WO2014033878A1 - 遠心圧縮機 - Google Patents
遠心圧縮機 Download PDFInfo
- Publication number
- WO2014033878A1 WO2014033878A1 PCT/JP2012/072038 JP2012072038W WO2014033878A1 WO 2014033878 A1 WO2014033878 A1 WO 2014033878A1 JP 2012072038 W JP2012072038 W JP 2012072038W WO 2014033878 A1 WO2014033878 A1 WO 2014033878A1
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- WIPO (PCT)
- Prior art keywords
- housing
- guide
- intake
- flow
- guide vane
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage pumps
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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
- F02B37/22—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
- F02B37/225—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 air passages
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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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/04—Mechanical drives; Variable-gear-ratio drives
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/024—Units comprising pumps and their driving means the driving means being assisted by a power recovery turbine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/02—Surge control
- F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/02—Surge control
- F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
- F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
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- 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
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
- F01D17/162—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for axial flow, i.e. the vanes turning around axes which are essentially perpendicular to the rotor centre line
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/50—Inlet or outlet
- F05D2250/51—Inlet
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to a centrifugal compressor having an impeller wheel rotated by a rotating shaft, and more particularly to a centrifugal compressor incorporated in an exhaust turbocharger.
- the compressor of such an exhaust turbocharger has a surge flow rate at which surging that is a pulsation of the entire system occurs, as shown in the normal compressor of the performance characteristic comparison table in which the pressure ratio in FIG. 10 is the vertical axis and the flow rate is the horizontal axis.
- the operation is stably performed in a flow rate range from the choke flow (the left line in the figure) to the choke flow (the right line in the figure) where choking occurs and the flow rate does not increase any more.
- Patent Document 1 discloses a technique in which a recirculation flow path for recirculating a part of intake gas sucked by an impeller wheel is provided in a turbocharger housing.
- the impeller wheel 201 of the centrifugal compressor 200 includes a plurality of rotatable blades 204 within a housing 202, the housing 202 having an inner wall disposed proximate to a radially outer edge 204a of the blade 204.
- the intake port of the centrifugal compressor 200 includes an outer annular wall 207 that forms a gas suction port 208 and an inner annular wall 209 that extends into the outer annular wall 207 and forms an inducer portion 210.
- An annular gas channel 211 is formed between the annular walls 209 and 207.
- the downstream opening 213 communicates the housing surface 205 through which the blades 204 pass and the annular channel 211.
- the upstream opening connects the annular flow path 211 and the inducer part 210, that is, the intake port suction part.
- An inlet guide vane 214 is provided inside the inducer section 210 downstream of the upstream opening to induce a leading spiral in the gas flow through the inducer section 210.
- the inner annular wall 209 and the outer annular wall 207 extend in the upstream direction and accommodate the inlet guide vane device.
- This inlet guide vane device includes a plurality of inlet guide vanes 214 extending between the central nose cone 215 and the inner annular wall 209.
- the air inlet guide vane 214 is swept forward with respect to the rotation direction of the impeller wheel 201, and induces a leading vortex in the air flow reaching the impeller wheel 201.
- the leading vortex flow causes a surge margin of the compressor. (Surge limit) is improved. That is, the preceding spiral flow reduces the flow causing the compressor to surge. (Refer to RCC + guide vanes in Fig. 10)
- the central nose cone 215 is located in the central space in the inner annular wall on the front surface of the impeller wheel. It is clear that the choke flow is reduced although it is not visible in FIG. 10, and it is also difficult to fabricate the central nose cone 215 and install the central nose cone on the central axis of the guide vane. That is, the conventional guide vanes that generate the swirl flow are provided with a cone-shaped member that guides the intake air to the guide vanes at the center, which increases the air resistance and reduces the choke flow rate.
- the inlet guide vane 214 is provided to induce a leading spiral in the gas flow through the inducer 210, but the vane angle of the inlet guide vane 214 is fixed. Therefore, the swirling direction of the swirling flow can always be only constant. In particular, since the air inlet guide vane 214 has a constant blade angle, a constant air resistance is always generated with respect to the intake air flow.
- the present invention has a guide vane located directly on the inner peripheral side of the housing on the front surface of the impeller wheel without providing a central nose cone.
- the purpose is to improve the margin.
- the present invention makes it possible to change the inclination angle of the guide blades that generate the swirl flow, to control the inclination angle suitable for the operating state of the compressor, to reduce the air resistance, to suppress the reduction of the choke flow rate, and
- the purpose is to expand the operating range of the compressor by reducing the surge flow rate.
- the present invention provides a housing having an air inlet opening in the direction of the rotation axis of the centrifugal compressor and an air intake passage connected to the air inlet, An impeller wheel that is disposed inside the housing so as to be rotatable about the rotation shaft, and compresses intake gas flowing from the intake port; A plurality of circumferentially arranged along the inner peripheral wall of the housing between the intake port and the impeller wheel, and a guide vane that imparts a swirl flow around a rotation axis to the intake gas flowing from the intake port; A central intake flow passage that is formed on the inner peripheral side of the plurality of guide vanes and flows into the impeller wheel without passing through the guide vanes, and a central intake flow passage that flows through the intake ports; And a guide vane moving mechanism that interlocks and changes an inclination angle of the plurality of guide vanes with respect to the rotation axis direction.
