WO2014170954A1 - 排気ターボ過給機のコンプレッサ - Google Patents
排気ターボ過給機のコンプレッサ Download PDFInfo
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- WO2014170954A1 WO2014170954A1 PCT/JP2013/061284 JP2013061284W WO2014170954A1 WO 2014170954 A1 WO2014170954 A1 WO 2014170954A1 JP 2013061284 W JP2013061284 W JP 2013061284W WO 2014170954 A1 WO2014170954 A1 WO 2014170954A1
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- Prior art keywords
- inlet
- gas
- egr
- groove
- passage
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
- F02M26/06—Low pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust downstream of the turbocharger turbine and reintroduced into the intake system upstream of the compressor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
- F02M26/19—Means for improving the mixing of air and recirculated exhaust gases, e.g. venturis or multiple openings to the intake system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/34—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with compressors, turbines or the like in the recirculation passage
-
- 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
- F02B2037/125—Control for avoiding pump stall or surge
-
- 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 an exhaust turbocharger compressor, and more particularly to an exhaust turbocharger compressor applied to an exhaust gas recirculation (EGR) system.
- EGR exhaust gas recirculation
- Patent Document 1 discloses introducing EGR gas into a compressor of an exhaust turbocharger.
- This compressor includes an annular EGR passage in an outer peripheral portion of a housing that houses an impeller.
- two reflux ports for introducing EGR gas into the compressor are formed.
- the first reflux port opens in the air passage at the impeller inlet.
- the second reflux port opens to the air passage on the upstream side of the impeller inlet.
- EGR gas that has flowed into the annular passage from the exhaust system of the internal combustion engine flows along the outer periphery of the annular passage, and passes through the first return port or the second return port depending on the amount of intake air flowing through the intake passage.
- Flow into the compressor Specifically, when the intake air amount is small, the EGR gas in the annular passage flows into the compressor via the first reflux port. When the amount of intake air is large, the EGR gas in the annular passage flows into the compressor via the second reflux port. This is due to the difference between the pressure in the annular passage and the pressure at the impeller inlet. According to the compressor having such a configuration, the interference between the EGR gas and the fresh air can be suppressed when the intake air amount is small, and the EGR gas can be directly introduced into the impeller inlet when the intake air amount is large.
- the EGR gas contains water vapor. Therefore, condensed water may be generated when the EGR gas is cooled. In particular, when the outside air temperature is low, the temperature of the constituent members of the compressor is also low. Therefore, there is a possibility that the EGR gas is cooled by the constituent members and condensed water is generated.
- the generated condensed water flows into the compressor together with EGR gas and intake air.
- the impeller may be damaged when the compressor flows in. Therefore, it is desirable to suppress the generation of condensed water upstream of the impeller as much as possible.
- the compressor of Patent Document 1 is configured such that when the amount of intake air flowing through the intake passage is large, the intake air flows into the annular passage from the first return port. Therefore, when the outside air temperature is low and the amount of intake air is large, the inner wall of the annular passage may be cooled by the intake air flowing into the annular passage from the first reflux port. Then, as a result of the EGR gas being cooled by the inner wall of the annular passage or the intake air flowing into the annular passage, condensed water may be generated in the annular passage. In addition, the condensed water generated may be combined in the annular passage, and the size of the condensed water may be increased.
- an object of the present invention is to provide a compressor for an exhaust turbocharger that can suppress the generation of condensed water by the constituent members.
- a first invention is a compressor for an exhaust turbocharger, An impeller coupled to the shaft of the exhaust turbine; An inlet communicating with an intake passage of the internal combustion engine upstream of the impeller; An annular space formed to surround the inlet and in communication with the inlet and the EGR passage, The annular space communicates with the inlet at one end on the intake passage side, communicates with the EGR passage on the impeller side rather than the communication portion with the inlet, and is closed on the impeller side than the communication portion with the EGR passage. And The inner diameter of the inlet at the intake passage side end is larger than the inner diameter at the inlet side end of the intake passage.
- the second invention is the first invention, wherein A part of the closed end of the annular space is formed closer to the intake passage than the other closed ends.
- the third invention is the second invention, wherein The part of the closed end is formed in a downstream region of a swirling flow of EGR gas flowing through the annular space in a radial cross section of the inlet including a gas outlet of the EGR passage, The other closed end is formed so as to move away from the inlet passage side of the inlet toward the upstream region of the swirling flow of EGR gas flowing through the annular space.
- the intake passage is bent upstream of the inlet;
- a center axis of the annular space is located on a bent outer side of the intake passage with respect to a rotation center axis of the shaft.
- the gas outlet of the EGR passage is inserted into the annular space, In the radial cross section of the inlet including the gas outlet, the central axis of the EGR passage passing through the center of the gas outlet is inclined toward the tangential side of the sectional circle of the annular space.
- the gas outlet of the EGR passage is disposed to face the closed end of the annular space, In a cross section in the axial direction of the inlet including the gas outlet, a center axis of the EGR passage passing through the center of the gas outlet is inclined toward the rotation center axis of the shaft.
