WO2017150543A1 - 過給機および内燃機関 - Google Patents
過給機および内燃機関 Download PDFInfo
- Publication number
- WO2017150543A1 WO2017150543A1 PCT/JP2017/007826 JP2017007826W WO2017150543A1 WO 2017150543 A1 WO2017150543 A1 WO 2017150543A1 JP 2017007826 W JP2017007826 W JP 2017007826W WO 2017150543 A1 WO2017150543 A1 WO 2017150543A1
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- WIPO (PCT)
- Prior art keywords
- port
- introduction
- flow
- introduction port
- exhaust gas
- Prior art date
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- 238000002485 combustion reaction Methods 0.000 title claims description 12
- 230000002093 peripheral effect Effects 0.000 claims description 19
- 238000009795 derivation Methods 0.000 claims description 5
- 239000002699 waste material Substances 0.000 description 99
- 230000007246 mechanism Effects 0.000 description 10
- 239000003054 catalyst Substances 0.000 description 8
- 230000004048 modification Effects 0.000 description 6
- 238000012986 modification Methods 0.000 description 6
- 230000004913 activation Effects 0.000 description 4
- 230000004308 accommodation Effects 0.000 description 3
- 238000007599 discharging Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Images
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
- 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
- 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
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/148—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of rotatable members, e.g. butterfly valves
-
- 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
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
-
- 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
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
- F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
-
- 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
- F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
- F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
-
- 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
- F02B2037/122—Control of rotational speed of the pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
- F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
- F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
- F02D9/1005—Details of the flap
- F02D9/1025—Details of the flap the rotation axis of the flap being off-set from the flap center axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
- F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
- F02D9/12—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having slidably-mounted valve members; having valve members movable longitudinally of conduit
- F02D9/16—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having slidably-mounted valve members; having valve members movable longitudinally of conduit the members being rotatable
-
- 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 turbocharger and an internal combustion engine.
- a turbocharger which is a turbocharger that supercharges an engine, uses exhaust gas to drive a turbine.
- the turbocharger has a wastegate mechanism that diverts the exhaust gas to prevent damage due to the supercharging pressure becoming too high.
- the waste gate mechanism can allow the exhaust gas to flow out of the system without passing through the turbine. Accordingly, the flow rate of the exhaust gas flowing into the turbine can be reduced according to the opening degree of the waste gate valve (see, for example, Patent Document 1).
- a flap type waste gate valve is often used.
- One aspect of the present invention is in view of the above-described circumstances, and it is an object of the present invention to provide a turbocharger and an internal combustion engine that can efficiently use exhaust gas.
- One aspect of the present invention is a first introduction portion having a first flow passage for guiding the exhaust gas from a first exhaust introduction passage leading to a turbine driven by the exhaust gas, and the second exhaust introduction passage leading to the turbine 1.
- a second introduction unit having a second flow path for introducing exhaust gas, a chamber into which the exhaust gas is introduced through the first flow path and the second flow path, and the exhaust gas in the chamber being introduced out of the system 1
- a lead-out portion having a plurality of lead-out flow paths, and a valve member accommodated in the chamber, wherein the chamber is provided with a first introduction port communicating with the first flow path, and a chamber communicating with the second flow path
- An inlet port and one or more outlet ports leading to the outlet channel, and a main flow space in which gas can flow is secured on the main surface side of the valve member in the chamber, the valve The member is centered on the axis
- the first inlet port, the second inlet port, and the outlet port can be opened and closed according to the rotational position around the
- valve member can communicate the first introduction port and the second introduction port through the main flow space.
- valve member can communicate the first introduction port and the second introduction port with the lead-out port through the main flow space.
- the chamber has an inner circumferential surface which is a cylindrical surface whose central axis is the axis, and the valve member is an outer periphery which is a cylindrical surface whose central axis is the axial line as a back surface opposite to the main surface
- a notch is formed on the outer peripheral surface of the valve member to form a secondary flow space through which gas can flow, and the notch is any of the first introduction port and the second introduction port. It is preferable that one side and the outlet port can be communicated through the sub circulation space.
- the valve member causes one of the first inlet port and the second inlet port to communicate with the outlet port through the main flow space, and the other of the first inlet port and the second inlet port. It is preferable that the communication port and the outlet port can communicate with each other through the auxiliary flow space.
- the plurality of lead-out ports include a first lead-out port and a second lead-out port, and the valve member is configured to main one of the first lead-in port and the second lead-in port and the first lead-out port. It is preferable that communication is made through the circulation space, and that the other of the first introduction port and the second introduction port can be communicated with the second lead-out port through the sub circulation space.
- a guide convex portion is formed on the main surface of the valve member to adjust the flow resistance of the gas flowing from at least one of the first introduction port and the second introduction port to the discharge port. It may be
- the supercharger adjusts the flow rate of gas from the port by covering at least one of the first introduction port and the second introduction port on the main surface of the valve member
- the convex part may be formed.
- a first introduction portion having a first flow path for introducing exhaust gas
- a second introduction portion having a second flow path for introducing exhaust gas, the first flow path and the second flow path
- a main flow space through which gas can flow is secured on the main surface side of the valve member, and the valve member is rotatable about an axis, and the first introduction port according to the rotational position around the axis.
- Said second introduction port and said derivation port An openable and closable, wherein the first inlet port, two or more ports which opens out of the second inlet port and said outlet port is communicable through the main circulation space, to provide an internal combustion engine.
- exhaust gas can be efficiently used.
- the turbocharger according to the embodiment is mounted, for example, on a vehicle such as a car having a reciprocating engine (hereinafter simply referred to as an engine) as a drive source as an internal combustion engine.
- the supercharger is a so-called turbocharger that compresses intake air by using exhaust gas from an engine.
- the engine has one or more (e.g. four) cylinders.
- FIG. 1 is a view showing a basic structure of a turbocharger according to a first embodiment.
- the turbocharger 1 includes a compressor unit 2, a turbine unit 3, a bearing unit 4, and a wastegate mechanism 5 (rotary valve device).
- the compressor unit 2 compresses intake air introduced from an air cleaner (not shown) and feeds it to a cylinder 7 of the engine 6.
- the compressor unit 2 includes a compressor wheel 8 and a compressor housing 9.
- the compressor wheel 8 rotates about its axis O1.
- the compressor wheel 8 flows the intake air A flowing from the direction of the axis O1 while compressing the intake air A from the inside in the radial direction centering on the axis by the centrifugal force.
- the compressed air B compressed by the compressor wheel 8 is discharged toward the outside of the compressor wheel 8 in the radial direction about the axis O1.
- the compressor housing 9 includes a wheel housing portion 10, a compressor introduction portion 11, and a compressor discharge portion 12.
- the wheel housing portion 10 covers the compressor wheel 8 from the outside in a rotatable state.
- the compressor introduction portion 11 communicates with the wheel housing portion 10 near the rotation center of the compressor wheel 8.
- the compressor introducing portion 11 forms an introducing passage 13 for introducing the intake air A in the direction of the axis O 1 with respect to the wheel accommodating portion 10.
- the compressor discharge portion 12 communicates with the wheel storage portion 10 at the radially outer side of the compressor wheel 8.
- the compressor discharge portion 12 is connected to the intake manifold 14.
- the compressor discharge portion 12 forms a discharge passage 15 for introducing the compressed air B into the cylinder 7 of the engine 6 through the intake manifold 14.
- the turbine unit 3 includes a turbine wheel 16 (turbine) and a turbine housing 17.
- the turbine wheel 16 recovers a part of the thermal energy of the exhaust gas C discharged from the engine 6 and rotates around its axis O2.
- the turbine housing 17 includes a turbine wheel accommodating portion 19, an exhaust introducing portion 20, and an exhaust discharging portion 21.
- the turbine wheel housing portion 19 covers the turbine wheel 16 from the outside in a state where the turbine wheel 16 can rotate.
- the exhaust introduction portion 20 forms an exhaust introduction passage (a high pressure side passage) 20 a for introducing the exhaust gas of the engine 6 into the turbine wheel housing portion 19.