- the surge flow rate (minimum flow rate) is reduced, the surge margin is improved, and the intake gas flow resistance in the central intake flow passage is small. Therefore, a decrease in the choke flow rate (maximum flow rate) can be suppressed, and the operating range can be expanded.
- the inclination angle of the guide vanes variable, it is possible to further expand the reduction of the surge flow rate (minimum flow rate) and the suppression of the reduction of the choke flow rate (maximum flow rate). That is, according to the operating state of the internal combustion engine, that is, according to the flow rate passing through the compressor, the blade inclination angle of the guide blade can be changed.For example, during low flow operation, the blade inclination angle is increased, The flow rate of the surging of the compressor can be made smaller by the swirling flow, and when the flow rate is large, the blade inclination angle can be reduced to suppress the reduction of the choke flow rate.
- the guide blade has a guide blade main shaft, the guide blade is rotated about the guide blade main shaft, and the guide blade main shaft extends toward the center of the intake passage. And an outer end portion of the guide blade main shaft is positioned outside the housing through the peripheral wall of the intake passage, and is connected to the guide blade movable mechanism.
- the guide blade main shafts of the plurality of guide blades arranged in the circumferential direction of the intake passage are rotated from the outside of the housing, respectively, so that the guide is not affected to the flow of the intake gas flowing through the intake passage.
- the wing inclination angle can be controlled. For this reason, it is possible to change the guide vanes without increasing the intake resistance.
- the guide vane moving mechanism is provided so as to surround an outer side of the housing and is rotatable along the outer periphery of the housing.
- the drive ring and the guide A lever member that connects the outer end of the blade main shaft and an actuator that rotates the drive ring are provided.
- the guide vane moving mechanism is mainly constituted by the ring-shaped drive ring that can rotate along the outer periphery of the housing, it is mounted along the periphery of the housing.
- the guide wing variable mechanism can be configured in a compact manner without greatly projecting and increasing in size. Furthermore, a plurality of guide vanes can be interlocked to rotate with high accuracy at the same inclination angle.
- a return spring is provided between the guide blade main shaft and the housing, and an urging force that always returns the inclination angle of the guide blade with respect to the rotation axis direction to zero acts. It is characterized by.
- the biasing force is acting so that the inclination angle of the guide blade is returned to the zero state by the return spring, it is possible to prevent the guide blade from being stuck during rotation and difficult to rotate.
- the guide vane is formed by a plate-like member, the center side of the intake passage has a tapered trapezoidal shape, and is arranged so that the surface of the plate-like member is along the flow direction of the intake passage,
- the height of the guide vane is characterized by being formed to be substantially the same as the height of the leading edge of the impeller wheel blade.
- the guide vanes are arranged so that the plate-like member has a tapered trapezoidal shape and the plate surface is aligned with the intake gas flow, so that the intake passage does not give a large loss to the intake flow. Can be placed inside. Because it is tapered, it can be supported while maintaining strength by cantilevering on the outer peripheral side of the guide vane. Further, since the height of the guide vanes is set to be substantially the same as the height of the leading edge of the impeller wheel blades, the swirl flow generated by the guide blades can be efficiently guided to the impeller wheel blades.
- the housing is provided with a recirculation flow path that communicates the outer peripheral portion of the impeller wheel blades with the intake passage upstream of the impeller wheel. It is characterized by.
- a surge margin is obtained by turning the intake air flow introduced into the impeller wheel by the guide vanes.
- a part of the intake gas sucked into the impeller is further obtained. Is circulated through a recirculation flow path that connects the outer peripheral portion of the impeller wheel blades and the intake passage upstream of the impeller wheel, whereby the surge flow rate can be reduced, so that the surge margin can be further improved.
- an opening end portion on the upstream side of the recirculation flow path is located upstream of the guide vanes. In this way, since the opening end on the upstream side of the recirculation flow path is located upstream of the guide vanes, more swirl is imparted when the circulated intake gas passes through the guide vanes, Furthermore, the surge margin is improved.
- the housing is divided into two parts, an upstream side and a downstream side, at a position where the recirculation flow path is divided.
- the circulation hole of the recirculation flow path is processed from the dividing surface of the housing. Therefore, it becomes easy to form a recirculation flow path.
- a surge flow (minimum flow rate) is reduced by applying a swirling flow to the intake gas flowing in from the intake port, the surge margin is improved, and the intake gas flow resistance in the central intake flow passage is small. Therefore, a decrease in the choke flow rate (maximum flow rate) can be suppressed, and the operating range can be expanded.
- the blade inclination angle of the guide blade can be changed according to the flow rate passing through the compressor. For example, during small flow rate operation, the blade tilt angle is increased to reduce the compressor surging flow rate due to the swirl flow, and during large flow operation, the blade tilt angle is decreased to reduce the choke flow rate. Can be suppressed.
