WO2020059631A1 - Compresseur et compresseur d'alimentation - Google Patents

Compresseur et compresseur d'alimentation Download PDF

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Publication number
WO2020059631A1
WO2020059631A1 PCT/JP2019/035892 JP2019035892W WO2020059631A1 WO 2020059631 A1 WO2020059631 A1 WO 2020059631A1 JP 2019035892 W JP2019035892 W JP 2019035892W WO 2020059631 A1 WO2020059631 A1 WO 2020059631A1
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WO
WIPO (PCT)
Prior art keywords
flow path
discharge
valve
compressor
cross
Prior art date
Application number
PCT/JP2019/035892
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English (en)
Japanese (ja)
Inventor
啓太郎 宮澤
Original Assignee
株式会社Ihi
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
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Application filed by 株式会社Ihi filed Critical 株式会社Ihi
Publication of WO2020059631A1 publication Critical patent/WO2020059631A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • 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
    • 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
    • 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
    • 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 disclosure relates to a compressor and a supercharger.
  • This application claims the benefit of priority based on Japanese Patent Application No. 2018-174848 filed on September 19, 2018, the contents of which are incorporated herein by reference.
  • the turbocharger is provided with a compressor.
  • an air bypass valve is provided to suppress stall at a small flow rate.
  • the air bypass valve opens and closes a return passage formed in the compressor housing.
  • Patent Document 1 discloses a compressor housing in which a return flow path is formed by assembling a plurality of divided pieces.
  • An object of the present disclosure is to provide a compressor and a supercharger capable of suppressing stall at a small flow rate with a simple configuration.
  • a compressor includes a housing in which an impeller is housed, a scroll passage formed in the housing, and provided radially outside the impeller with respect to the impeller, and a scroll.
  • a discharge flow path extending from the flow path to a discharge port formed in the housing; and a discharge flow path provided in the discharge flow path, wherein when the flow path cross-sectional area of the discharge flow path is the minimum, the extension of the discharge flow path among the discharge flow paths
  • a valve having a throttle portion located on the impeller side in a flow path cross section orthogonal to the existing direction.
  • the end of the discharge port side is closer to the center of the flow path cross section orthogonal to the extending direction of the discharge flow path than the end of the scroll flow path. It may have a near inclined surface.
  • the end of the inclined surface on the scroll flow path side may be located outside the inner wall surface of the discharge flow path when the flow path cross-sectional area of the discharge flow path is minimum.
  • the valve may have a curved portion whose thickness increases from the end on the scroll flow path side toward the end on the discharge port side when the cross-sectional area of the discharge flow path is the maximum.
  • a supercharger includes the compressor.
  • FIG. 1 is a schematic sectional view of the supercharger.
  • FIG. 2 is a sectional view of the compressor housing and the valve.
  • FIG. 3 is a view of the valve as viewed from an arrow III in FIG. 2.
  • FIG. 4 is a diagram for explaining a state in which the cross-sectional area of the discharge channel is minimum.
  • FIG. 5 is a view on arrow V in FIG.
  • FIG. 6 is a cross-sectional view of a portion corresponding to FIG. 4 in the first modification.
  • FIG. 7 is a view taken in the direction of the arrow VII in FIG.
  • FIG. 8 is a sectional view of a portion corresponding to a section taken along line VIII-VIII of FIG. 6 in the second modification.
  • FIG. 9 is a view on arrow IX of FIG.
  • FIG. 10 is a cross-sectional view of a portion corresponding to FIG. 4 in the third modification.
  • FIG. 11 is a view of the valve as viewed from the discharge port side.
  • FIG. 12 is a cross-sectional view of a portion corresponding to FIG. 4 in the fourth modification.
  • FIG. 13 is a cross-sectional view of a portion corresponding to FIG. 4 in the fifth modification.
  • FIG. 14 is a diagram for explaining a state at the minimum opening degree in the fifth modification.
  • FIG. 15 is a diagram for explaining a state at the time of the maximum opening degree in the sixth modification.
  • FIG. 16 is a diagram for explaining a state at the minimum opening degree in the sixth modification.
  • FIG. 17 is a diagram for explaining a state at the maximum opening degree in the seventh modification.