- the turbine wheel housing portion 19 communicates with the exhaust gas introduction portion 20 at the radially outer side of the turbine wheel 16.
- the exhaust discharge portion 21 forms an exhaust discharge passage (a low pressure side passage) 21 a communicating with the turbine wheel housing portion 19 near the rotation center of the compressor wheel 8.
- the bearing unit 4 includes a rotating shaft 18 and a bearing housing (not shown).
- the rotating shaft 18 transmits the rotation of the turbine wheel 16 to the compressor wheel 8.
- the rotating wheel 18 has a turbine wheel 16 fixed to a first end 18 a thereof and a compressor wheel 8 fixed to a second end 18 b thereof.
- the bearing housing covers the rotating shaft 18 from the outside.
- the bearing housing has a bearing (not shown) that rotatably supports the rotating shaft 18.
- a slide bearing, a rolling bearing, etc. can be illustrated, for example.
- the compressor housing 9 and the turbine housing 17 described above are respectively fixed to the bearing housing.
- the waste gate mechanism 5 adjusts the flow rate of the exhaust gas supplied to the turbine wheel 16. In other words, the wastegate mechanism 5 causes the excess exhaust gas to flow to the exhaust discharge portion 21 without passing through the turbine wheel housing portion 19.
- FIG. 2 is a perspective view showing a schematic configuration of part of the turbocharger 1.
- FIG. 3 is a plan view showing a schematic configuration of part of the turbocharger 1.
- FIG. 4 is a cross-sectional view schematically showing a part of the supercharger 1, and more specifically a cross-sectional view orthogonal to the axis of the waste gate valve.
- 5 and 6 are perspective views showing a part of the turbocharger 1.
- the exhaust gas introducing portion 20 has a first exhaust gas introducing portion 20A formed in a spiral shape and a second exhaust gas introducing portion 20B formed in a spiral shape.
- the first exhaust gas introducing portion 20A forms a first exhaust gas introducing passage 20a1.
- the second exhaust introduction portion 20B forms a second exhaust introduction passage 20a2.
- exhaust gas from the second and third cylinders (not shown) of the four cylinders of the engine is introduced into the second exhaust introducing portion 20B.
- the second exhaust gas introducing portion 20B is arranged in the radial direction of the first exhaust gas introducing portion 20A (in the radial direction of the turbine wheel 16) side by side with the first exhaust gas introducing portion 20A. It is provided.
- the supercharger 1 is a supercharger having a so-called "double scroll" type structure in which two spiral exhaust introduction parts 20A, 20B are provided in line in the radial direction.
- the waste gate mechanism 5 includes a first introducing part 31, a second introducing part 32, a chamber 23, a waste gate valve 24 (valve member), and a waste gate outlet 33 ( And a derivation unit).
- the first introduction part 31 forms a first flow path 31 a.
- the first introducing unit 31 is connected to the first exhaust introducing unit 20A and the chamber 23.
- the first introducing unit 31 can guide the exhaust gas from the first exhaust introducing passage 20a1 to the chamber 23 through the first flow passage 31a.
- the second introduction part 32 forms a second flow path 32a.
- the second introduction unit 32 is connected to the second exhaust introduction unit 20 ⁇ / b> B and the chamber 23.
- the second introduction unit 32 can guide the exhaust gas from the second exhaust introduction passage 20a2 to the chamber 23 through the second flow passage 32a.
- the west gate outlet 33 forms an outlet channel 33a.
- the waste gate outlet 33 is connected to the chamber 23 and the exhaust outlet 21 (see FIG. 1).
- the waste gate outlet 33 can lead the exhaust gas from the chamber 23 to the exhaust outlet 21 through the outlet channel 33a.
- the first introducing portion 31, the second introducing portion 32, the chamber 23 and the waste gate outlet 33 communicate the exhaust introducing portion 20 and the exhaust discharging portion 21 shown in FIG. 1 without passing through the turbine wheel accommodating portion 19. Form a bypass.
- the chamber 23 is formed in a cylindrical shape whose center axis is the axis O3.
- the chamber 23 has a receiving space 25 for receiving the waste gate valve 24.
- the inner peripheral surface 23a of the chamber 23 is formed to have a circular cross section orthogonal to the axis O3. That is, the inner circumferential surface 23a is a cylindrical surface having the axis O3 as a central axis.
- at least one part of the cross section orthogonal to an axis line should just be formed in circular arc shape about the internal peripheral surface of a chamber.
- the chamber 23 has a first inlet port 26, a second inlet port 27 and an outlet port 28.
- the first introduction port 26, the second introduction port 27 and the lead-out port 28 are respectively long holes extending in the direction of the axis O3.
- the first inlet port 26, the second inlet port 27, and the outlet port 28 are formed at different positions in the direction around the axis O3.
- the first introduction port 31 is connected to the first introduction port 26.
- the storage space 25 of the chamber 23 is in communication with the first exhaust gas introduction passage 20a1 of the first exhaust gas introduction portion 20A through the first introduction port 26 and the first flow passage 31a.
- the second introduction port 32 is connected to the second introduction port 27.
- the accommodation space 25 of the chamber 23 is in communication with the second exhaust introduction passage 20a2 of the second exhaust introduction portion 20B through the second introduction port 27 and the second flow passage 32a.
- the west gate outlet 33 is connected to the outlet port 28.
- the accommodation space 25 of the chamber 23 is in communication with the exhaust gas discharge passage 21 a (see FIG. 1) of the exhaust gas discharge unit 21 through the discharge port 28 and the discharge flow passage 33 a.
- the waste gate valve 24 is accommodated in the accommodation space 25 of the chamber 23.
- the waste gate valve 24 is rotatably supported by the chamber 23 around the axis O4.
- the waste gate valve 24 switches between communication and non-communication between two or more of the first inlet port 26, the second inlet port 27, and the outlet port 28, as described later.
- the chamber 23 functions as a valve box of the waste gate valve 24.
- FIG. 7 is a perspective view showing the waste gate valve 24.
- the waste gate valve 24 has a valve body 29 and a drive protrusion 30.
- the valve body 29 is generally cylindrical with the axis O4 as the central axis.
- the outer diameter of the valve body 29 is slightly smaller than the inner diameter of the chamber 23.
- a circulation recess 35 is formed on the side of the valve body 29.
- the space in the circulation recess 35 is referred to as a main circulation space 36.
- the bottom surface of the flow through recess 35 is referred to as a main surface 35 a.
- the main surface 35 a is a plane along the axis O 4 and is a plane perpendicular to the radial direction of the valve body 29.
- the main circulation space 36 is a space secured on the main surface 35 a side.
- the cross section of the valve main body 29 which passes through the main surface 35a and is orthogonal to the axis O4 has an arc shape consisting of a linear main surface 35a and an arc-shaped outer peripheral surface 29a.
- the outer circumferential surface 29a is a surface opposite to the main surface 35a, that is, the back surface.
- the drive protrusion 30 is formed on one of the two end surfaces 34 in the direction of the axis O 4 of the valve body 29.
- the drive projection 30 projects from the end face 34 along an extension of the axis O4 of the valve body 29.
- the waste gate valve 24 can be rotated about the axis O4, for example, by driving the drive protrusion 30 by the power of an actuator (not shown).
- FIGS. 8 to 10 are cross-sectional views schematically showing a part of the turbocharger 1.
- the waste gate valve 24 is rotatable around the axis O4, and depending on the rotational position around the axis O4, the first inlet port 26, the second inlet port 27, and the outlet port 28. One or more of them can be opened and closed. Details will be described below.
- the opening portion of the flow through recess 35 overlaps the first introduction port 26, whereby the first introduction port 26 is opened.
- the first flow path 31 a of the first introduction portion 31 and the main flow space 36 communicate with each other.
- the second inlet port 27 and the outlet port 28 are closed by the outer peripheral surface 29a of the valve main body 29 because the second inlet port 27 and the outlet port 28 do not overlap with the opening of the flow recess 35.