- the inner diameter of the intake passage has a small diameter equivalent to the diameter of the front edge portion of the impeller wheel blades and a large diameter formed on the inflow side larger than that. Characterize. Further, the large-diameter portion of the intake passage may be set so as to expand a flow passage area corresponding to a flow passage area that decreases when at least the plurality of guide vanes block the flow passage.
- the flow passage area reduced by the guide vanes can be expanded, the influence of the flow resistance by the guide vanes can be eliminated, and the efficiency improvement and the reduction of the choke flow rate (maximum flow rate) can be suppressed.
- FIG. 2 is a cross-sectional view of a main part taken along line BB in FIG.
- FIG. 5 is a cross-sectional view of a main part corresponding to FIG. 1, showing a second embodiment.
- FIG. 5 is a cross-sectional view of a main part corresponding to FIG. 1 according to a third embodiment. It is a characteristic view which shows the change tendency of a surging line based on the inclination angle of a guide blade. It is sectional explanatory drawing which shows the centrifugal compressor of a prior art. It is a comparison figure of the general performance characteristic of a centrifugal compressor.
- FIG. 1 is a cross-sectional view of a main part in the direction of the rotation axis of an exhaust turbocharger 1 of an internal combustion engine.
- the exhaust turbocharger 1 includes a turbine housing 5 that houses a turbine rotor 3 that is driven by exhaust gas from an internal combustion engine, a rotary shaft 9 that transmits the rotational force of the turbine rotor 3 to an impeller wheel 7, and a bearing 11.
- a bearing housing 13 that is rotatably supported through a compressor housing 15 and a compressor housing 15 that houses an impeller wheel 7 that sucks and compresses air as intake gas.
- a scroll passage 17 formed in a spiral shape is formed on the outer periphery of the turbine housing 5, and exhaust gas from the internal combustion engine flows from the outer peripheral side to the shaft center side, and then is discharged in the axial direction. Thus, the turbine rotor 3 is rotated.
- the impeller wheel 7 is supported in the compressor housing 15 so as to be rotatable about the rotation axis M of the rotary shaft 9 and the intake gas before being compressed, for example, air
- the intake passage 21 that guides the air to the impeller wheel 7 extends in the direction of the rotational axis M and in a cylindrical shape coaxially.
- An intake port 23 connected to the intake passage 21 opens at an end of the intake passage 21.
- the air inlet 23 is tapered in diameter toward the end so that air can be easily introduced.
- a diffuser 25 extending in a direction perpendicular to the rotation axis M is formed outside the impeller wheel 7, and a spiral air passage 27 is provided on the outer periphery of the diffuser 25.
- the spiral air passage 27 forms an outer peripheral portion of the compressor housing 15.
- the impeller wheel 7 is provided with a plurality of blades 31 that are rotationally driven together with a hub portion 29 that is rotationally driven about the rotation axis M.
- the hub portion 29 is attached to the rotary shaft 9 and a plurality of blades 31 are provided on a radially outer surface thereof.
- the blade 31 compresses the air that has passed through the intake air passage 21 from the intake port 23 by being rotationally driven, and the shape is not particularly limited.
- the blade 31 is provided with a front edge 31a which is an upstream edge, a rear edge 31b which is a downstream edge, and an outer peripheral edge (outer peripheral part) 31c which is a radially outer edge.
- the outer peripheral edge 31 c is a side edge portion covered by the shroud portion 33 of the compressor housing 15. And the outer periphery 31c is arrange
- the impeller wheel 7 of the compressor 19 is rotationally driven around the rotational axis M by the rotational driving force of the turbine rotor 3. Then, outside air is drawn from the air inlet 23 and flows between the plurality of blades 31 of the impeller wheel 7, and mainly after the dynamic pressure is increased, it flows into the diffuser 25 arranged on the radially outer side. A part of the dynamic pressure is converted into a static pressure, the pressure is increased, and the pressure is discharged through the spiral air passage 27. And it is supplied as intake air of an internal combustion engine.
- the recirculation flow path 41 has an annular downstream opening end 43 that opens on the inner peripheral wall of the compressor housing 15 facing the outer peripheral edge 31 c of the blade 31, and the compressor housing 15 upstream of the front edge 31 a of the blade 31. It is provided so as to communicate with the upstream side opening end portion 45 that opens in the inner peripheral wall. Then, the air immediately after flowing in between the plurality of blades 31 or a part of the air being pressurized is recirculated through the recirculation passage 41 and into the intake passage 21 on the upstream side of the blades 31. It has become.
- the recirculation flow path 41 is configured by a plurality of circulation holes 51 arranged on the circumference around the rotation axis M outside the cylindrical intake passage 21.
- the compressor housing 15 is divided into two parts, an upstream housing 15a and a downstream housing 15b, at a position where the recirculation channel 41 is divided in the middle, and a spiral air passage further downstream of the downstream housing 15b.
- the shroud side housing 15 c having 27 is divided into three parts.
