valve shaft 51 is integrally formed at the central portion of the valve main body 49 and the detent 53 being integrally provided at the distal end portion of the valve shaft 51
- the valve shaft 51 is integrally formed at the central portion of the valve main body 49.
- a detent 53 may be formed integrally with the tip of the valve stem 51.
- the valve shaft 51 is integrally provided at a central portion of the valve main body 49 by, for example, caulking, fillet welding, TIG welding, or laser beam welding.
- the proximal end (one end) of the link member (link plate) 55 is integrally connected to the proximal end of the stem 39.
- the valve 45 swings in the forward and reverse directions (opening direction and closing direction) via the stem 39 and the mounting member 43.
- the base end of the link member 55 is integrally connected to the base end of the stem 39 by, for example, fillet welding, TIG welding, laser beam welding, caulking, or the like.
- an actuator 57 is provided on the outer wall of the compressor housing 11 via a bracket 59.
- the actuator 57 is, for example, a diaphragm-type actuator as described below, and swings the link member 55 around the axis of the stem 39 in the forward and reverse directions.
- the actuator 57 includes a cylindrical actuator body 61. Further, in the actuator body 61, a diaphragm 63 is provided so as to separate the pressure chamber 65 and the atmosphere chamber 67.
- the pressure chamber 65 is a chamber (space) to which a positive pressure from the air outlet 21 as a pressure source is applied.
- the atmosphere chamber 67 is a chamber in communication with the atmosphere.
- a first retainer plate 69 is provided on the surface of the diaphragm 63 on the pressure chamber 65 side.
- a second retainer plate 71 is provided on the surface of the diaphragm 63 on the atmosphere chamber 67 side.
- a return spring (coil spring) 73 is provided in the atmosphere chamber 67. The return spring 73 biases the diaphragm 63 to the pressure chamber 65 side.
- An actuating rod 75 is provided on the actuator body 61 via a bush 77.
- the actuating rod 75 protrudes outward from the actuator body 61 and is movable in the axial direction.
- the proximal end of the actuating rod 75 is integrally connected to the central portion of the diaphragm 63.
- the tip of the actuating rod 75 has a flat plate shape, and is rotatably (swayably) connected to the tip of the link member 55. Further, in order to rotatably connect the tip of the actuating rod 75 and the tip of the link member 55, a connecting pin 79 having a circular cross section is integrally provided at the tip of the actuating rod 75.
- connection pin 79 for inserting (engaging) the connection pin 79 is formed through the tip of the link member 55.
- the connecting pin 79 is provided with a snap ring 83 for preventing the link member 55 from coming off with respect to the actuating rod 75.
- the connecting pin 79 is integrally provided at the tip of the operating rod 75 by, for example, caulking, fillet welding, TIG welding, or laser beam welding.
- the cross-sectional shape of the connection pin 79 and the shape of the pin hole 81 in the present embodiment are circular. However, these shapes may be changed to any shape such as a square shape as long as the connecting pin 79 can rotate relative to the pin hole 81.
- a disc spring 85 is provided as the (first biasing member). That is, the disc spring 85 biases the distal ends of the link member 55 and the distal end of the actuating rod 75 such that the distal ends thereof are separated from each other in the axial direction of the actuating rod 75.
- the disc spring 85 is made of, for example, a heat-resistant metal such as a Ni-based alloy, a Ni--Co-based alloy, or stainless steel. The tip of the actuating rod 75 is inserted into the disc spring 85.
- a receiving seat (a washer) 87 is provided at the tip of the actuating rod 75 via a snap ring 89.
- the receiving seat 87 supports (holds) one end (right end) of the disc spring 85.
- the biasing force (elastic force) of the disc spring 85 By the biasing force (elastic force) of the disc spring 85, the inner circumferential surface of the pin hole 81 of the link member 55 is in pressure contact with the outer circumferential surface of the connection pin 79 locally.
- the term “pressure contact” means contact while being pressed.
- the biasing direction of the disc spring 85 coincides with the axial direction of the actuating rod 75.
- the biasing direction may be inclined with respect to the axial direction of the actuating rod 75 within the range where the effects of the present invention can be exhibited.
- another receiving seat for supporting the other end (left end) of the disc spring 85 may be provided at the tip of the actuating rod 75.
- the connecting pin 91 is integrally provided at the tip of the link member 55 by caulking or the like, and the connecting pin 91 is inserted through the tip of the actuating rod 75 Pin holes 93 for fitting) may be formed through.