- the first flow passage 31a and the second flow passage 32a are separated. Therefore, the output of the turbine unit 3 (see FIG. 1) at the time of low rotation of the engine 6 can be increased.
- the opening of the flow through recess 35 overlaps the first introduction port 26 and the second introduction port 27, thereby the first introduction port 26 and the The introduction port 27 is opened.
- the first introduction port 26 and the second introduction port 27 communicate with each other via the main flow space 36. Therefore, the first flow path 31 a of the first introduction portion 31 and the second flow path 32 a of the second introduction portion 32 are communicated with each other.
- the outlet port 28 is closed by the outer peripheral surface 29a of the valve main body 29 because the outlet port 28 does not overlap with the opening of the flow recess 35. Therefore, the main flow space 36 does not communicate with the outlet flow path 33a. Therefore, the exhaust gas in the main flow space 36 is not discharged from the lead-out flow path 33a.
- the first flow passage 31a and the second flow passage 32a communicate with each other. Since the flow paths (the first flow path 31 a and the second flow path 32 a) of the two introduction portions (the first introduction portion 31 and the second introduction portion 32) are communicated, the turbine portion 3 (the high speed rotation of the engine 6) 1) can be enhanced.
- the opening of the flow through recess 35 overlaps with part of the outlet port 28 in addition to the first inlet port 26 and the second inlet port 27. . Therefore, the first introduction port 26, the second introduction port 27 and the lead-out port 28 are opened. Thereby, the first introduction port 26 and the second introduction port 27 communicate with the lead-out port 28 via the main flow space 36. Therefore, the first flow path 31 a of the first introduction portion 31 and the second flow path 32 a of the second introduction portion 32 are in communication with the discharge flow path 33 a of the waste gate outlet 33.
- the boost pressure can be adjusted by adjusting the output of the turbine unit 3 (see FIG. 1).
- the turbocharger 1 sets the waste gate valve 24 to the first position P1 in a state where the number of revolutions of the engine 6 (see FIG. 1) is low and the flow rate of exhaust gas is small.
- the first channel 31a and the second channel 32a can be separated. Therefore, the output of the turbine unit 3 (see FIG. 1) at the time of low rotation of the engine 6 (see FIG. 1) can be increased.
- the waste gate valve 24 is set to the second position P2, whereby the first flow passage 31a and the second flow passage are obtained. It can be in communication with 32a. Thereby, although the double scroll type (see FIGS.
- the efficiency of the turbine unit 3 can be enhanced when the engine 6 (see FIG. 1) has a high revolution.
- the waste gate valve 24 is set to the third position P3, and a part of the exhaust gas is taken out from the flow passage 33a and the exhaust discharge passage 21a (FIG. 1). It can be discharged out of the system through This makes it possible to adjust the supercharging pressure and to reduce the inlet pressure of the turbine unit 3.
- the turbocharger 1 allows the communication between the first flow passage 31a and the second flow passage 32a (see FIG. 9) and the discharge of exhaust gas (see FIG. 10) by the single waste gate mechanism 5. Both become possible. Therefore, the device structure can be simplified, and the device can be miniaturized and the cost can be reduced. Therefore, in the turbocharger 1, the exhaust gas can be efficiently used as described above while having a simple structure.
- the turbocharger 1 uses a waste gate valve 24 which is rotatable around an axis O4 in the chamber 23. Therefore, noise associated with the opening and closing of the valve can be reduced as compared with a turbocharger using a flap type waste gate valve. Further, since the waste gate valve 24 opens and closes the port by rotation around the axis O4, uneven wear of the waste gate valve 24 is unlikely to occur. The waste gate valve 24 is also superior to the flap type waste gate valve in terms of controllability of the valve operation.
- FIG. 11 is a cross-sectional view schematically showing a part of the turbocharger 101 according to the second embodiment, and more specifically, a cross-sectional view orthogonal to the axis of the waste gate valve 124.
- the turbocharger 101 differs from the turbocharger 1 of the first embodiment shown in FIG. 8 and the like in that a notch 130 is formed on the outer peripheral surface 129a of the valve body 129 of the waste gate valve 124.
- the notch 130 has an inner surface 130 a whose cross section perpendicular to the axis O 4 of the waste gate valve 124 is curved and concave.
- the cross-sectional shape of the inner surface 130a is, for example, an arc shape, an elliptical arc shape, or the like.
- the cross-sectional shape of the inner surface 130a is not particularly limited as long as gas can flow in the notch 130, and may be rectangular or V-shaped.
- the notch 130 is formed along the axis O4 direction. A gas can flow through the sub-circulation space 131 which is an internal space of the notch 130.
- the waste gate valve 124 when the waste gate valve 124 is in the second position P5, the open portion of the flow through recess 35 overlaps the first introduction port 26 and part of the outlet port 28. Therefore, the first introduction port 26 and a part of the outlet port 28 are opened by the circulation recess 35. Thereby, the first introduction port 26 is in communication with the outlet port 28 via the main flow space 36. Therefore, the first flow passage 31 a of the first introduction portion 31 is in communication with the lead-out flow passage 33 a of the waste gate lead-out portion 33 via the main flow passage space 36.
- the opening portion of the notch 130 overlaps with a part of the second introduction port 27 and a part of the outlet port 28, so that a part of the second introduction port 27 and a part of the outlet port 28 are cut off. It is opened by the notch 130.
- the second introduction port 27 and the lead-out port 28 communicate with each other through the auxiliary flow space 131. Therefore, the second flow passage 32 a of the second introduction portion 32 and the discharge flow passage 33 a of the waste gate discharge portion 33 communicate with each other.
- the opening of the flow through recess 35 does not overlap with the second introduction port 27, and the opening of the notch 130 does not overlap with the first introduction port 26, so that the first introduction port 26; It does not communicate with the second introduction port 27.
- the waste gate valve 124 When the waste gate valve 124 is in the second position P5, the first flow passage 31a and the lead-out flow passage 33a are communicated with each other through the main circulation space 36, so the inside of the first exhaust introduction passage 20a1 (see FIG. Exhaust gas can be discharged out of the system through the first flow passage 31a, the main flow space 36, the outlet port 28, the discharge passage 33a, and the exhaust gas discharge passage 21a (see FIG. 1). Further, since the second flow passage 32a and the lead-out flow passage 33a are communicated with each other through the sub circulation space 131, the exhaust gas in the second exhaust gas introduction passage 20a2 (see FIG. 4) It can discharge
- the exhaust gas can be allowed to flow through the lead-out passage 33a, so the output of the turbine unit 3 can be adjusted to adjust the supercharging pressure.
- the exhaust gas from the first flow passage 31a and the second flow passage 32a is led to the discharge flow passage 33a in a state where the first introduction port 26 and the second introduction port 27 do not communicate. be able to.
- the amount of exhaust gas led to the outlet flow path 33a can be increased, so the catalyst (not shown) on the downstream side can be efficiently heated, and the activation of the catalyst can be promoted.
- the opening of the flow through recess 35 overlaps the first introduction port 26 and the second introduction port 27 so that the first introduction port 26 and the The introduction port 27 is opened.
- the first introduction port 26 and the second introduction port 27 communicate with each other via the main flow space 36. Therefore, the first flow path 31 a of the first introduction portion 31 and the second flow path 32 a of the second introduction portion 32 are communicated with each other.
- the outlet port 28 is closed by the outer peripheral surface 29a of the valve body 29. Therefore, the main flow space 36 does not communicate with the outlet flow path 33a. Therefore, the exhaust gas in the main flow space 36 is not discharged from the lead-out flow path 33a.
- the output of the turbine unit 3 at the time of high rotation of the engine 6 can be increased.
- the waste gate valve 124 when the waste gate valve 124 is at the fourth position P7, the first introduction port 26, the second introduction port 27 and the lead-out port 28 are opened by the circulation recess 35. Thereby, the first introduction port 26 and the second introduction port 27 communicate with the lead-out port 28 via the main flow space 36.