- the mating surfaces of the upstream housing 15a and the downstream housing 15b form a step-shaped mating surface, and are aligned in the direction of the rotational axis M and in the radial direction perpendicular thereto by fitting with a spigot.
- the upstream housing 15a and the downstream housing 15b are coupled by a bolt 47. Further, the downstream housing 15b and the shroud housing 15c are aligned by a pin 49 and welded.
- FIG. 5 is a cross-sectional view of a main part taken along line BB in the downstream housing 15b.
- a plurality of, for example, 13 substantially oval circulation holes 51 are positioned with the longitudinal direction of the oval in the circumferential direction. Are arranged at regular intervals.
- An annular curved concave groove 53 that forms the upstream opening end 45 is formed on the dividing surface between the upstream housing 15a and the downstream housing 15b. Due to the curved shape of the concave groove, the discharge direction of the reflux air is directed toward the impeller wheel 7.
- the circulation hole 51 of the recirculation channel 41 and the concave groove 53 of the upstream opening end 45 can be processed from the division surface of the upstream housing 15a and the division surface of the downstream housing 15b, respectively. Formation of the circulation channel 41 is facilitated.
- Providing the recirculation channel 41 operates as follows.
- the air passing through the recirculation flow path 41 flows downstream from the upstream opening end 45 toward the downstream opening end 43 through the air from the intake port 23. It flows into the outer peripheral edge 31 c of the blade 31 from the side opening end 43.
- the flow rate through the compressor 19 is reduced to a low flow rate that causes surging
- the air passing through the recirculation flow path 41 is reversed from the downstream opening end 43 to the upstream opening end 45.
- the air is reintroduced into the intake passage 21 and reintroduced into the impeller wheel 7.
- the flow rate that flows into the leading edge 31a of the blade 31 is apparently increased, and the surge flow rate at which surging occurs can be reduced.
- the surge flow rate can be reduced by providing the recirculation flow path 41
- the impeller wheel 7 generates noise having a predetermined frequency determined by the number of blades 31 and the rotational speed.
- the length of the path 41 in the direction of the rotation axis M, the cross-sectional shape of the circulation hole 51, and the number of the circulation holes 51 are set so that the frequency band by the circulation hole 51 does not resonate with the frequency emitted by the impeller wheel 7. Need to be done.
- the compressor housing 15 is configured by dividing the upstream housing 15a, the downstream housing 15b, and the shroud housing 15c into three parts, so that the direction of the rotation axis M of the recirculation passage 41 set as a noise countermeasure Therefore, it is possible to cope with the change in the length and the number of the circulation holes 51 only by changing the upstream housing 15a and the downstream housing 15b.
- the swirl flow generating means 61 is provided in the intake passage 21 of the downstream housing 15b, is disposed between the intake port 23 and the impeller wheel 7, and flows in from the intake port 23.
- a swirl flow around the rotation axis M is applied to the inner peripheral wall of the intake passage 21 of the downstream housing 15b, specifically, a plurality of guide vanes 63 arranged along the circumferential direction. Is done.
- the guide vane 63 has a guide vane main shaft 65, is attached to the tip of the guide vane main shaft 65, and is rotated about the guide vane main shaft 65. Further, the center line N of the guide blade main shaft 65 is arranged so as to spread radially from the center point P of the intake passage 21 as shown in FIG.
- the guide vane 63 is made of a thin plate member, and the shape in the direction of the rotation axis M is a substantially trapezoidal quadrangle whose tip is narrower than the base.
- the plate thickness is a uniform flat plate. Further, the plate thickness may be thicker at the base and thinner toward the tip, or may be a plate shape having a thin root and tip and a thick central portion.
- the height H of the guide vane 63 is formed to be substantially the same as the height WH of the front edge 31 a of the blade 31 of the impeller wheel 7. As a result, the swirling flow by the guide vanes 63 efficiently acts on the blades 31 of the impeller wheel 7.
- the guide vanes 63 are attached so that the inclination angle ⁇ with respect to the rotation axis M direction can be changed.
- the air flowing in the direction of the rotation axis M is swirled in the same direction as the rotation direction of the impeller wheel 7 to generate a swirling flow.
- the swirl flow swirls the intake air flow that flows into the blades 31, so that the surge flow rate can be further reduced by the recirculation channel 41 described above.
- the inclination angle ⁇ is greater than 0 degrees and less than or equal to 60 degrees when the rotation axis M direction is 0 (zero) degrees and the blade surface is 90 degrees with respect to the rotation axis M. 0 ° ⁇ ⁇ 60 °) is preferable. If it exceeds 60 degrees, flow loss increases and surge increases, but it greatly affects efficiency reduction due to pressure loss.
- the guide blade main shaft 65 penetrates the downstream housing 15b and protrudes outside the housing.
- the guide blade main shaft 65 is rotatably supported in the through hole via a support bush 68.
- a seal member 67 and a return spring 69 are interposed between the guide blade main shaft 65 and the guide blade main shaft 65.