- the EGR gas that has flowed into the annular space from the EGR passage can overflow from the communication portion with the inlet and flow along the outer peripheral wall of the inlet. Contact can be suppressed. Therefore, the temperature drop of EGR gas by the said outer peripheral wall can be suppressed. Moreover, the heat retaining property of the outer peripheral wall can be improved by flowing high-temperature EGR gas along the outer peripheral wall. Therefore, even if condensed water is generated at the inlet, the increase in size can be suppressed by heat transfer from the outer peripheral wall.
- the inner diameter at the inlet passage side end of the inlet is larger than the inner diameter at the inlet side end portion of the intake passage, it is possible to suppress the intake air from flowing into the annular space. Therefore, it is possible to suppress the temperature drop of the EGR gas due to the intake air.
- the EGR gas that has flowed into the annular space from the EGR passage is reflected at the closed end of the annular space and overflows from the communication point with the inlet.
- the EGR gas reflected to the part of the closed end is reflected to the other closed end. It can be overflowed in a shorter time than EGR gas. Therefore, even if condensed water is generated in the annular space, it can be discharged into the inlet before its size increases.
- the partial closed end is formed in the downstream region of the swirling flow of the EGR gas flowing through the annular space, and the swirling flow Since the other closed end is formed so as to move away from the inlet passage side end of the inlet toward the upstream region, the radial flow of EGR gas from the other closed end toward the partially closed end can be smoothed. . Accordingly, it is possible to improve the drainage of the condensed water generated in the annular space.
- the central axis of the annular space is located on the bent outer side of the intake passage with respect to the rotational center axis of the shaft, the intake air is not even when the intake passage is bent upstream of the inlet. It can suppress flowing into the annular space.
- the gas outlet of the EGR passage is inserted into the annular space, and the central axis of the EGR passage passing through the center of the gas outlet is set in the annular space in the radial cross section of the inlet including the gas outlet. Since it is inclined toward the tangential side of the cross-sectional circle, the collision of the EGR gas flowing into the annular space from the EGR passage to the inner peripheral wall can be mitigated. Therefore, the radial flow of EGR gas in the annular space can be made smooth.
- the gas outlet of the EGR passage is disposed so as to face the closed end of the annular space, and EGR passing through the center of the gas outlet in the axial cross section of the inlet including the center of the gas outlet. Since the center axis of the passage is inclined toward the rotation center axis of the shaft, the EGR gas flowing into the annular space from the EGR passage can directly collide with and be reflected at the closed end of the annular space. Therefore, the EGR gas reflected to the closed end can overflow in a short time. Therefore, even if condensed water is generated in the annular space, it can be discharged into the inlet before its size increases.
- FIG. 6 is a diagram showing a modification of the compressor of the first embodiment.
- FIG. 6 is a view showing a modified example of the intake passage connectable to the compressor of the first embodiment.
- FIG. 6 is a diagram showing a modification of the compressor of the first embodiment.
- FIG. 6 is an enlarged cross-sectional view of the vicinity of a compressor 60 according to Embodiment 2.
- FIG. FIG. 10 is a cross-sectional view taken along the line AA ′ of FIG.
- FIG. 6 is a diagram for explaining the flow of LPL gas in a groove.
- 6 is an enlarged cross-sectional view of the vicinity of a compressor 70 according to Embodiment 3.
- FIG. FIG. 6 is a diagram for explaining the flow of LPL gas in a groove.
- FIG. 10 is an enlarged cross-sectional view in the vicinity of a compressor 80 according to a fourth embodiment. It is AA 'sectional drawing of FIG. It is a figure for demonstrating the flow of the LPL gas in the groove
- FIG. FIG. 10 is a diagram showing a modification of the compressor of the fourth embodiment.
- FIG. 10 is an enlarged cross-sectional view of the vicinity of a compressor 90 according to a fifth embodiment. It is AA 'sectional drawing of
- FIG. 1 is a diagram for explaining an overall configuration of an EGR system including a compressor according to the first embodiment.
- the EGR system includes an engine 10 as an internal combustion engine.
- Each cylinder of the engine 10 is provided with a piston, an intake valve, an exhaust valve, a fuel injector, and the like. Note that the number of cylinders and the cylinder arrangement of the engine 10 are not particularly limited.
- the EGR system has a supercharger 12.
- the supercharger 12 includes a turbine 16 provided in the exhaust passage 14 and a compressor 20 provided in the intake passage 18.
- the turbine 16 and the compressor 20 are connected to each other.
- the turbine 16 receives the exhaust pressure and rotates, thereby driving the compressor 20 and compressing the gas flowing into the compressor 20.
- the intake passage 18 is provided with an intercooler 22 for cooling the compressed gas.
- the EGR system includes an EGR passage 24 for introducing a low pressure loop (LPL) EGR gas.
- the EGR passage 24 connects the exhaust passage 14 downstream of the turbine 16 and the compressor 20.
- An EGR cooler 26 that cools the EGR gas is provided in the middle of the EGR passage 24.
- An EGR valve 28 that controls the flow rate of EGR gas is provided in the EGR passage 24 downstream of the EGR cooler 26.
- the low-pressure loop EGR gas is referred to as “LPL gas”.
- FIG. 2 is an enlarged cross-sectional view of the vicinity of the compressor 20 of FIG.
- the compressor 20 includes an impeller 30, a housing 32, and a connecting shaft 34.
- the impeller 30 is connected to an impeller (not shown) of the turbine 16 via a connecting shaft 34.