- a retaining ring 95 is provided on the connecting pin 91 to prevent the actuating rod 75 from disengaging from the link member 55. Accordingly, the inner peripheral surface of the pin hole 93 of the actuating rod 75 is locally pressed against the outer peripheral surface of the connection pin 91 by the biasing force (elastic force) of the disc spring 85.
- Fig.6 (a) you may use the wave washer 97 which consists of heat-resistant alloys as an above-mentioned biasing member.
- a coil spring 99 made of a heat-resistant alloy may be used as the biasing member.
- Fig.7 (a) you may use the cyclic
- the rubber member 101 is made of, for example, a heat resistant rubber such as silicone rubber and chloroprene rubber.
- the inner circumferential surface of the pin hole 81 of the link member 55 is in pressure contact with the outer circumferential surface of the connection pin 79 locally by the biasing force (elastic force) of the wave washer 97 or the like.
- an annular damping alloy member 103 may be used as the above-mentioned biasing member.
- the damping alloy member 103 is made of, for example, a damping alloy such as a Mg-based alloy, a Ti-Ni-based alloy, an Al-Zn-based alloy, a Mn-Cn-based alloy, or a Cu-Al-Mn-based alloy.
- Damping alloy member 103 may have a hollow structure.
- the damping alloy member 103 may be filled with air or oil, or an elastic member such as rubber may be interposed.
- the inner peripheral surface of the pin hole 81 of the link member 55 is locally in pressure contact with the outer peripheral surface of the connection pin 79 by the biasing force of the damping alloy member 103.
- the spring clip 105 may be used as the above-mentioned biasing member.
- the spring clip 105 has a bent portion 107 elastically deformable in the axial direction of the actuating rod 75 at one end.
- the bent portion 107 is sandwiched by the link member 55 and the receiving seat 87.
- a slit (notch) 109 for fitting the actuating rod 75 is formed at the center of the spring clip 105.
- a protrusion (not shown) for retaining is formed on the inlet side of the slit 109.
- the inner circumferential surface of the pin hole 81 of the link member 55 is in pressure contact with the outer circumferential surface of the connection pin 79 locally by the biasing force (elastic force) of the bent portion 107 of the spring clip 105.
- an insertion hole (not shown) for inserting the actuating rod 75 may be formed.
- the biasing member such as the disc spring 85 and the receiving seat 87 may be disposed on the left side of the tip of the link member 55 instead of the right side of the tip of the link member 55.
- a disc spring 111 may be used as a biasing member (second biasing member).
- the disc spring 111 biases the tip of the link member 55 and the tip of the actuating rod 75 in opposite directions in the axial direction of the connecting pin 79 (or 91).
- the above-mentioned wave washer, coil spring, annular damping alloy member or spring clip may be used instead of the disc spring 111.
- the connection pin 79 (or 91) is inserted inside the biasing member such as the disc spring 111 or the like.
- the disc spring The link member 55 is brought into pressure contact with the retaining ring 83 by the biasing force (elastic force) of the biasing member 111 or the like.
- FIG. 10 (b) in the state where the connecting pin 91 is integrally provided at the tip of the link member 55 and the pin hole 93 is formed through the tip of the actuating rod 75, The actuating rod 75 is brought into pressure contact with the retaining ring 95 by the biasing force (elastic force) of the biasing member.
- the biasing direction of the biasing member such as the disc spring 111 is the axial direction of the connecting pin 79 (or 91)
- the connecting pin 79 (or 91) is within the range where the effects of the present invention can be exhibited. It may be inclined with respect to the axial direction of.
- a leaf spring 113 may be used instead of using a biasing member such as a disc spring 111 or the like.
- the plate spring 113 is formed in a strip shape, has a folded portion 113t formed by press molding, for example, in the middle in the longitudinal direction, and has a U-shape in a side view.
- a first insertion hole 115 for inserting the connection pin 79 is formed in a penetrating manner.
- a second insertion hole 117 for inserting the connection pin 79 is formed in a penetrating manner.
- one end of the plate spring 113 is in pressure contact with the tip of the link member 55 by the elastic force of the plate spring 113, and the other end of the plate spring 113 is the tip of the operating rod 75 by caulking the connection pin 79 or the like. It is fixed to the department. Further, instead of the other end of the plate spring 113 being fixed to the end of the actuating rod 75, as shown in FIG. 11 (b), it is in pressure contact with the end of the actuating rod 75 by the elastic force of the plate spring 113. May be Here, the link member 55 is in pressure contact with the retaining ring 83 by the biasing force (elastic force) of the plate spring 113.