- the return spring 69 is provided, the urging
- a central intake flow passage 71 is formed on the inner peripheral side of the plurality of guide vanes 63 to allow air flowing from the intake port 23 to flow to the impeller wheel 7 without passing through the guide vanes 63.
- the central intake flow passage 71 has a large effect of suppressing a reduction in choke flow (maximum flow) because the flow resistance of intake air is small.
- the inner peripheral end of the guide vane 63 is opened, but it may be supported by a cylindrical member.
- the support rigidity of the guide vane 63 is improved, and the stable support of the guide vane 63 and the control accuracy of the tilt angle are improved.
- the guide vane moving mechanism 73 is provided so as to surround the outer side of the downstream housing 15b, and has an annular drive ring 75 that can rotate along the outer periphery of the downstream housing 15b, and the drive ring 75 and the guide vane main shaft.
- a lever member 77 that connects the outer end portion of 65 and an actuator 79 that rotates the drive ring 75 are mainly provided.
- a groove having a concave cross section is formed in the circumferential direction on the outer peripheral surface of the downstream housing 15b, and an annular drive ring 75 is rotatably fitted in the groove via a roller bearing 81.
- the drive ring 75 is provided with a rotating portion 83 that fits into the groove through the roller bearing 81 and an arm portion 85 that is integrally formed with the rotating portion 83 and extends in the direction of the rotation axis M.
- a concave notch 87 is formed in the arm portion 85 so as to have a notch opening in the right direction in FIG. 1 and aligned in the circumferential direction.
- the lever member 77 connected to the outer end portion of the guide blade main shaft 65 is fixed to the guide blade main shaft 65 at one end portion of the lever member 77, and a roller 91 is rotatably attached to the other end portion by a bolt 89.
- the roller 91 is loosely fitted inside the concave notch 87 of the arm portion 85.
- the rotation range of the guide vanes 63 is restricted by the protrusions 93 provided on the drive ring 75 coming into contact with the stoppers 95 provided on the shroud housing 15 c of the compressor housing 15. Further, the restriction range of the stopper 95 can be adjusted by the adjusting screw 97.
- the guide vane 63 by setting the inclination angle ⁇ of the guide vane 63 by the stopper 95 within a range of, for example, 0 ° ⁇ ⁇ ⁇ 60 °, and energizing the return spring 69 to be always 0 °, the guide vane It is possible to avoid a state in which 63 is fixed in an inclined state. In addition, a reduction in the choke flow rate caused by the guide vanes can be suppressed by varying the tilt angle as necessary as compared with the case where the tilt angle of the guide vanes is fixed.
- FIG. 8 shows changes in the surging line when the inclination angle ⁇ of the guide vane 63 is changed to 0 °, 20 °, 40 °, and 60 °.
- the inclination angle ⁇ of the guide vane 63 is increased, the swirling flow It can be seen that the generation effect is large and the surge flow rate can be reduced. Therefore, by changing the blade inclination angle ⁇ of the guide vane 63 according to the operating state of the internal combustion engine, that is, according to the flow rate passing through the compressor 19, for example, small flow rate operation such as at low rotation or low load.
- the blade inclination angle ⁇ is increased so that the surging does not occur at the operating point, so that it is controlled to the small flow rate side, and the operating point is on the large flow rate side during high rotation or high load operation. In this case, it is possible to control the large flow rate side by reducing the blade inclination angle ⁇ and considering the choke flow rate margin rather than the occurrence of surging.
- the operating range of the compressor 19 can be expanded. That is, the operating range can be expanded as compared with a compressor provided with only a recirculation passage, or a guide blade provided with a cone member at the center of the intake passage as described in Patent Document 1.
- the inclination angle of the guide vanes 63 can be varied, the optimum suitable for improving the surge flow rate (minimum flow rate) and the choke flow rate (maximum flow rate) according to the operating state of the internal combustion engine. Angle setting is possible.
- a guide blade movable mechanism 73 that varies the inclination angle of the guide blade 63 is provided so as to surround the outer side of the downstream housing 15b, and can be rotated along the outer periphery of the downstream housing 15b.
- the guide vanes 63 can be accurately linked to the same inclination angle.
- the compressor housing 100 is configured by three divisions of an upstream housing 100 a, a downstream housing 100 b, and a shroud housing 15 c including a spiral air passage 27.
- the recirculation flow path 41 is not provided in the upstream housing 100a and the downstream housing 100b.
- the fitting surfaces of the respective members have an inlay structure and are positioned by being positioned in the direction of the rotation axis M and the radial direction.
- guide wing 63 and the guide wing movable mechanism 73 are the same as those in the first embodiment.
- the upstream housing 100a and the downstream housing 100b are not formed with the recirculation channel 41 as in the first embodiment.
- the side housing structure is simplified. As a result, the processing of the upstream housing 100a and the downstream housing 100b is facilitated and the assembly work is facilitated.
- the guide blades have appropriate sizes according to the size of the blades 31 of the impeller wheel 7. Can be easily changed.