- the housing 32 supports the connecting shaft 34 rotatably.
- the housing 32 includes an inlet 36 for introducing gas to the suction side of the impeller 30, an annular groove 38 formed on the outer periphery of the inlet 36, a spiral scroll 40 formed on the outer periphery of the impeller 30, and the impeller 30.
- a diffuser 42 that communicates between the discharge side and the scroll 40 is formed.
- the inner diameter ID 38 of the groove 38 is processed to be larger than the inner diameter ID 18 of the gas outlet end (inlet 36 side end) of the intake passage 18.
- the groove 38 communicates with the inlet 36 on the intake passage 18 side.
- the impeller 30 side of the groove 38 is closed.
- a gas outlet of the EGR passage 24 is connected to the middle of the groove 38.
- the downstream end of the EGR passage 24 including the gas outlet is disposed orthogonal to the groove 38.
- 3 is a cross-sectional view taken along the line AA ′ of FIG. As shown in FIG. 3, the gas outlet 44 of the EGR passage 24 is inserted into the housing 32 and communicates with the groove 38.
- FIG. 4 is a view for explaining the gas flow in the compressor 20 and the heat transfer phenomenon in the housing 32.
- the LPL gas that has flowed into the groove 38 from the EGR passage 24 collides with the inner peripheral wall of the groove 38 and then diffuses throughout the groove 38 while turning along the inner peripheral wall. Since the impeller 30 side of the groove 38 is closed, the LPL gas in the groove 38 overflows from the intake passage 18 side. Further, as shown in FIG. 4, intake air flows into the compressor 20 from the intake passage 18 side. Therefore, the LPL gas overflowing from the groove 38 is sent to the impeller 30 together with the intake air.
- the inner diameter ID 38 is processed to be larger than the inner diameter ID 18 . Therefore, as shown in FIG. 4, the intake air flowing into the inlet 36 from the intake passage 18 side is sent to the impeller 30 without flowing into the groove 38. Further, the LPL gas overflowing from the groove 38 flows along the outer peripheral wall of the inlet 36. That is, in the housing 32, the intake air flows in the central portion and the LPL gas flows in the outer peripheral portion thereof.
- the compressor 20 of the present embodiment since the above-described gas flow can be formed, mixing of the LPL gas and the intake air is suppressed. Therefore, the temperature drop due to the intake air of the LPL gas can be suppressed.
- the LPL gas can flow along the outer peripheral wall of the inlet 36, the contact of the intake air with the outer peripheral wall can be suppressed. Therefore, it is possible to suppress the temperature drop of the LPL gas due to the outer peripheral wall. Therefore, generation
- the heat retaining property of the outer peripheral wall of the inlet 36 can be improved.
- the temperature of the outer peripheral wall of the inlet 36 increases due to heat transfer from the LPL gas. (FIG. 4 (i)).
- the temperature of the outer peripheral wall rises also in the vicinity of the impeller 30 due to heat transfer from the LPL gas (FIG. 4 (ii)).
- the temperature of the outer peripheral wall also rises due to heat transfer from the LPL gas (about 100 to 150 ° C.) in the scroll 40 (FIG. 4 (iii)). Therefore, even if condensed water is generated in the inlet 36, the increase in size can be suppressed by heat transfer from the outer peripheral wall.
- FIG. 5 is a diagram for explaining the flow of gas in a conventional compressor.
- the conventional compressor 50 has an EGR passage 54 connected to the compressor side end of the intake passage 52. Since the downstream side of the EGR passage 54 is bent in an L shape, the LPL gas can flow along the outer peripheral wall of the inlet 56 and the intake air can flow inside thereof. However, since there is a distance from the connection port of the EGR passage 54 to the impeller 58, the LPL gas and the intake air may be mixed upstream of the impeller 58, and the temperature of the LPL gas may decrease. In addition, the LPL gas may be cooled in the intake passage 52 at the L-shaped bent portion, and condensed water may be generated.
- the gas inlet end (the end on the intake passage 18 side) of the inlet 36 is closer to the impeller 30 than the gas outlet end portion of the intake passage 18.
- LPL gas can be introduced. Therefore, mixing of the LPL gas and the intake air upstream of the impeller 30 can be suppressed.
- the LPL gas overflowing from the groove 38 can be made to flow along the outer peripheral wall of the inlet 36 with improved heat retention. Therefore, generation
- FIG. 6 is a view showing a modification of the compressor of the first embodiment.
- the groove diameter of the groove 38 may be increased as it goes from the intake passage 18 toward the impeller 30.
- the groove diameter of the groove 38 may be reduced as it goes from the intake passage 18 to the impeller 30.
- the groove width of the groove 38 may be increased as it goes from the intake passage 18 toward the impeller 30.
- the inner diameter ID 36 of the gas inlet end of the inlet 36 if it is processed greater than the gas outlet end of the inner diameter ID 18 of the intake passage 18 can be suppressed from flowing into the groove 38 of the intake air. Therefore, as long as the inner diameter ID 36 is processed to be larger than the inner diameter ID 18 , the shape of the groove 38 can be variously modified.