- the waste gate valve 124 When the waste gate valve 124 is at the fourth position P7, in addition to the communication between the first flow path 31a and the second flow path 32a, the flow paths 31a and 32a and the discharge flow path 33a are connected. Therefore, the exhaust gas in the first exhaust introduction passage 20a1 and the second exhaust introduction passage 20a2 (see FIG. 4) is transferred to the main flow space 36, the outlet port 28, the outlet flow passage 33a, and the exhaust discharge passage 21a (see FIG. 1). Can be discharged out of the system. Therefore, the output of the turbine unit 3 at the time of high rotation of the engine 6 can be increased. Furthermore, the boost pressure can be adjusted by adjusting the output of the turbine unit 3 (see FIG. 1).
- the first flow passage 31a and the second flow passage 32a are in a state where the first introduction port 26 and the second introduction port 27 do not communicate with each other at the second position P5 shown in FIG.
- Exhaust gas from the exhaust gas can be led to the outlet flow passage 33a.
- the amount of exhaust gas led to the outlet flow path 33a can be increased, so the catalyst (not shown) on the downstream side can be efficiently heated, and the activation of the catalyst can be promoted.
- FIG. 15 is a cross-sectional view schematically showing a part of the turbocharger 201 according to the third embodiment, and specifically showing a cross section orthogonal to the axis of the waste gate valve 124.
- the turbocharger 201 has two west gate lead out portions 133A and 133B, that is, a first waste gate lead out portion 133A and a second waste gate lead out portion 133B in place of the west gate lead out portion 33, as shown in FIG. It differs from the turbocharger 101 of the second embodiment shown.
- the first waste gate outlet 133A is connected to a part of the outlet port 28 (first outlet port 28A).
- the second west gate lead-out unit 133B is connected to the other part (second lead-out port 28B) of the lead-out port 28.
- the first waste gate outlet 133A forms a first outlet channel 133Aa.
- the second waste gate outlet 133B forms a second outlet channel 133Ba.
- the first lead-out channel 133Aa and the second lead-out channel 133Ba are independent of each other.
- the operation of the turbocharger 201 will be described with reference to FIG. 15 to FIG.
- the first introduction port 26 is opened by the flow recess 35.
- the second inlet port 27 and the outlet port 28 are closed by the outer peripheral surface 29 a of the valve body 29.
- the first introduction port 26 and part of the lead-out port 28 are opened by the flow-through recess 35.
- the first introduction port 26 is in communication with a part of the lead-out port 28 (first lead-out port 28A) through the main flow space 36. Therefore, the first flow passage 31 a of the first introduction portion 31 is in communication with the first lead flow passage 133 Aa of the first waste gate lead-out portion 133 A via the main circulation space 36.
- the second introduction port 27 and the other part (second lead-out port 28B) of the lead-out port 28 are opened by the notch 130.
- the second introduction port 27 is communicated with the other part of the lead-out port 28 (second lead-out port 28 B) via the auxiliary flow space 131. Therefore, the second flow passage 32 a of the second introduction part 32 is in communication with the second lead-out flow passage 133 Ba of the second waste gate lead-out portion 133 B via the auxiliary flow space 131.
- the first introduction port 26 and the second introduction port 27 do not communicate with each other.
- the waste gate valve 124 When the waste gate valve 124 is in the second position P9, the first flow passage 31a and the first lead-out passage 133Aa are communicated with each other through the main flow passage 36, so the first exhaust introduction passage 20a1 (see FIG. 4) The exhaust gas inside can be discharged out of the system through the main flow space 36, the outlet port 28 (first outlet port 28A), the first outlet passage 133Aa, and the exhaust discharge passage 21a (see FIG. 1). Further, since the second flow passage 32a and the second lead-out flow passage 133Ba are communicated with each other through the sub circulation space 131, the exhaust gas in the second exhaust gas introduction passage 20a2 (see FIG. 4) It can be discharged out of the system through the outlet port 28 (second outlet port 28B), the second outlet channel 133Ba, and the exhaust discharge passage 21a (see FIG. 1).
- the output of the turbine unit 3 can be adjusted to adjust the supercharging pressure.
- the exhaust gas from the first flow path 31a and the second flow path 32a are respectively directed to the discharge flow paths 133Aa and 133Ba. It can lead. Since the lead-out channels 133Aa and 133Ba are independent of each other, it is possible to prevent the leak flow between the two lead-out channels 133Aa and 133Ba and to increase the exhaust gas discharge amount. Therefore, the catalyst (not shown) on the downstream side can be heated more efficiently by the exhaust gas, and activation of the catalyst can be promoted.
- the waste gate valve 124 when the waste gate valve 124 is in the third position P10, the first introduction port 26 and the second introduction port 27 are opened. As a result, the first introduction port 26 and the second introduction port 27 communicate with each other through the main circulation space 36, and thus the first flow path 31 a of the first introduction portion 31 and the second flow of the second introduction portion 32. It is in communication with the passage 32a.
- the outlet port 28 In the third position P10, the outlet port 28 is closed by the outer peripheral surface 29a of the valve body 29. At the third position P10, since the first flow passage 31a and the second flow passage 32a are in communication, the output of the turbine unit 3 at the time of high rotation of the engine 6 can be increased.
- the waste gate valve 124 when the waste gate valve 124 is at the fourth position P11, the first introduction port 26, the second introduction port 27 and the lead-out port 28 are opened by the circulation recess 35. Thereby, the first introduction port 26 and the second introduction port 27 communicate with the lead-out port 28 via the main flow space 36.
- the waste gate valve 124 When the waste gate valve 124 is at the fourth position P11, in addition to the communication between the first flow path 31a and the second flow path 32a, the flow paths 31a and 32a and the discharge flow paths 133Aa and 133Ba are connected. Ru. Therefore, the exhaust gas in the first exhaust introduction passage 20a1 and the second exhaust introduction passage 20a2 (see FIG. 4) is transferred to the main flow space 36, the outlet port 28, the outlet flow passages 133Aa and 133Ba, and the exhaust discharge passage 21a (FIG. 1). It can be discharged out of the system through Therefore, the output of the turbine unit 3 at the time of high rotation of the engine 6 can be increased. Furthermore, the boost pressure can be adjusted by adjusting the output of the turbine unit 3 (see FIG. 1).
- first flow path 31a and second flow path 32a In supercharger 201, as described above, in the state where first introduction port 26 and second introduction port 27 do not communicate with each other at second position P9 shown in FIG. 16, first flow path 31a and second flow path 32a.
- the exhaust gas from the exhaust gas can be led to the outlet flow channels 133Aa and 133Ba, respectively. Since the lead-out channels 133Aa and 133Ba are independent of each other, it is possible to prevent the leak flow between the two lead-out channels 133Aa and 133Ba and to increase the exhaust gas discharge amount. Therefore, the catalyst (not shown) on the downstream side can be heated more efficiently by the exhaust gas, and activation of the catalyst can be promoted.
- FIGS. 19 and 20 are cross sectional views showing a schematic configuration of a part of a specific example of the turbocharger 201.
- the turbocharger 201 has a first waste gate outlet 133A and a second waste gate outlet 133B.
- the first waste gate outlet 133A is connected to a part of the outlet port 28 (first outlet port 28A).
- the second west gate lead-out unit 133B is connected to the other part (second lead-out port 28B) of the lead-out port 28.
- the waste gate valve 124 is in the first position P8 (see FIG. 15).
- the first introduction port 26 is opened by the circulation recess 35.
- the second inlet port 27 and the outlet port 28 are closed by the outer peripheral surface 29 a of the valve body 29.
- the waste gate valve 124 when the waste gate valve 124 is in the second position P9 (see FIG. 16), the first introduction port 26 and part of the lead port 28 (first lead port 28A) It is released.
- the second inlet port 27 and the other part of the outlet port 28 (second outlet port 28 B) are opened by the notch 130.