- the guide vane 63 and the guide vane movable mechanism 73 that varies the inclination angle of the guide vane 63 are provided in the downstream housing 100b and attached to the upstream housing 100a by the bolts 47. It is not necessary to change the entire compressor housing, and it is only necessary to change the mounting on the downstream housing 100b, so that the change in the downstream housing 100b can cope with this change.
- the effect of the swirl flow generating means 61 is the same as that of the first embodiment, and it is possible to improve the surge margin by reducing the surge flow rate (minimum flow rate) and suppress the reduction of the choke flow rate (maximum flow rate). Expansion of the operating range of the compressor can be achieved with a simple structure. Further, the guide blade 63 can be adjusted to an optimum angle according to the operation state by changing the inclination angle of the guide blade 63.
- the shape of the inner peripheral wall of the intake passage 21 of the first embodiment is not a cylindrical shape, but has a shape in which the inner diameter changes in the direction of the rotation axis M.
- Other configurations are the same as those of the first embodiment.
- the inner peripheral wall of the upstream housing 115a has a large diameter J
- the inner peripheral wall of the downstream housing 115b is formed to change from the large diameter J to the small diameter K.
- the small diameter K is substantially the same as the diameter of the front edge 31a portion of the blade 31 of the impeller wheel 7.
- the expansion change from the small diameter K to the large diameter J is set so as to expand an area corresponding to a flow path area which is reduced by at least the plurality of guide vanes 63 blocking the flow path. That is, the large-diameter J portion prevents the flow passage area in the intake passage 121 from being reduced by the installation of the guide vanes 63.
- the flow path area may be further reduced in consideration of the lower end portion of the support bush 68 that supports the guide vanes 63.
- a surge flow (minimum flow rate) is reduced by applying a swirling flow to the intake gas flowing in from the intake port, the surge margin is improved, and the intake gas flow resistance in the central intake flow passage is small. Therefore, the reduction of the choke flow rate (maximum flow rate) can be suppressed, the operating range can be expanded, and further, by changing the oblique angle of the guide vanes, according to the flow rate passing through the compressor, Since the blade inclination angle of the guide blade can be changed, it is useful as an application technique to an exhaust turbocharger of an internal combustion engine.
Abstract
Description
遠心圧縮機200のインペラーホイール201は、ハウジング202内に回転可能な複数の羽根204を含み、ハウジング202は、羽根204の半径方向外側縁204aに近接配置された内側壁を有する。