- a closed end 46 of the groove 38 may be formed immediately downstream of the gas outlet of the EGR passage 24. If the impeller 30 side is closed from the gas outlet of the EGR passage 24 in the groove 38, the flow of the LPL gas described with reference to FIG. 4 can be generated. Therefore, as long as the impeller 30 side is closed from the gas outlet of the EGR passage 24, the groove depth of the groove 38 (distance from the gas inlet end of the inlet 36 to the closed end 46) can be variously modified.
- FIG. 7 is a view showing a modification of the intake passage connectable to the compressor of the first embodiment.
- the gas outlet end portion of the intake passage 48 is partially narrowed in inner diameter and is expanded again on the compressor 20 side. Even with such an intake passage 48, intake air flowing into the inlet 36 from the intake passage 18 side can be sent to the impeller 30 without flowing into the groove 38.
- the inner diameter ID 36 of the gas inlet end of the inlet 36 to the extent that is processed larger than the minimum inner diameter ID 48 at the gas outlet end of the intake passage 48, the shape of the gas outlet end portion of the intake passage 18 various modifications of Is possible.
- the EGR passage 24 has one gas outlet, but there may be a plurality of gas outlets.
- FIG. 8 is a view showing a modification of the compressor of the first embodiment. As shown in FIG. 8, two gas outlets 44 may be provided. If the EGR passage 24 communicates with the EGR passage 24 on the impeller 30 side of the groove 38 from the communication portion with the inlet 36, and the impeller 30 side is closed with respect to the communication portion of the groove 38 with the EGR passage 24, FIG. It is possible to generate a flow of LPL gas. Therefore, as long as such a positional relationship is established, the number of gas outlets 44 can be variously modified.
- the turbine 16 is the “exhaust turbine” of the first invention
- the intake passage 18 is the “intake passage” of the invention
- the EGR passage 24 is the “EGR passage” of the invention.
- the impeller 30 corresponds to the “impeller” of the invention
- the connecting shaft 34 corresponds to the “shaft” of the invention
- the inlet 36 corresponds to the “inlet” of the invention
- the groove 38 corresponds to the “annular space” of the invention. ing.
- Embodiment 2 a second embodiment of the present invention will be described with reference to FIGS.
- the groove 38 and the EGR passage are orthogonal to each other as in the first embodiment.
- this embodiment differs from the EGR passage 24 of the first embodiment in that the gas outlet of this EGR passage is arranged in the tangential direction of the cross-sectional circle of the groove 38.
- this difference will be mainly described.
- FIG. 9 is an enlarged cross-sectional view of the vicinity of the compressor 60 of the second embodiment.
- the EGR passage 62 is disposed orthogonally to the groove 38.
- the gas outlet 64 of the EGR passage 62 opens in the groove 38.
- 10 is a cross-sectional view taken along the line AA ′ of FIG.
- the EGR passage 62 is inserted into the housing 32.
- the central axis CA 62 of the EGR passage 62 passing through the center C 64 of the gas outlet 64 is parallel with the tangential line TL 38 of the cross section circle described by the inner peripheral wall of the groove 38.
- FIG. 11 is a view for explaining the flow of the LPL gas in the groove 38.
- the LPL gas that has flowed into the groove 38 from the EGR passage 24 collides with the inner peripheral wall of the groove 38 the flow of the LPL gas may be disturbed.
- the LPL gas flowing into the groove 38 from the EGR passage 62 can be swung along the inner peripheral wall without colliding with the inner peripheral wall of the groove 38. It becomes possible. Therefore, since the flow rate of the LPL gas flowing in the groove 38 can be made uniform, the temperature of the outer peripheral wall of the inlet 36 can be increased uniformly. 10 and 11, the turning direction of the LPL gas is the same as the rotation direction of the impeller, but may be reversed.
- the central axis CA 62 is arranged in parallel with the tangent TL 38.
- the central axis CA 62 may not be parallel to the tangent TL 38 . If the central axis CA 62 is not perpendicular to the tangent TL 38 (that is, if the central axis CA 62 is inclined toward the tangential TL 38 ), the collision of the LPL gas with the inner peripheral wall of the groove 38 can be mitigated. Therefore, as long as the central axis CA 62 are inclined tangentially TL 38 side, the positional relationship between the center axis CA 62 and the tangent TL 38 can be modified in various ways.
- the gas outlet 44 is the “gas outlet” of the fifth invention
- the center axis CA 62 is the “center axis” of the invention
- the tangent TL 38 is the “tangent” of the invention.
- Embodiment 3 of the present invention will be described with reference to FIGS.
- an EGR passage is connected to the groove 38 as in the first embodiment.
- the gas outlet of the EGR passage is disposed so as to face the closed end of the groove 38 on the impeller 30 side, and the EGR passage is inclined toward the connecting shaft 34 side. This is different from the EGR passage 24 of the first embodiment.
- this difference will be mainly described.
- FIG. 12 is an enlarged cross-sectional view of the vicinity of the compressor 70 of the third embodiment.
- the gas outlet 74 of the EGR passage 72 is disposed so as to face the closed end 76 of the groove 38.
- the central axis CA 72 of the EGR passage 72 passing through the center C 74 of the gas outlet 74 is inclined with respect to the rotation center axis CA 34 of the connecting shaft 34.
- FIG. 13 is a view for explaining the flow of the LPL gas in the groove 38.