  • FIG. 11 is a view of the valve as viewed from the discharge port side.
  • FIG. 12 is a cross-sectional view of a portion corresponding to FIG. 4 in the fourth modification.
  • FIG. 18 is a diagram for explaining a state at the minimum opening degree in the seventh modification.
  • FIG. 19 is a diagram for explaining a state at the time of the maximum opening degree in the eighth modification.
  • FIG. 20 is a diagram for explaining a state at the minimum opening degree in the eighth modification.
  • FIG. 1 is a schematic sectional view of the supercharger TC. 1 will be described as the left side of the supercharger TC. The direction of arrow R shown in FIG. 1 will be described as the right side of the supercharger TC.
  • the supercharger TC includes a supercharger main body 1.
  • the supercharger main body 1 includes a bearing housing 2.
  • a turbine housing 4 is connected to the left side of the bearing housing 2 by a fastening bolt 3.
  • a compressor housing 6 (housing) is connected to the right side of the bearing housing 2 by a fastening bolt 5.
  • a bearing hole 2a is formed in the bearing housing 2.
  • the bearing hole 2a penetrates the supercharger TC in the left-right direction.
  • a bearing 7 is provided in the bearing hole 2a.
  • FIG. 1 shows a full floating bearing as an example of the bearing 7. However, the bearing 7 may be another radial bearing such as a semi-floating bearing or a rolling bearing.
  • the shaft 8 is rotatably supported by the bearing 7.
  • a turbine impeller 9 is provided at the left end of the shaft 8.
  • a turbine impeller 9 is rotatably housed in the turbine housing 4.
  • a compressor impeller 10 is provided at the right end of the shaft 8.
  • a compressor impeller 10 is rotatably housed in a housing space S formed in the compressor housing 6.
  • An intake port 11 is formed in the compressor housing 6.
  • the intake port 11 opens to the right of the supercharger TC.
  • the intake port 11 is connected to an air cleaner (not shown).
  • the diffuser flow path 12 is formed in a state where the bearing housing 2 and the compressor housing 6 are connected by the fastening bolts 5, the diffuser flow path 12 is formed.
  • the diffuser channel 12 pressurizes air.
  • the diffuser flow path 12 is formed in an annular shape from the inside to the outside in the radial direction of the shaft 8.
  • the diffuser flow path 12 communicates with the intake port 11 via the compressor impeller 10 on the radially inner side.
  • a compressor scroll channel 13 (scroll channel) is formed inside the compressor housing 6.
  • the compressor scroll channel 13 is annular.
  • the compressor scroll passage 13 is located, for example, radially outside the shaft 8 (compressor impeller 10) from the diffuser passage 12 (compressor impeller 10).
  • the compressor scroll passage 13 communicates with an intake port of an engine (not shown).
  • the compressor scroll channel 13 also communicates with the diffuser channel 12.
  • the supercharger TC includes the compressor C.
  • the compressor C includes a compressor housing 6, a compressor impeller 10, and a compressor scroll passage 13.
  • An exhaust port 14 is formed in the turbine housing 4.
  • the exhaust port 14 opens on the left side of the supercharger TC.
  • the exhaust port 14 is connected to an exhaust gas purification device (not shown).
  • the turbine housing 4 is provided with a flow path 15 and a turbine scroll flow path 16.
  • the turbine scroll passage 16 is located radially outside the turbine impeller 9 relative to the turbine impeller 9.
  • the flow path 15 is located between the turbine impeller 9 and the turbine scroll flow path 16.
  • the turbine scroll passage 16 communicates with the gas inlet. Exhaust gas discharged from an exhaust manifold (not shown) of the engine is guided to the gas inlet.
  • the turbine scroll flow path 16 also communicates with the flow path 15 described above.
  • the exhaust gas guided from the gas inlet to the turbine scroll flow path 16 is guided to the exhaust port 14 via the flow path 15 and the space between the blades of the turbine impeller 9.
  • the exhaust gas guided to the exhaust port 14 rotates the turbine impeller 9 during the flow of the exhaust gas.
  • FIG. 2 is a cross-sectional view of the compressor housing 6 and the valve 20.
  • a discharge port 6 a is formed in the compressor housing 6.