- the plate spring 113 has a U-shape in a side view
- the shape of the plate spring 113 (a shape in a side view ) May be changed to any shape.
- a U-shaped first cutout (not shown) for inserting the connecting pin 79 may be formed.
- a U-shaped second notch (not shown) for inserting the connecting pin 79 may be formed.
- a torsion spring 119 may be used which biases the tip of the link member 55 and the tip of the actuating rod 75 in a direction toward or away from each other.
- the torsion spring 119 includes a coil portion 121 disposed on the connection pin 79, and a first arm portion provided to project from the coil portion 121 and having a distal end portion locked or fixed to a part of the link member 55.
- FIG. 12 (a) shows a state in which the distal end portion of the link member 55 and the distal end portion of the actuating rod 75 are urged in a direction approaching by the torsion spring 119
- FIG. 12 (b) is a torsion.
- a state is shown in which the tip end of the link member 55 and the tip end of the actuating rod 75 are biased in a direction away from each other by the spring 119.
- the exhaust gas introduced from the gas introduction port 27 flows from the inlet side to the outlet side of the turbine impeller 25 via the turbine scroll flow path 29, whereby torque (rotational torque) is calculated using pressure energy of the exhaust gas.
- the rotor shaft 9 and the compressor impeller 13 can be rotated integrally with the turbine impeller 25.
- the air introduced from the air inlet 15 can be compressed and discharged from the air outlet 21 via the diffuser passage 17 and the compressor scroll passage 19, and the air supplied to the engine can be supercharged. can do.
- the supercharging pressure pressure of the air discharge port 21
- a positive pressure is applied to the pressure chamber 65 from the air discharge port 21 as a pressure source
- the operating rod 75 moves to one side (left direction) in the axial direction (axial direction of the actuating rod 75) to swing the link member 55 in the forward direction (clockwise direction in FIGS. 1 and 3).
- the valve 45 swings in the forward direction (opening direction) via the stem 39 and the attachment member 43, and the opening of the bypass passage 33 can be opened.
- a part of the exhaust gas introduced from the gas inlet 27 can bypass the turbine impeller 25 to reduce the flow rate of the exhaust gas supplied to the turbine impeller 25 side.
- the charging pressure becomes less than the set pressure
- the actuation rod of the return spring 73 75 moves to the other side (right direction) in the axial direction to swing the link member 55 in the reverse direction (counterclockwise direction in FIGS. 1 and 3).
- the valve 45 swings in the reverse direction (closing direction) via the stem 39 and the attachment member 43, and the opening of the bypass passage 33 can be closed. Therefore, the flow of the exhaust gas in the bypass passage 33 can be shut off to increase the flow rate of the exhaust gas supplied to the turbine impeller 25 side.
- the distal end of the link member 55 and the distal end of the actuating rod 75 are biased in opposite directions by the biasing member such as the disc spring 85 or the like, pulsation (pulsating pressure) of exhaust gas from the engine side or a diaphragm actuator Even if pulsation or the like occurs from the side 57, the vibration of the link member 55 and the actuating rod 75 due to the pulsation or the like can be reduced.
- the biasing direction of the biasing member such as the disc spring 85 is the axial direction of the actuating rod 75, exhaust from the engine side is performed while the biasing force of the biasing member such as the disc spring 85 is stabilized by the receiving seat 87.
- Vibration of the link member 55 and the like due to pulsation of gas and pulsation from the side of the diaphragm actuator 57 can be effectively suppressed.
- the biasing direction of the biasing member such as the disc spring 111 or the like is the axial direction of the connection pin 79 (or 91)
- the vibration of the link member 55 or the like due to the pulsation of exhaust gas from the engine side is effectively suppressed. be able to.
- the vibration of the valve 45 due to the pulsation or the like can be suppressed as a result.
- vibration of the link member 55 and the operating rod 75 due to pulsation of exhaust gas from the engine side can be suppressed, and chattering noise from the waste gate valve 35 (contact noise due to vibration) Can be reduced to improve the quietness of the waste gate valve 35.