下流開口部213は、羽根204が近傍通過するハウジング表面205と環状流路211とを連通する。
これは、圧縮機の性能を安定化させ、圧縮機サージマージンとチョーク流とを共に向上させる(図10のRCC(再循環コンプレッサ)を参照)。
即ち、従来の旋回流を発生させる案内翼には、中央部に吸入空気を案内翼に導くコーン状の部材が設けられ、空気抵抗が増大し、チョーク流量が減少するという問題があった。
特に、吸気口案内翼214の翼角度が一定のため、吸気流に対して常に一定の空気抵抗が発生しているため、チョーク流量が減少するという問題があった。
前記ハウジングの内部に、前記回転軸を中心に回転可能に配置され、前記吸気口から流入する吸気ガスを圧縮するインペラーホイールと、
前記吸気口とインペラーホイールとの間の前記ハウジングの内周壁に沿って周方向に複数配置されるとともに、前記吸気口から流入する吸気ガスに回転軸周りに旋回流を付与する案内翼と、
前記複数の案内翼の内周側に形成されて前記吸気口から流入する吸気ガスを、前記案内翼を通過することなく前記インペラーホイールに流通させる中央吸気流通路と、
前記複数の案内翼の前記回転軸方向に対する傾斜角度を連動して変化させる案内翼可動機構と、をそなえたことを特徴とする。
このように、リターンスプリングで案内翼の傾斜角度をゼロの状態に戻すように付勢力が作用しているため、案内翼が回動途中で固着して回動困難となることを回避できる。
また、案内翼の高さをインペラーホイールの羽根の前縁の高さと略同一の高さにするため、案内翼で生成された旋回流を効率よく、インペラーホイールの羽根に導くことができる。
このように、再循環流路の上流側の開口端部が、案内翼よりも上流に位置するため、循環した吸気ガスが案内翼を通過することにより、より多くの旋回が付与されるので、さらにサージマージンが改善される。
このように、コンプレッサハウジングを、再循環流路を分断する位置で、上流側ハウジングと、下流側ハウジンとに2分割するため、このハウジングの分割面から再循環流路の循環孔を加工することができるので、再循環流路の形成が容易となる。
例えば、小流量運転時においては、翼傾斜角度を大きくして、旋回流によってコンプレッサのサージングの発生流量をより小流量にし、また、大流量運時には、翼傾斜角度を小さくしてチョーク流量の低減を抑えることができる。
さらに、前記吸気通路の大径の部分は、少なくとも前記複数の案内翼が流路を遮ることで減少する流路面積に相当する流路面積を拡大するように設定されているとよい。
図1は、内燃機関の排気ターボ過給機1の回転軸方向の要部断面図を示す。該排気ターボ過給機1は、内燃機関の排ガスによって駆動されるタービンロータ3を収納するタービンハウジング5と、該タービンロータ3の回転力をインペラーホイール7に伝達する回転軸9を、軸受11を介して回転自在に支持する軸受ハウジング13と、吸気ガスとして空気を吸引して圧縮するインペラーホイール7を収納するコンプレッサハウジング15とが結合されて構成される。
次に、コンプレッサハウジング15に形成される再循環流路41について説明する。
再循環流路41は、前記羽根31の外周縁31cに対向するコンプレッサハウジング15の内周壁に開口する環状の下流側開口端部43と、羽根31の前縁31aより上流側のコンプレサハウジング15の内周壁に開口する上流側開口端部45とを連通するように設けられている。
そして、複数の羽根31間に流入した直後の空気または、加圧途中の空気の一部を、再循環流路41を通って、羽根31の上流側の吸気通路21内に再循環させるようになっている。
また、コンプレッサハウジング15は、再循環流路41を途中で分断する位置で、上流側ハウジング15aと下流側ハウジング15bに2分割され、さらに、下流側ハウジング15bのさらに下流側に渦巻状の空気通路27を有するシュラウド側ハウジング15cの3分割によって構成される。
図5に、下流側ハウジング15bにおけるB-B線の要部断面図を示す。図5より、吸気通路21の外側に、同一円周上に本実施形態では、複数個、例えば13個の略長円状の循環孔51が、長円形状の長手方向を周方向に位置させて等間隔で配置されている。
コンプレッサ19を通る空気量が適正な流量状態では、再循環流路41を通る空気は、吸気口23からの空気が上流側開口端部45から下流側開口端部43に向かって流れて、下流側開口端部43から、羽根31の外周縁31cに流れ込む。
一方、コンプレッサ19を通る空気量が減少してサージングを生じるような低流量になると、再循環流路41を通る空気は、逆になり、下流側開口端部43から上流側開口端部45に向かって流れて、吸気通路21に再導入されて、インペラーホイール7に再導入される。これによって、見かけ上、羽根31の前縁31aに流入する流量が多くなり、サージングが発生するサージ流量を小流量化できる。
次に、旋回流生成手段61について説明する。
図1~3に示すように、旋回流生成手段61は、下流側ハウジング15bの吸気通路21内部に設けられ、吸気口23とインペラーホイール7との間に配置され、吸気口23から流入する空気に、回転軸線M周りの旋回流を付与するものであり、具体的には、下流側ハウジング15bの吸気通路21の内周壁に、周方向に沿って配置される複数枚の案内翼63によって構成される。
次に、案内翼可動機構73について説明する。
案内翼可動機構73は、下流側ハウジング15bの外側を囲うように設けられて、下流側ハウジング15bの外周に沿って回動可能な環形状のドライブリング75と、該ドライブリング75と案内翼主軸65の外端部とを連結するレバー部材77と、ドライブリング75を回動するアクチュエータ79とを主に備えている。
ドライブリング75には、ころ軸受81を介して凹溝に嵌合する回動部83と、該回動部83と一体に形成されて回転軸線M方向に延びるアーム部85とが設けられている。アーム部85には凹形状の切欠き87が、切り欠きの開口を図1中右方向に有し、且つ周方向に並んで形成されている。
従って、内燃機関の運転状態に応じて、すなわち、コンプレッサ19を通過する流量に応じて案内翼63の翼傾斜角度θを変更することで、例えば、低回転若しくは低負荷時のような小流量運転時においては、翼傾斜角度θを大きくして、作動点でサージングが起らないようにより小流量側に制御し、また、高回転若しくは高負荷運転時のような大流量側に作動点がある場合は、翼傾斜角度θを小さくして、サージングの発生よりもチョーク流量のマージンを考え、大流量側の制御を行なうことができる。
さらに、案内翼63の内周側に形成される中央吸気流通路71によって、吸入空気に対する流通抵抗を小さくできるので、チョーク流量(最大流量)の減少を抑制することができる。このように、コンプレッサ19の作動レンジを拡大できる。