- FIG. 13 (a) corresponds to the flow of LPL gas flowing into the groove 38 from the EGR passage 72
- FIG. 13 (b) corresponds to the flow of LPL gas flowing into the groove 38 from the EGR passage 24 of the first embodiment. is doing.
- the EGR gas overflows from the groove 38, flows along the outer peripheral wall of the inlet 36, and is sent to the impeller 30. This point is as described in the first embodiment.
- the LPL gas that has flowed into the groove 38 from the EGR passage 72 violently collides with the closed end 76 and is reflected, and overflows from the intake passage 18 side (FIG. 13A).
- the LPL gas that has flowed into the groove 38 from the EGR passage 24 collides with the closed end 46 after colliding with the inner peripheral wall of the groove 38, is reflected, and overflows from the intake passage 18 side (FIG. 13B). This is due to the fact that the center axis CA 24 of the EGR passage 24 passing through the center C 44 of the gas outlet 44 is perpendicular to the rotation center axis CA 34 .
- the LPL gas flowing in from the EGR passage 72 can be directly collided with the closed end 76 and reflected. Therefore, a strong LPL gas flow from the closed end 76 toward the intake passage 18 can be generated in the groove 38. Therefore, even if the condensed water shown in FIG. 13 is generated in the groove 38, the condensed water can be discharged out of the groove 38 in this flow.
- the gas outlet 74 is the “gas outlet” of the sixth invention
- the closed end 76 is the “closed end” of the invention
- the center axis CA 72 is the “center axis” of the invention.
- the rotation center axis CA 34 corresponds to the “rotation center axis” of the present invention.
- FIG. 14 is an enlarged cross-sectional view of the vicinity of the compressor 80 according to the fourth embodiment.
- the groove depth GD 82 of the groove 82 (the distance from the gas inlet end of the inlet 36 to the closed end 84) is the groove depth GD 38 of the groove 38 (from the gas inlet end of the inlet 36 to the closed end). (Distance up to 76).
- FIG. 15 is a cross-sectional view taken along the line AA ′ of FIG. As shown in FIG. 15, the groove 82 is formed on the opposite side of the gas outlet 44.
- the arrows in the figure indicate the flow of LPL gas. That is, the groove 82 is formed in the downstream region of the swirling flow of the LPL gas that flows from the EGR passage 24.
- the EGR passage 24 is connected to the housing 32 from above in the gravitational direction (vertical direction). That is, the groove 82 is located below the gravitational direction.
- FIG. 16 is a view for explaining the flow of the LPL gas in the grooves 38 and 82.
- FIG. 16A corresponds to the flow of LPL gas in the groove 82
- FIG. 16B corresponds to the flow of LPL gas in the groove 38.
- the EGR gas overflows from the grooves 38 and 82, flows along the outer peripheral wall of the inlet 36, and is sent to the impeller 30. This point is as described in the first embodiment.
- the groove depth GD 82 is processed to be shallower than the groove depth GD 38
- the LPL gas in the groove 82 overflows in a shorter time than the LPL gas in the groove 38.
- the arrow shown in FIG. 16 has shown the movement distance per unit time of LPL gas. That is, the EGR gas in the groove 82 moves to a location closer to the impeller 30 than the EGR gas in the groove 38.
- the LPL gas in the groove 82 can be sent to the impeller 30 in a shorter time than the LPL gas in the groove 38. Therefore, as shown in FIG. 16, even if condensed water is generated in the groove 38, it can be sent out from the groove 82 to the impeller 30 before the size of the condensed water increases.
- the groove 82 is located below the gravity direction. Therefore, the condensed water can be sent out from the groove 82 more smoothly.
- the groove depth GD 38 is constant. However, the groove depth increases from the groove 82 toward the upstream region of the swirling flow of EGR gas (as it approaches the gas outlet 44 from the groove 82). GD 38 may be processed so as to gradually become deeply. If the depth GD 38 is processed in this manner, the condensed water can be sent out from the groove 82 more smoothly.
- FIG. 17 is a diagram showing a modification of the compressor of the fourth embodiment. As shown in FIG. 17A, the gas outlet 44 may be provided below the position of FIG. 15 in the gravity direction, and the groove 82 may be formed above the position of FIG.
- FIG. 17B is a diagram showing an example of the location where the groove 82 is formed in the case of FIG.
- FIG. 17 (b) when the central axes CA 62 and TL 38 are parallel, the groove 82 can be formed in the downstream region of the swirling flow of the EGR gas flowing from the gas outlet 64.
- FIG. 17C is a diagram showing an example of a location where the groove 82 is formed when two gas outlets 64 are arranged. As shown in FIG. 17C, when two gas outlets 64 are arranged, the grooves 82 can be formed in each of the downstream areas of the swirling flow of the EGR gas flowing from the gas outlet 64.
- the present embodiment can be variously modified.
- the closed end 84 corresponds to the “partially closed end” of the second invention, and the closed end 76 corresponds to the “other closed end” of the invention.
- FIG. 18 is an enlarged cross-sectional view of the vicinity of the compressor 90 according to the fifth embodiment.
- the intake passage 92 is bent toward the EGR passage 24 side. Also, it does not coincide with the center axis CA 38 of the rotation center axis CA 34 and the groove 38 of the connecting shaft 34.