- the first introduction port 26 and the second introduction port 27 do not communicate with each other. Therefore, the first flow passage 31a and the first lead-out flow passage 133Aa are communicated via the main flow passage space 36, and the second flow passage 32a and the second lead-out flow passage 133Ba are communicated via the sub flow passage space 131. Be done.
- FIG. 21 is a cross-sectional view schematically showing a waste gate valve 24A which is a first modification of the waste gate valve 24 of the turbocharger 1 according to the first embodiment.
- FIG. 21 is a view showing a cross section orthogonal to the axis O4.
- FIG. 22 is a perspective view showing the waste gate valve 24A.
- the waste gate valve 24A differs from the waste gate valve 24 shown in FIGS. 7 and 8 in that a guide projection 37 is formed on the main surface 35a of the valve body 29A.
- the guide convex portion 37 is formed to protrude from the main surface 35 a.
- the guide convex portion 37 has a constant projecting height in the direction of the axis O4.
- the cross section of the guide convex portion 37 orthogonal to the axis O4 has a shape in which the height gradually decreases from the vertex 37a toward the side edges 35a1 and 35a2 of the main surface 35a.
- the surface from the ridgeline 37 b including the apex 37 a of the guide convex portion 37 to one side edge 35 a 1 of the main surface 35 a is referred to as a guide surface 38.
- the guide surface 38 is a surface whose cross section orthogonal to the axis O4 has a curved concave shape.
- the cross-sectional shape of the guide surface 38 is, for example, an arc shape, an elliptical arc shape, or the like.
- the position (circumferential position) of the waste gate valve 24A around the axis O4 is a position where the first introduction port 26, the second introduction port 27 and the lead-out port 28 are opened by the circulation recess 35.
- the guide surface 38 is inclined with respect to the radial direction of the waste gate valve 24A.
- the inclination direction of the guide surface 38 of the waste gate valve 24A is a direction approaching the outlet port 28 while reducing the protruding height with respect to the main surface 35a as going radially outward.
- the exhaust gas flowing into the main flow space 36 from the first introduction port 26 and the second introduction port 27 travels to the outlet port 28 under the influence of the guide surface 38 of the guide convex portion 37.
- a part of the exhaust gas flowing into the main circulation space 36 from the first introduction port 26 flows along the guide surface 38 from the ridgeline 37b toward the side edge 35a1 while the flow is adjusted. Head. Therefore, the exhaust gas has a low flow resistance and smoothly flows toward the outlet port 28.
- the guide projection 37 also affects the flow resistance of the exhaust gas flowing from the second introduction port 27 to the outlet port 28.
- the guide convex portion 37 can adjust the flow resistance of the exhaust gas flowing from the at least one of the first introduction port 26 and the second introduction port 27 to the lead-out port 28. Therefore, the flow rate of the exhaust gas flowing in from the first introduction port 26, the flow rate of the exhaust gas flowing in from the second introduction port 27, and the ratio of these flow rates can be adjusted.
- FIG. 23 is a perspective view showing a waste gate valve 24B which is a second modification of the waste gate valve 24 of the turbocharger 1 according to the first embodiment.
- a guide convex portion 37B is formed on the valve main body 29B.
- the waste gate valve 24B differs from the waste gate valve 24A shown in FIG. 22 in that the guide convex portion 37B gradually reduces the projecting height in one direction along the axis O4.
- the waste gate valve 24B can adjust the effect of adjusting the flow of the exhaust gas according to the shape of the guide convex portion 37B.
- FIG. 24 is a cross-sectional view showing a turbocharger having a waste gate valve 24C which is a third modification of the waste gate valve 24 of the turbocharger 1 according to the first embodiment.
- FIG. 25 is a perspective view showing the waste gate valve 24C.
- FIG. 26 is a cross-sectional view showing a turbocharger having a waste gate valve 24C, and is a cross-sectional view taken along line II of FIG.
- FIG. 27 is a cross-sectional view showing a turbocharger having a waste gate valve 24C, and is a II-II cross-sectional view of FIG.
- the waste gate valve 24C differs from the waste gate valve 24 shown in FIGS. 7 and 8 in that the adjustment projection 40 is formed on the main surface 35a of the valve body 29C. .
- the adjustment convex portion 40 is formed in a region including a part in the length direction (direction along the axis O4) of the main surface 35a, more specifically, one end in the direction along the axis O4.
- the cross section of the adjustment projection 40 orthogonal to the axis O4 has a shape having an arc-shaped outer peripheral surface 40a and a curved concave inner surface 40b.
- the outer peripheral surface 40a is a cylindrical surface having the axis O4 as a central axis, and is formed continuously from the outer peripheral surface 29Ca of the valve main body 29C.
- the inner surface 40b is shaped to gradually increase in height from one side edge 35a1 of the main surface 35a to the other side edge.
- the inner surface 40b is a surface whose cross section orthogonal to the axis O4 has a curved concave shape.
- the cross-sectional shape of the inner surface 40b is, for example, an arc shape, an elliptical arc shape, or the like. As shown in FIG.
- the portion where the adjustment convex portion 40 is formed is referred to as a first portion 29C1, and the portion where the adjustment convex portion 40 is not formed is the second portion 29C2. It is said.
- the first introduction port 26 communicates with the outlet port 28 via the main flow space 36, and the second introduction port 27 flows in the sub flow space 131. It can be in communication with the outlet port 28 via
- the outer peripheral surface 40a of the adjustment convex portion 40 covers a part of the first introduction port 26 in the first portion 29C1. Therefore, the amount of gas flowing into the chamber 23 (main flow space 36) from the first introduction port 26 can be adjusted.
- the waste gate valve 24 C allows gas to flow from the second introduction port 27 into the chamber 23 (main flow space 36).
- the amount can be adjusted.
- an adjustment convex part can also be formed so that a part can be covered about both a 1st introductory port and a 2nd introductory port. According to this configuration, the amount of gas flowing into the chamber from the first introduction port and the second introduction port can be adjusted.
- FIG. 28 is a perspective view showing a schematic configuration of part of a turbocharger 301 according to the fourth embodiment.
- the exhaust introducing portion 320 of the turbocharger 301 has a first exhaust introducing portion 320A formed in a spiral shape and a second exhaust introducing portion 320B formed in a spiral shape.
- the first exhaust introducing portion 320A and the second exhaust introducing portion 320B are provided side by side in the axial direction (the axial direction of the turbine wheel 16).
- the supercharger 301 is a supercharger having a so-called "twin scroll" type structure in which two spiral exhaust introduction parts 320A and 320B are provided in line in the axial direction.
- the supercharger 301 can be provided with a wastegate mechanism 5 (see FIG.
- the first introducing unit 31 (see FIG. 4) is connected to the first exhaust introducing unit 320A
- the second introducing unit 32 (see FIG. 4) is connected to the second exhaust introducing unit 320B.
- FIG. 29 is a view showing a schematic configuration of a part of the internal combustion engine 400 according to the embodiment.
- the engine 406 the first introduction portion 431, the second introduction portion 432, the chamber 23, the valve 24 (valve member), the waste gate outlet portion 433 and A feeder 401 is provided.
- the first introduction portion 431 forms a first flow path 431a.
- the first introduction conduit 441 and the fourth introduction conduit 444 are connected to the first introduction portion 431.
- the first cylinder (not shown) is connected to the first introduction pipeline 441, and the fourth cylinder (not shown) is connected to the fourth introduction pipeline 444.
- the second introduction part 432 forms a second flow path 432a.
- the second introduction conduit 442 and the third introduction conduit 443 are connected to the second introduction part 432.
- the second cylinder (not shown) of the four cylinders of the engine 406 is connected to the second inlet line 442, and the third cylinder (not shown) is connected to the third inlet line 443.
- the west gate outlet 433 forms an outlet channel 433a.
- the internal combustion engine 400 can discharge the exhaust gas led from the engine 406 through the first flow passage 431 a and the second flow passage 432 a to the outside of the system through the chamber 23 and the outlet flow passage 433 a.