- chattering noise from the waste gate valve 35 contact noise due to vibration
- the wear of the outer peripheral surface of the connection pin 79 (or 91) and the wear of the inner peripheral surface of the pin hole 81 of the link member 55 (or the pin hole 93 of the actuating rod 75) can be reduced.
- waste gate valve 35 for opening and closing the bypass passage 33 at an appropriate position of the turbine housing 23 at an appropriate position of the turbine housing 23.
- exhaust is provided at an appropriate position of an exhaust manifold (not shown) connected in communication with the gas inlet 27 of the turbine housing 23.
- a waste gate valve (not shown) may be provided to open and close the opening of a bypass passage (not shown) formed in the manifold.
- a negative pressure may be applied to the pressure chamber 65 from another pressure source (not shown) on the engine side.
- the return spring 73 is provided in the pressure chamber 65.
- the actuator body 61 may have another pressure chamber (not shown) to which a negative pressure can be applied from another pressure source (not shown) such as a negative pressure pump instead of the atmosphere chamber 67.
- an electrically controlled electric actuator (not shown) or a hydraulic actuator (not shown) by hydraulic drive may be used.
- at least one of the tip of the link member 55 and the tip of the actuating rod 75 may have a bifurcated shape.
- the flow rate variable valve mechanism of the present invention is not limited to the above-described waste gate valve 35, and, for example, as shown in JP-A-61-33923 and JP-A-2001-263078, a turbine housing ( Switching valve mechanism (not shown) that switches between the supply state and the supply stop state of the exhaust gas with respect to any of the turbine scroll flow paths (not shown) formed in the interior) Is also applicable.
- the flow rate variable valve mechanism according to the present application is, for example, disclosed in JP-A-2010-209688, JP-A-2011-106358, etc.
- the turbine housing of any one of the stages of turbine housings not shown.
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Abstract
Description
Claims (8)
- タービンハウジング又は前記タービンハウジングに連通した状態で接続した接続体の内部に、タービンインペラ側へ供給される排気ガスの流量を調整するためのガス流量可変通路を含む過給機に用いられ、前記ガス流量可変通路の開口部を開閉する流量可変バルブ機構であって、
前記タービンハウジング又は前記接続体の外壁に支持されたステムと、
基端部が前記ステムに一体的に連結された取付部材と、
前記取付部材の先端部に設けられ、前記ガス流量可変通路の開口部を開閉するバルブと、
基端部が前記ステムの基端部に一体的に連結されたリンク部材と、
先端部が前記リンク部材の先端部に回転可能に連結され、前記リンク部材を前記ステムの軸心周りに正方向及び逆方向へ揺動させるための作動ロッドと、
前記リンク部材の先端部又は前記作動ロッドの先端部に形成されるピン穴と、
前記作動ロッドの先端部又は前記リンク部材の先端部に設けられ、前記ピン穴に挿通される連結ピンと、
前記リンク部材の先端部と前記作動ロッドの先端部を互いに反対方向へ付勢する付勢部材と
を具備することを特徴とする流量可変バルブ機構。 - 前記作動ロッドの先端部に設けられ、前記付勢部材の端部を支持する受け座を更に具備することを特徴とする請求項1に記載の流量可変バルブ機構。
- 前記付勢部材の付勢方向は、前記作動ロッドの軸方向であることを特徴とする請求項1又は請求項2に記載の流量可変バルブ機構。
- 前記付勢部材によって、前記ピン穴の内周面は、前記連結ピンの外周面に局所的に圧接することを特徴とする請求項3に記載の流量可変バルブ機構。
- 前記付勢部材の付勢方向は、前記連結ピンの軸方向であることを特徴とする請求項1に記載の流量可変バルブ機構。
- 前記付勢部材は、内側に前記連結ピンが位置する穴を有し、且つ、前記作動ロッドの先端部と前記リンク部材の先端部との間に位置することを特徴とする請求項5に記載の流量可変バルブ機構。
- 前記付勢部材は板バネであり、前記板バネの両端部には、内側に前記連結ピンが位置する穴或いは切欠が形成されていることを特徴とする請求項5に記載の流量可変バルブ機構。
- エンジンからの排気ガスのエネルギーを利用して、前記エンジンに供給される空気を過給する過給機において、
請求項1から請求項7のうちのいずれか一項に記載の流量可変バルブ機構を具備したことを特徴とする過給機。
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CN106605052B (zh) | 2019-03-15 |
US10487725B2 (en) | 2019-11-26 |
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US20170145911A1 (en) | 2017-05-25 |
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