- the center axis CA 38 is offset to the outer side of the bend having a large radius of curvature Rb (> Ra) with respect to the rotation center axis CA 34 .
- 19 is a cross-sectional view taken along the line AA ′ of FIG. As shown in FIG. 19, the center axis CA 38 is offset in a direction away from the gas outlet 44 with respect to the rotation center axis CA 34 .
- the center axis CA 38 corresponds to the “center axis” of the fourth invention
- the rotation center axis CA 34 corresponds to the “rotation center axis” of the invention.
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- Supercharger (AREA)
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Abstract
Description
排気タービンのシャフトと連結されたインペラと、
前記インペラの上流において内燃機関の吸気通路と連通するインレットと、
前記インレットを取り囲むように形成され、前記インレットおよびEGR通路と連通する環状空間と、を備え、
前記環状空間は、前記吸気通路側の一端において前記インレットと連通し、前記インレットとの連通箇所よりも前記インペラ側において前記EGR通路と連通し、前記EGR通路との連通箇所よりも前記インペラ側が閉塞され、
前記インレットの吸気通路側端における内径は、前記吸気通路のインレット側端部における内径よりも大きいことを特徴とする。
前記環状空間の一部の閉塞端が、他の閉塞端よりも前記吸気通路側に形成されていることを特徴とする。
前記一部の閉塞端は、前記EGR通路のガス出口を含む前記インレットの径方向の断面において前記環状空間を流れるEGRガスの旋回流の下流域に形成され、
前記他の閉塞端は、前記環状空間を流れるEGRガスの旋回流の上流域に向かうほど、前記インレットの吸気通路側から遠ざかるように形成されていることを特徴とする。
前記吸気通路は、前記インレットの上流において屈曲し、
前記環状空間の中心軸線が、前記シャフトの回転中心軸線よりも前記吸気通路の屈曲外側に位置することを特徴とする。
前記EGR通路のガス出口は、前記環状空間に挿入され、
前記ガス出口を含む前記インレットの径方向の断面において、前記ガス出口の中心を通る前記EGR通路の中心軸線が、前記環状空間の断面円の接線側に傾斜していることを特徴とする。
前記EGR通路のガス出口は、前記環状空間の閉塞端と向かい合うように配置され、
前記ガス出口を含む前記インレットの軸方向の断面において、前記ガス出口の中心を通る前記EGR通路の中心軸線が、前記シャフトの回転中心軸線側に傾斜していることを特徴とする。
[システム構成の説明]
先ず、図1乃至図8を参照しながら、本発明の実施の形態1について説明する。
図1は、実施の形態1のコンプレッサを含むEGRシステムの全体構成を説明するための図である。図1に示すように、EGRシステムは、内燃機関としてのエンジン10を備えている。エンジン10の各気筒には、ピストン、吸気弁、排気弁、燃料インジェクタ等が設けられている。なお、エンジン10の気筒数および気筒配置は特に限定されない。
図2は、図1のコンプレッサ20近傍の断面拡大図である。図2に示すように、コンプレッサ20は、インペラ30とハウジング32と連結軸34とを備えている。インペラ30は連結軸34を介してタービン16のインペラ(図示しない)に接続されている。ハウジング32は、連結軸34を回転自在に支持するものである。ハウジング32には、インペラ30の吸引側にガスを導くインレット36と、インレット36の外周に形成された円環状の溝38と、インペラ30の外周に形成された渦巻き状のスクロール40と、インペラ30の吐出側とスクロール40とを連通するディフューザ42とが形成されている。
図4は、コンプレッサ20内のガスの流れおよびハウジング32内の伝熱現象を説明するための図である。図4に示すように、EGR通路24から溝38に流入したLPLガスは、溝38の内周壁に衝突した後、この内周壁に沿って旋回しながら溝38内の全域に拡散する。溝38のインペラ30側は閉塞されているので、溝38内のLPLガスは吸気通路18側から溢れ出す。また、図4に示すように、コンプレッサ20には、吸気通路18側から吸入空気が流入する。そのため、溝38から溢れ出したLPLガスは、吸入空気と共にインペラ30に送られる。
次に、図9乃至図11を参照しながら、本発明の実施の形態2について説明する。
本実施形態のコンプレッサにおいては、上記実施の形態1同様、溝38とEGR通路とが直交している。但し、本実施形態においては、このEGR通路のガス出口を溝38の断面円の接線方向に配置する点で上記実施の形態1のEGR通路24と異なる。以下、この相違点を中心に説明する。
図9は、実施の形態2のコンプレッサ60近傍の断面拡大図である。EGR通路62は、溝38に直交配置されている。図9に示すように、EGR通路62のガス出口64は、溝38において開口している。図10は、図9のA-A´断面図である。図10に示すように、EGR通路62はハウジング32内に挿入されている。また、ガス出口64の中心C64を通るEGR通路62の中心軸線CA62は、溝38の内周壁によって描かれる断面円の接線TL38と平行となっている。
図11は、溝38内のLPLガスの流れを説明するための図である。上記実施の形態1において、EGR通路24から溝38に流入したLPLガスは、溝38の内周壁に衝突するので、LPLガスの流れが乱れる可能性がある。この点、図11に示すように、コンプレッサ60によれば、EGR通路62から溝38に流入したLPLガスを、溝38の内周壁に衝突させることなく、当該内周壁に沿って旋回させることが可能となる。従って、溝38内を流れるLPLガスの流量を均一化できるので、インレット36の外周壁の温度を一様に上昇させることが可能となる。なお、図10,11において、LPLガスの旋回方向はインペラの回転方向と同一であるとしているが、逆でもよい。