- the exhaust gas is disposed by arranging the valve 24 at any one of the first position P1 (see FIG. 8), the second position P2 (see FIG. 9), and the third position P3 (see FIG. 10). Flow can be adjusted.
- the turbocharger 1 shown in FIG. 4 etc. has two introduction parts (the first introduction part 31 and the second introduction part 32), the number of introduction parts is two or more in the turbocharger of the embodiment. It may be any number.
- the first inlet port 26 can communicate with the outlet port 28 via the main flow space 36, and the second inlet port 27 communicates with the outlet port 28 via the auxiliary flow space 131. It is possible.
- the first introduction port can communicate with the outlet port via the secondary flow space 131, and the second introduction port can communicate with the outlet port via the main circulation space. It is also good.
- the valve member can be configured to be able to open and close the first introduction port.
- the valve member may allow communication between any two or more of the first introduction port, the second introduction port, and the lead-out port through the main flow space. For example, among the three ports (the first inlet port, the second inlet port, and the outlet port), the first inlet port and the outlet port may be able to communicate with each other, or the second inlet port and the outlet port may be able to communicate with each other. Good.
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Abstract
Description
本願は、2016年2月29日に米国に出願された米国特許仮出願第62/300926号に基づき優先権を主張し、その内容をここに援用する。
実施形態の過給機は、例えば、内燃機関としてレシプロエンジン(以下、単にエンジンと称する)を駆動源として有した自動車等の車両に搭載されている。この過給機は、エンジンの排気ガスを利用して吸気を圧縮する、いわゆるターボチャージャーである。前記エンジンは、1または複数(例えば4つ)のシリンダーを有する。
図1に示すように、過給機1は、コンプレッサー部2と、タービン部3と、軸受部4と、ウェストゲート機構5(ロータリー弁装置)と、備えている。
コンプレッサー部2は、エアクリーナー(図示せず)から導入された吸気を圧縮して、エンジン6のシリンダー7に送り込む。コンプレッサー部2は、コンプレッサーホイール8と、コンプレッサーハウジング9とを備えている。
コンプレッサーホイール8は、その軸線O1を中心に回転する。コンプレッサーホイール8は、その遠心力により、軸線O1方向から流入する吸気Aを、軸線を中心とした径方向の内側から外側に向かって圧縮しながら流す。コンプレッサーホイール8により圧縮された圧縮空気Bは、軸線O1を中心とする径方向において、コンプレッサーホイール8の外側に向かって排出される。
タービンホイール16は、エンジン6から排出される排気ガスCの熱エネルギーの一部を回収して、その軸線O2回りに回転する。
タービンハウジング17は、タービンホイール収容部19と、排気導入部20と、排気排出部21と、を備えている。
排気導入部20は、エンジン6の排気ガスをタービンホイール収容部19へ導入する排気導入通路(高圧側の通路)20aを形成する。
タービンホイール収容部19は、タービンホイール16の径方向外側で排気導入部20と連通している。
排気排出部21は、コンプレッサーホイール8の回転中心の近くでタービンホイール収容部19に連通する排気排出通路(低圧側の通路)21aを形成する。
回転軸18は、タービンホイール16の回転を、コンプレッサーホイール8に伝達する。回転軸18は、その第一端部18aにタービンホイール16が固定され、その第二端部18bにコンプレッサーホイール8が固定されている。
軸受ハウジングは、回転軸18を外側から覆う。この軸受ハウジングは、回転軸18を回転自在に支持する軸受(図示せず)を有している。この軸受としては、例えば、すべり軸受や、転がり軸受などが例示できる。軸受ハウジングには、上述したコンプレッサーハウジング9およびタービンハウジング17がそれぞれ固定される。
図2~図4に示すように、排気導入部20は、渦巻き状に形成された第1排気導入部20Aと、渦巻き状に形成された第2排気導入部20Bとを有する。
第1排気導入部20Aは、第1排気導入通路20a1を形成する。第1排気導入部20Aは、例えば、エンジンの4つのシリンダーのうち第1シリンダーおよび第4シリンダー(図示略)からの排気ガスが導入される。
第2排気導入部20Bは、第2排気導入通路20a2を形成する。第2排気導入部20Bは、例えば、エンジンの4つのシリンダーのうち第2シリンダーおよび第3シリンダー(図示略)からの排気ガスが導入される。図2および図3に示すように、第2排気導入部20Bは、第1排気導入部20Aの径方向(タービンホイール16の径方向)の内方側に、第1排気導入部20Aに並んで設けられている。
過給機1は、2つの渦巻き状の排気導入部20A,20Bが径方向に並んで設けられた構造、いわゆる「ダブルスクロール」型の構造を有する過給機である。
第2導入部32は、第2流路32aを形成する。第2導入部32は、第2排気導入部20Bとチャンバー23とに接続されている。第2導入部32は、第2排気導入通路20a2からの排気ガスを、第2流路32aを通してチャンバー23に導くことができる。
ウェストゲート導出部33は、導出流路33aを形成する。ウェストゲート導出部33は、チャンバー23と排気排出部21(図1参照)とに接続されている。ウェストゲート導出部33は、チャンバー23からの排気ガスを、導出流路33aを通して排気排出部21に導くことができる。
第1導入部31、第2導入部32、チャンバー23およびウェストゲート導出部33は、図1に示す排気導入部20と排気排出部21とを、タービンホイール収容部19を経由することなく連通させるバイパス路を形成する。
なお、チャンバーの内周面は、軸線に直交する断面の少なくとも一部が円弧状に形成されていればよい。
第1導入ポート26には第1導入部31が接続されている。これにより、チャンバー23の収容空間25は、第1導入ポート26、第1流路31aを通して、第1排気導入部20Aの第1排気導入通路20a1に連通されている。
第2導入ポート27には第2導入部32が接続されている。これにより、チャンバー23の収容空間25は、第2導入ポート27、第2流路32aを通して、第2排気導入部20Bの第2排気導入通路20a2に連通されている。
導出ポート28には、ウェストゲート導出部33が接続されている。これにより、チャンバー23の収容空間25は、導出ポート28、導出流路33aを通して、排気排出部21の排気排出通路21a(図1参照)に連通されている。
弁本体29は、概略、軸線O4を中心軸とする円柱状である。弁本体29の外径は、チャンバー23の内径より僅かに小さい。弁本体29の側部には、流通凹部35が形成されている。流通凹部35内の空間を主流通空間36という。流通凹部35の底面を主面35aという。主面35aは、軸線O4に沿う平面であり、弁本体29の径方向に対して垂直な面である。主流通空間36は、主面35a側に確保された空間である。