すなわち、再循環通路だけを設けたコンプレッサや、特許文献1で説明したような、案内翼を設けても吸気通路の中央部にコーン部材を設けたものに比べて、作動レンジを拡大できる。
次に、図6を参照して第2実施形態について説明する。
第2実施形態は、第1実施形態の再循環流路41が設けられていないものであり、その他の構成は、第1実施形態と同じである。
また、それぞれの部材の嵌合面は、インロー構造になっていて回転軸線M方向および径方向の位置決めがされて位置決めされる。
その結果、上流側ハウジング100aおよび下流側ハウジング100bの加工が容易になるとともに組み付け作業も容易になる。
次に、図7を参照して第3実施形態について説明する。
第3実施形態は、前記第1実施形態の吸気流路21の内周壁の形状が円筒形状ではなく回転軸線M方向に内径が変化する形状を有している。その他の構成は、第1実施形態と同じである。
この小径Kから大径Jへの拡大変化は、少なくとも複数の案内翼63が流路を遮ることで減少する流路面積に相当する面積を拡大するように設定されている。
すなわち、大径Jの部分によって、吸気通路121内の流路面積が案内翼63の設置によって、減少しないようになっている。案内翼63だけではなく、案内翼63を支持する支持ブッシュ68の下端部による流路面積の減少を考慮してさらに拡大するようにしてもよい。
7 インペラーホイール
9 回転軸
15、100 コンプレッサハウジング(ハウジング)
15a、100a、115a 上流側ハウジング
15b、100b、115b 下流側ハウジング
15c シュラウド側ハウジング
19 遠心圧縮機
21、121 吸気通路
23 吸気口
25 ディフューザ
27 渦巻状の空気通路
29 ハブ
31 羽根
31a 羽根の前縁
31b 羽根の後縁
31c 羽根の外周縁(外周部)
41 再循環流路
43 下流側開口端部
45 上流側開口端部
51 循環孔
61 旋回流生成手段
63 案内翼
65 案内翼主軸
69 リターンスプリング
71 中央吸気流通路
73 案内翼可動機構
75 ドライブリング
77 レバー部材
79 アクチュエータ
69 リターンスプリング
91 ローラ
M 回転軸線
θ 案内翼の傾斜角度
Claims (10)
- 遠心圧縮機の回転軸方向に開口する吸気口と該吸気口につながる吸気通路とを有するハウジングと、
前記ハウジングの内部に、前記回転軸を中心に回転可能に配置され、前記吸気口から流入する吸気ガスを圧縮するインペラーホイールと、
前記吸気口とインペラーホイールとの間の前記ハウジングの内周壁に沿って周方向に複数配置されるとともに、前記吸気口から流入する吸気ガスに回転軸周りに旋回流を付与する案内翼と、
前記複数の案内翼の内周側に形成されて前記吸気口から流入する吸気ガスを、前記案内翼を通過することなく前記インペラーホイールに流通させる中央吸気流通路と、
前記複数の案内翼の前記回転軸方向に対する傾斜角度を連動して変化させる案内翼可動機構と、をそなえたことを特徴とする遠心圧縮機。 - 前記案内翼は案内翼主軸を有し、前記案内翼は前記案内翼主軸を中心に回動されるとともに、該案内翼主軸は吸気通路の中心に向かって延びて配置され、該案内翼主軸の外端部は吸気通路の周壁を貫通して前記ハウシングの外側に位置し、前記案内翼可動機構に連結されることを特徴とする請求項1記載の遠心圧縮機。
- 前記案内翼可動機構は、前記ハウジングの外側を囲うように設けられて前記ハウジンの外周に沿って回動可能な環形状のドライブリングと、該ドライブリングと前記案内翼主軸の外端部とを連結するレバー部材と、前記ドライブリングを回動するアクチュエータとを備えていることを特徴とする請求項2記載の遠心圧縮機。
- 前記案内翼主軸と前記ハウジングとの間にはリターンスプリングが設けられ、前記案内翼の前記回転軸方向に対する傾斜角度を常にゼロに戻す付勢力が作用していることを特徴とする請求項2または3記載の遠心圧縮機。
- 前記案内翼は板状部材によって形成され、吸気通路の中心側が先細の台形形状をなし、吸気通路の流通方向に板状部材の面が沿うように配置され、該案内翼の高さは前記インペラーホイールの羽根の前縁の高さと略同一の高さに形成されていることを特徴とする請求項2記載の遠心圧縮機。
- 前記ハウジングには、
前記インペラーホイールの羽根の外周部と該インペラーホイールより上流側の前記吸気通路とを連通させる再循環流路が、前記吸気通路の外側に設けられていることを特徴とする請求項1記載の遠心圧縮機。 - 前記再循環流路の上流側の開口端部が、前記案内翼よりも上流に位置することを特徴とする請求項6記載の遠心圧縮機。
- 前記ハウジングは、前記再循環流路を分断する位置で、上流側と下流側に2分割されることを特徴とする請求項6または7記載の遠心圧縮機。
- 前記吸気通路の内径は、前記インペラーホイールの羽根の前縁部分の径とそれより大きい流入側の大径とを有して形成されることを特徴とする請求項1または2記載の遠心圧縮機。
- 前記吸気通路の大径の部分は、少なくとも前記複数の案内翼が流路を遮ることで減少する流路面積に相当する流路面積を拡大するように設定されていることを特徴とする請求項9記載の遠心圧縮機。
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Also Published As
Publication number | Publication date |
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CN107816440A (zh) | 2018-03-20 |
CN107816440B (zh) | 2020-03-06 |
JP5599528B2 (ja) | 2014-10-01 |
EP2863032A1 (en) | 2015-04-22 |
EP2863032A4 (en) | 2015-05-06 |
CN104428509A (zh) | 2015-03-18 |
EP2863032B1 (en) | 2017-11-01 |
US20150192133A1 (en) | 2015-07-09 |
JPWO2014033878A1 (ja) | 2016-08-08 |
CN104428509B (zh) | 2018-05-08 |
US9732756B2 (en) | 2017-08-15 |
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