次に、図12乃至図13を参照しながら、本発明の実施の形態3について説明する。
本実施形態のコンプレッサにおいては、上記実施の形態1同様、溝38にEGR通路が接続されている。但し、本実施形態においては、このEGR通路のガス出口を溝38のインペラ30側の閉塞端と向かい合うように配置し、尚且つ、このEGR通路を連結軸34側に傾斜させた点で上記実施の形態1のEGR通路24と異なる。以下、この相違点を中心に説明する。
図12は、実施の形態3のコンプレッサ70近傍の断面拡大図である。図12に示すように、EGR通路72のガス出口74は、溝38の閉塞端76と向かい合うように配置されている。また、ガス出口74の中心C74を通るEGR通路72の中心軸線CA72は、連結軸34の回転中心軸線CA34に対して傾斜している。
図13は、溝38内のLPLガスの流れを説明するための図である。図13(a)がEGR通路72から溝38に流入したLPLガスの流れに、図13(b)が上記実施の形態1のEGR通路24から溝38に流入したLPLガスの流れに、それぞれ対応している。図13に示すように、EGRガスは、溝38から溢れ出してインレット36の外周壁に沿って流れ、インペラ30に送られる。この点については、上記実施の形態1で説明したとおりである。但し、EGR通路72から溝38に流入したLPLガスは、閉塞端76に勢い良く衝突して反射し、吸気通路18側から溢れ出す(図13(a))。他方、EGR通路24から溝38に流入したLPLガスは、溝38の内周壁に衝突した後に閉塞端46に衝突、反射し、吸気通路18側から溢れ出す(図13(b))。これは、ガス出口44の中心C44を通るEGR通路24の中心軸線CA24が、回転中心軸線CA34に対して直角であることに起因している。
[実施の形態4の特徴]
次に、図14乃至図17を参照しながら、本発明の実施の形態4について説明する。
図14は、実施の形態4のコンプレッサ80近傍の断面拡大図である。図14に示すように、溝82の溝深さGD82(インレット36のガス入口端から閉塞端84までの距離)は、溝38の溝深さGD38(インレット36のガス入口端から閉塞端76までの距離)よりも浅く加工されている。図15は、図14のA-A´断面図である。図15に示すように、溝82は、ガス出口44の反対側に形成されている。図中の矢印はLPLガスの流れを示している。即ち、溝82は、EGR通路24から流入したLPLガスの旋回流の下流域に形成されている。なお、本実施形態において、EGR通路24は、重力方向(鉛直方向)上方からハウジング32に接続している。つまり、溝82は、重力方向下方に位置している。
図16は、溝38,82内のLPLガスの流れを説明するための図である。図16(a)が溝82内のLPLガスの流れに、図16(b)が溝38内のLPLガスの流れに、それぞれ対応している。図16に示すように、EGRガスは、溝38,82から溢れ出してインレット36の外周壁に沿って流れ、インペラ30に送られる。この点については、上記実施の形態1で説明したとおりである。但し、コンプレッサ80においては、溝深さGD82が溝深さGD38よりも浅く加工されているので、溝82内のLPLガスは、溝38内のLPLガスよりも短時間で溢れ出す。図16に示す矢印は、LPLガスの単位時間当たりの移動距離を示している。即ち、溝82内のEGRガスは、溝38内のEGRガスに比べて、よりインペラ30に近い箇所まで移動する。
[実施の形態5の特徴]
次に、図18乃至図19を参照しながら、本発明の実施の形態5について説明する。
図18は、実施の形態5のコンプレッサ90近傍の断面拡大図である。図18に示すように、吸気通路92はEGR通路24側に屈曲している。また、連結軸34の回転中心軸線CA34と溝38の中心軸線CA38とは一致していない。具体的に、中心軸線CA38は、回転中心軸線CA34に対して、曲率半径Rb(>Ra)の大きい屈曲外側にオフセットされている。図19は、図18のA-A´断面図である。図19に示すように、中心軸線CA38は、回転中心軸線CA34よりも、ガス出口44から遠ざかる方向にオフセットされている。
吸気通路92が屈曲していると吸入空気に遠心力が働くので、屈曲外側に位置する溝38bには、屈曲内側に位置する溝38aに比べて吸入空気が流入し易くなる。この点、コンプレッサ90においては、中心軸線CA38が屈曲外側にオフセットされているので、屈曲外側位置する溝38bへの吸入空気の流入を抑制できる。
16 タービン
18,52,92 吸気通路
20,50,60,70,80,90 コンプレッサ
24,54,62,72 EGR通路
30,58 インペラ
32 ハウジング
34 連結軸
36,56 インレット
38,82 溝
44,64,74 ガス出口
46,76,84 閉塞端
Claims (6)
- 排気タービンのシャフトと連結されたインペラと、
前記インペラの上流において内燃機関の吸気通路と連通するインレットと、
前記インレットを取り囲むように形成され、前記インレットおよびEGR通路と連通する環状空間と、を備え、
前記環状空間は、前記吸気通路側の一端において前記インレットと連通し、前記インレットとの連通箇所よりも前記インペラ側において前記EGR通路と連通し、前記EGR通路との連通箇所よりも前記インペラ側が閉塞され、
前記インレットの吸気通路側端における内径は、前記吸気通路のインレット側端部における内径よりも大きいことを特徴とする排気ターボ過給機のコンプレッサ。 - 前記環状空間の一部の閉塞端が、他の閉塞端よりも前記吸気通路側に形成されていることを特徴とする請求項1に記載の排気ターボ過給機のコンプレッサ。
- 前記一部の閉塞端は、前記EGR通路のガス出口を含む前記インレットの径方向の断面において前記環状空間を流れるEGRガスの旋回流の下流域に形成され、
前記他の閉塞端は、前記環状空間を流れるEGRガスの旋回流の上流域に向かうほど、前記インレットの吸気通路側端から遠ざかるように形成されていることを特徴とする請求項2に記載の排気ターボ過給機のコンプレッサ。 - 前記吸気通路は、前記インレットの上流において屈曲し、