図4に示すように、主面35aを通り、軸線O4に直交する弁本体29の断面は、直線状の主面35aと、円弧状の外周面29aとからなる弓形である。外周面29aは、主面35aに対して反対側の面、すなわち背面である。
ウェストゲートバルブ24は、例えば、アクチュエータ(図示略)の動力により駆動突出部30を駆動させることによって、軸線O4周りに回転させることができる。
図8~図10に示すように、ウェストゲートバルブ24は、軸線O4周りに回転自在であり、軸線O4周りの回転位置に応じて、第1導入ポート26、第2導入ポート27および導出ポート28のうち1または2以上を開閉可能である。以下、詳しく説明する。
ウェストゲートバルブ24が第1位置P1にあるときには、第1流路31aと第2流路32aとは分離されている。そのため、エンジン6の低回転時におけるタービン部3(図1参照)の出力を高めることができる。
第2位置P2では、導出ポート28は流通凹部35の開放部とは重ならないため、導出ポート28は弁本体29の外周面29aによって閉止される。そのため、主流通空間36は導出流路33aとは連通しない。よって、主流通空間36内の排気ガスは導出流路33aから排出されることはない。
図9に示すように、エンジン6の回転数が高くなり、排気ガスの流量が多くなった場合、ウェストゲートバルブ24を第2位置P2とすることにより、第1流路31aと第2流路32aとを連通させることができる。これにより、ダブルスクロール型(図2および図3参照)を採用するにもかかわらず、エンジン6(図1参照)が高回転のときにタービン部3の効率を高めることができる。
図10に示すように、過給圧力が高くなりすぎてしまった場合には、ウェストゲートバルブ24を第3位置P3とし、排気ガスの一部を導出流路33a、排気排出通路21a(図1参照)を通して系外に排出することができる。これにより、過給圧を調整すると共に、タービン部3の入口圧力を低減することが可能となる。
図11は、第2実施形態に係る過給機101の一部を模式的に示す断面図であり、詳しくは、ウェストゲートバルブ124の軸線に直交する断面を模式的に示す図である。以下、既出の実施形態との共通構成については同じ符号を付してその説明を省略する。
過給機101は、ウェストゲートバルブ124の弁本体129の外周面129aに、切欠き130が形成されている点で、図8等に示す第1実施形態の過給機1と異なる。
図11に示すように、ウェストゲートバルブ124が第1位置P4にあるときには、流通凹部35の開放部が第1導入ポート26と重なることにより、第1導入ポート26は開放される。第2導入ポート27および導出ポート28は弁本体29の外周面29aによって閉止される。そのため、エンジン6の低回転時におけるタービン部3(図1参照)の出力を高めることができる。
第2位置P5では、流通凹部35の開放部は第2導入ポート27とは重ならず、かつ切欠き130の開放部は第1導入ポート26とは重ならないため、第1導入ポート26と、第2導入ポート27とは連通していない。
これに加え、第2位置P5では、第1導入ポート26と第2導入ポート27とが連通しない状態で、第1流路31aおよび第2流路32aからの排気ガスを導出流路33aに導くことができる。これにより、導出流路33aに導かれる排気ガスの量を多くすることができるため、下流側にある触媒(図示略)を効率よく加温し、前記触媒の活性化を促すことができる。
第3位置P6では、導出ポート28は弁本体29の外周面29aによって閉止される。そのため、主流通空間36は導出流路33aとは連通しない。よって、主流通空間36内の排気ガスは導出流路33aから排出されることはない。
第3位置P6では、第1流路31aと第2流路32aとが連通されているため、エンジン6の高回転時におけるタービン部3の出力を高めることができる。
図15は、第3実施形態に係る過給機201の一部を模式的に示す断面図であり、詳しくは、ウェストゲートバルブ124の軸線に直交する断面を模式的に示す図である。以下、既出の実施形態との共通構成については同じ符号を付してその説明を省略する。
過給機201は、ウェストゲート導出部33に代えて、2つのウェストゲート導出部133A,133B、すなわち第1ウェストゲート導出部133Aおよび第2ウェストゲート導出部133Bを有する点で、図11等に示す第2実施形態の過給機101と異なる。第1ウェストゲート導出部133Aは、導出ポート28の一部(第1導出ポート28A)に接続される。第2ウェストゲート導出部133Bは、導出ポート28の他部(第2導出ポート28B)に接続される。第1ウェストゲート導出部133Aは、第1導出流路133Aaを形成する。第2ウェストゲート導出部133Bは、第2導出流路133Baを形成する。第1導出流路133Aaと第2導出流路133Baとは互いに独立している。
図15に示すように、ウェストゲートバルブ124が第1位置P8にあるときには、第1導入ポート26は流通凹部35により開放される。第2導入ポート27および導出ポート28は弁本体29の外周面29aによって閉止される。
第2位置P9においては、第1導入ポート26と第2導入ポート27とが連通しない状態で、第1流路31aおよび第2流路32aからの排気ガスを、それぞれ導出流路133Aa,133Baに導くことができる。導出流路133Aa,133Baは互いに独立しているため、2つの導出流路133Aa,133Ba間の漏れ流れを防ぎ、排気ガスの排出量を増やすことができる。よって、排気ガスによって下流側の触媒(図示略)をさらに効率よく加温し、前記触媒の活性化を促すことができる。
第3位置P10では、導出ポート28は弁本体29の外周面29aによって閉止される。
第3位置P10では、第1流路31aと第2流路32aとは連通されているため、エンジン6の高回転時におけるタービン部3の出力を高めることができる。
図19に示すように、過給機201は、第1ウェストゲート導出部133Aおよび第2ウェストゲート導出部133Bを有する。第1ウェストゲート導出部133Aは、導出ポート28の一部(第1導出ポート28A)に接続される。第2ウェストゲート導出部133Bは、導出ポート28の他部(第2導出ポート28B)に接続される。
この図では、ウェストゲートバルブ124は第1位置P8にある(図15参照)。第1導入ポート26は流通凹部35により開放される。第2導入ポート27および導出ポート28は弁本体29の外周面29aによって閉止される。
図21および図22に示すように、ウェストゲートバルブ24Aは、弁本体29Aの主面35aに、ガイド凸部37が形成されている点で、図7および図8に示すウェストゲートバルブ24と異なる。
図22に示すように、ガイド凸部37は、主面35aから突出して形成されている。ガイド凸部37は、軸線O4方向にわたって一定の突出高さとされている。
図21に示すように、ガイド凸部37の、軸線O4に直交する断面は、頂点37aから、主面35aの両側縁35a1,35a2に向かって徐々に高さを減じる形状である。ガイド凸部37の頂点37aを含む稜線37bから、主面35aの一方の側縁35a1に至る面をガイド面38という。ガイド面38は、軸線O4に直交する断面が湾曲凹状となる面である。ガイド面38の断面形状は、例えば円弧状、楕円弧状などである。
図23に示すように、ウェストゲートバルブ24Bは、弁本体29Bにガイド凸部37Bが形成されている。ウェストゲートバルブ24Bは、ガイド凸部37Bが、軸線O4に沿う一方向に徐々に突出高さを減じる点で、図22に示すウェストゲートバルブ24Aと異なる。
ウェストゲートバルブ24Bは、ガイド凸部37Bの形状に応じて、排気ガスの流れを整える効果を調整することができる。
図27に示すように、軸線O4に直交する調整凸部40の断面は、円弧状の外周面40aと、湾曲凹状の内面40bとを有する形状である。外周面40aは、軸線O4を中心軸とする円柱面であって、弁本体29Cの外周面29Caから連続して形成されている。内面40bは、主面35aの一方の側縁35a1から他方の側縁に向かって徐々に高さを増す形状である。内面40bは、軸線O4に直交する断面が湾曲凹状となる面である。内面40bの断面形状は、例えば円弧状、楕円弧状などである。
図25に示すように、ウェストゲートバルブ24Cの弁本体29Cのうち、調整凸部40が形成された部分を第1部分29C1といい、調整凸部40が形成されていない部分を第2部分29C2という。
ウェストゲートバルブ24Cは、調整凸部40の外周面40aが第2導入ポート27の一部を覆う位置に配置すれば、第2導入ポート27からチャンバー23(主流通空間36)へのガスの流入量を調整することができる。
なお、調整凸部は、第1導入ポートと第2導入ポートの両方について一部を覆うことができるように形成することもできる。この構成によれば、第1導入ポートおよび第2導入ポートからチャンバーへのガスの流入量を調整することができる。
図28は、第4実施形態に係る過給機301の一部の概略構成を示す斜視図である。
過給機301の排気導入部320は、渦巻き状に形成された第1排気導入部320Aと、渦巻き状に形成された第2排気導入部320Bとを有する。第1排気導入部320Aと第2排気導入部320Bとは、軸方向(タービンホイール16の軸方向)に並んで設けられている。