前記環状空間の中心軸線が、前記シャフトの回転中心軸線よりも前記吸気通路の屈曲外側に位置することを特徴とする請求項1乃至3何れか1項に記載の排気ターボ過給機のコンプレッサ。 - 前記EGR通路のガス出口は、前記環状空間に挿入され、
前記ガス出口を含む前記インレットの径方向の断面において、前記ガス出口の中心を通る前記EGR通路の中心軸線が、前記環状空間の断面円の接線側に傾斜していることを特徴とする請求項1乃至4何れか1項に記載の排気ターボ過給機のコンプレッサ。 - 前記EGR通路のガス出口は、前記環状空間の閉塞端と向かい合うように配置され、
前記ガス出口を含む前記インレットの軸方向の断面において、前記ガス出口の中心を通る前記EGR通路の中心軸線が、前記シャフトの回転中心軸線側に傾斜していることを特徴とする請求項1乃至5何れか1項に記載の排気ターボ過給機のコンプレッサ。
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JP2015512220A JP6004091B2 (ja) | 2013-04-16 | 2013-04-16 | 排気ターボ過給機のコンプレッサ |
PCT/JP2013/061284 WO2014170954A1 (ja) | 2013-04-16 | 2013-04-16 | 排気ターボ過給機のコンプレッサ |
CN201380075505.8A CN105102787B (zh) | 2013-04-16 | 2013-04-16 | 排气涡轮增压器的压缩机 |
US14/784,327 US10329999B2 (en) | 2013-04-16 | 2013-04-16 | Compressor of exhaust turbocharger |
EP13882463.6A EP2987983B1 (en) | 2013-04-16 | 2013-04-16 | Compressor for exhaust-gas turbo-supercharger |
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2013
- 2013-04-16 JP JP2015512220A patent/JP6004091B2/ja not_active Expired - Fee Related
- 2013-04-16 WO PCT/JP2013/061284 patent/WO2014170954A1/ja active Application Filing
- 2013-04-16 EP EP13882463.6A patent/EP2987983B1/en active Active
- 2013-04-16 US US14/784,327 patent/US10329999B2/en active Active
- 2013-04-16 CN CN201380075505.8A patent/CN105102787B/zh not_active Expired - Fee Related
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Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
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GB2535996A (en) * | 2015-02-27 | 2016-09-07 | Ford Global Tech Llc | A low condensation LP EGR System |
GB2535996B (en) * | 2015-02-27 | 2019-12-11 | Ford Global Tech Llc | A low condensation LP EGR System |
DE102015209666A1 (de) * | 2015-05-27 | 2016-12-01 | Volkswagen Aktiengesellschaft | Verdichter |
WO2016188712A1 (de) | 2015-05-27 | 2016-12-01 | Volkswagen Aktiengesellschaft | Verdichter, abgasturbolader und brennkraftmaschine |
US10655642B2 (en) | 2015-05-27 | 2020-05-19 | Volkswagen Aktiengesellschaft | Compressor, exhaust gas turbocharger and internal combustion machine |
JP2017015026A (ja) * | 2015-07-02 | 2017-01-19 | 本田技研工業株式会社 | コンプレッサ構造 |
JP2017015025A (ja) * | 2015-07-02 | 2017-01-19 | 本田技研工業株式会社 | コンプレッサ構造 |
JP7521367B2 (ja) | 2020-10-05 | 2024-07-24 | 三菱自動車工業株式会社 | 内燃機関 |
WO2022264856A1 (ja) * | 2021-06-16 | 2022-12-22 | 三菱重工エンジン&ターボチャージャ株式会社 | 配管分岐装置及びコンプレッサ |
Also Published As
Publication number | Publication date |
---|---|
CN105102787A (zh) | 2015-11-25 |
EP2987983A4 (en) | 2016-04-27 |
JP6004091B2 (ja) | 2016-10-05 |
US10329999B2 (en) | 2019-06-25 |
US20160069302A1 (en) | 2016-03-10 |
EP2987983A1 (en) | 2016-02-24 |
JPWO2014170954A1 (ja) | 2017-02-16 |
EP2987983B1 (en) | 2018-08-01 |
CN105102787B (zh) | 2017-07-11 |
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