過給機301は、2つの渦巻き状の排気導入部320A,320Bが軸方向に並んで設けられた構造、いわゆる「ツインスクロール」型の構造を有する過給機である。
過給機301は、過給機1(図2参照)と同様に、ウェストゲート機構5(図1参照)を設けることができる。ウェストゲート機構5は、例えば、第1導入部31(図4参照)が第1排気導入部320Aに接続され、第2導入部32(図4参照)が第2排気導入部320Bに接続される。
図29に示すように、内燃機関400は、エンジン406と、第1導入部431と、第2導入部432と、チャンバー23と、バルブ24(弁部材)と、ウェストゲート導出部433と、過給機401とを備えている。
第1導入部431は第1流路431aを形成する。第1導入部431には、第1導入管路441および第4導入管路444が接続されている。第1導入管路441には、エンジン406の4つのシリンダーのうち第1シリンダー(図示略)が接続されており、第4導入管路444には第4シリンダー(図示略)が接続されている。
第2導入部432は第2流路432aを形成する。第2導入部432には、第2導入管路442および第3導入管路443が接続されている。第2導入管路442には、エンジン406の4つのシリンダーのうち第2シリンダー(図示略)が接続されており、第3導入管路443には第3シリンダー(図示略)が接続されている。
ウェストゲート導出部433は、導出流路433aを形成する。
内燃機関400は、エンジン406から第1流路431aおよび第2流路432aを通して導かれた排気ガスを、チャンバー23、導出流路433aを通して系外に排出することができる。
例えば、図4等に示す過給機1は、2つの導入部(第1導入部31および第2導入部32)を有するが、実施形態の過給機では、導入部の数は2以上の任意の数であればよい。
図12に示す過給機101では、第1導入ポート26が主流通空間36を介して導出ポート28と連通可能であり、第2導入ポート27が副流通空間131を介して導出ポート28と連通可能である。実施形態の過給機は、逆に、第1導入ポートが副流通空間131を介して導出ポートと連通可能であり、第2導入ポートが主流通空間を介して導出ポートと連通可能であってもよい。
前記弁部材は、第1導入ポートを開閉可能に構成することができる。
前記弁部材は、第1導入ポート、第2導入ポートおよび導出ポートのうち任意の2以上のポートを主流通空間を通して連通可能とすることができる。例えば、3つのポート(第1導入ポート、第2導入ポートおよび導出ポート)のうち第1導入ポートと導出ポートとを連通可能としてもよいし、第2導入ポートと導出ポートとを連通可能としてもよい。
16 タービンホイール(タービン)
20a1 第1排気導入通路
20a2 第2排気導入通路
23 チャンバー
23a 内周面
24,24A~24C ウェストゲートバルブ(弁部材)
26 第1導入ポート
27 第2導入ポート
28 導出ポート
28A 第1導出ポート
28B 第2導出ポート
29a,129a 外周面
31 第1導入部
31a 第1流路
32 第2導入部
32a 第2流路
33 ウェストゲート導出部(導出部)
33a 導出流路
35a 主面
36 主流通空間
130 切欠き
131 副流通空間
133A 第1ウェストゲート導出部(導出部)
133Aa 第1導出流路
133B 第2ウェストゲート導出部(導出部)
133Ba 第2導出流路
400 内燃機関
Claims (9)
- 排気ガスにより駆動されるタービンに通じる第1排気導入通路から前記排気ガスを導く第1流路を有する第1導入部と、
前記タービンに通じる第2排気導入通路から前記排気ガスを導く第2流路を有する第2導入部と、
前記第1流路および前記第2流路を通して前記排気ガスが導入されるチャンバーと、
前記チャンバー内の排気ガスを系外に導く1または複数の導出流路を有する導出部と、
前記チャンバーに収容された弁部材と、を備え、
前記チャンバーは、前記第1流路に通じる第1導入ポートと、前記第2流路に通じる第2導入ポートと、前記導出流路に通じる1または複数の導出ポートと、を有し、
前記チャンバー内の、前記弁部材の主面側にガスが流通可能な主流通空間が確保され、
前記弁部材は、軸線を中心に回転自在であって、前記軸線周りの回転位置に応じて前記第1導入ポート、前記第2導入ポートおよび前記導出ポートを開閉可能であり、前記第1導入ポート、前記第2導入ポートおよび前記導出ポートのうち開放した2以上のポートを、前記主流通空間を通じて連通可能である、過給機。 - 前記弁部材は、前記第1導入ポートと前記第2導入ポートとを、前記主流通空間を通じて連通可能である、請求項1に記載の過給機。
- 前記弁部材は、前記第1導入ポートおよび前記第2導入ポートと、前記導出ポートとを前記主流通空間を通じて連通可能である、請求項1または2に記載の過給機。
- 前記チャンバーは、前記軸線を中心軸とする円筒面である内周面を有し、
前記弁部材は、前記主面とは反対側の背面として、前記軸線を中心軸とする円柱面である外周面を有し、
前記弁部材の外周面には、ガスが流通可能な副流通空間を形成する切欠きが形成され、
前記切欠きは、前記第1導入ポートと前記第2導入ポートのうちいずれか一方と、前記導出ポートとを前記副流通空間を通じて連通可能である、請求項1~3のうちいずれか1項に記載の過給機。 - 前記弁部材は、前記第1導入ポートと前記第2導入ポートのうちいずれか一方と前記導出ポートとを前記主流通空間を通じて連通させるとともに、前記第1導入ポートと前記第2導入ポートのうち他方と前記導出ポートとを前記副流通空間を通じて連通可能である、請求項4に記載の過給機。
- 前記複数の導出ポートは、第1導出ポートおよび第2導出ポートを含み、
前記弁部材は、前記第1導入ポートと前記第2導入ポートのうちいずれか一方と前記第1導出ポートとを前記主流通空間を通じて連通させるとともに、前記第1導入ポートと前記第2導入ポートのうち他方と前記第2導出ポートとを前記副流通空間を通じて連通可能である、請求項4に記載の過給機。 - 前記弁部材の主面に、前記第1導入ポートと前記第2導入ポートのうち少なくともいずれか一方から前記導出ポートに流れるガスの流れ抵抗を調整するガイド凸部が形成されている、請求項1~6のうちいずれか1項に記載の過給機。
- 前記弁部材の主面に、前記第1導入ポートと前記第2導入ポートのうち少なくともいずれか一方の一部を覆うことによって、そのポートからのガスの流量を調整する調整凸部が形成されている、請求項1~7のうちいずれか1項に記載の過給機。
- 排気ガスを導く第1流路を有する第1導入部と、
排気ガスを導く第2流路を有する第2導入部と、
前記第1流路および前記第2流路を通して前記排気ガスが導入されるチャンバーと、
前記チャンバー内の排気ガスを系外に導く1または複数の導出流路を有する導出部と、
前記チャンバーに収容された弁部材と、を備え、
前記チャンバーは、前記第1流路に通じる第1導入ポートと、前記第2流路に通じる第2導入ポートと、前記導出流路に通じる1または複数の導出ポートと、を有し、
前記チャンバー内の、前記弁部材の主面側にガスが流通可能な主流通空間が確保され、
前記弁部材は、軸線を中心に回転自在であって、前記軸線周りの回転位置に応じて前記第1導入ポート、前記第2導入ポートおよび前記導出ポートを開閉可能であり、前記第1導入ポート、前記第2導入ポートおよび前記導出ポートのうち開放した2以上のポートを、前記主流通空間を通じて連通可能である、内燃機関。
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CN111556920A (zh) * | 2018-01-29 | 2020-08-18 | 三菱重工发动机和增压器株式会社 | 带增压器的内燃机 |
JPWO2019146125A1 (ja) * | 2018-01-29 | 2021-01-28 | 三菱重工エンジン&ターボチャージャ株式会社 | 過給機付き内燃機関 |
JP7162623B2 (ja) | 2018-01-29 | 2022-10-28 | 三菱重工エンジン&ターボチャージャ株式会社 | 過給機付き内燃機関 |
Also Published As
Publication number | Publication date |
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JP6670924B2 (ja) | 2020-03-25 |
US20190048791A1 (en) | 2019-02-14 |
CN108779705B (zh) | 2020-12-29 |
CN108779705A (zh) | 2018-11-09 |
EP3409917A1 (en) | 2018-12-05 |
EP3409917A4 (en) | 2019-02-20 |
JPWO2017150543A1 (ja) | 2018-12-20 |
US10590838B2 (en) | 2020-03-17 |
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