  • the discharge port 6a opens outside the compressor housing 6.
  • a discharge passage 6b is formed in the compressor housing 6.
  • the discharge channel 6b extends in a substantially straight line from the compressor scroll channel 13 to the discharge port 6a.
  • the discharge channel 6b connects (communicates) the downstream portion 13a of the compressor scroll channel 13 with the discharge port 6a.
  • the downstream portion 13a and the upstream portion 13b of the compressor scroll flow path 13 are separated by a tongue 6c.
  • the tongue 6c is located between the downstream 13a and the upstream 13b.
  • the air flow path extends from the circumferential direction to the linear direction on the downstream side of the compressor scroll flow path 13.
  • the downstream portion 13a is a portion of the compressor scroll flow path 13 that extends in a straight line direction.
  • the boundary between the discharge passage 6b and the compressor scroll passage 13 is, for example, located at the tip of the tongue 6c.
  • the discharge port 6a is closer to the discharge port 6a than the tongue 6c.
  • the downstream side 13a of the compressor scroll flow path 13 is located on the side of the tongue 6c farther from the discharge port 6a than the tip.
  • the boundary between the discharge flow path 6b and the compressor scroll flow path 13 may be located on a side farther from the discharge port 6a than the tip of the tongue 6c.
  • Only one of the discharge passages 6b is provided as a passage communicating between the compressor scroll passage 13 and the discharge port 6a.
  • the flow path connecting the compressor scroll flow path 13 and the discharge port 6a is not provided other than the discharge flow path 6b. All the air flowing out of the compressor scroll flow path 13 flows out of one discharge port 6a through the discharge flow path 6b.
  • the air flowing out of the compressor scroll channel 13 merges after being separated.
  • a loss due to the speed difference occurs. Since the compressor housing 6 has one discharge passage 6b and one discharge port 6a, loss due to a speed difference at the time of merging is avoided.
  • FIG. 3 is a view of the valve 20 viewed from the arrow III in FIG.
  • the right side is the discharge port 6a side
  • the left side is the downstream portion 13a side of the compressor scroll flow path 13.
  • a valve 20 is provided in the discharge channel 6b.
  • the valve 20 has, for example, a shape obtained by halving an ellipse (hereinafter, referred to as a semi-elliptical shape). In this semi-elliptical shape, the length of the ellipse in the longitudinal direction is half. Further, the valve 20 has an approximately plate shape.
  • the one end surface 20a of the valve 20 is more toward the compressor impeller 10 than the other end surface 20b.
  • the other end surface 20b of the valve 20 is located on the back side.
  • valve 20 is rotated in a direction indicated by an arrow in FIG. 2 by an actuator (not shown). In FIG. 2, the flow path cross-sectional area of the discharge flow path 6b is maximum. The valve 20 rotates around the end 22 closer to the discharge port 6a (downstream) than the center 21 in the longitudinal direction.
  • FIG. 4 is a view for explaining a state in which the flow path cross-sectional area of the discharge flow path 6b is minimized.
  • a minimum opening when the flow passage cross-sectional area of the discharge flow passage 6 b is minimum (hereinafter, referred to as a minimum opening), the upstream end (compressor scroll flow passage 13 side) of the valve 20.
  • Reference numeral 23 contacts the inner wall surface of the discharge channel 6b. The end portion 23 of the valve 20 abuts on the inner wall surface of the discharge passage 6b on the compressor impeller 10 side.
  • the valve 20 when the flow rate is small, the valve 20 has the minimum opening, so that the flow velocity of the air is increased and the stall of the air can be suppressed. Therefore, the operation area on the small flow rate side can be expanded. Since the valve 20 may be provided in the discharge channel 6b, the structure can be simplified. For example, in order to reduce the flow path cross-sectional area on the compressor scroll flow path 13 side, a plurality of valves are required. However, since the valve 20 is disposed on the discharge port 6a side with respect to the tongue 6c, the air flow path is united in the compressor scroll flow path 13. Therefore, the cross-sectional area of the air passage can be reduced by one valve 20.
  • the valve 20 has the minimum opening, the end 22 on the discharge port 6a side is closer to the center O of the discharge flow path 6b than the end 23 on the compressor scroll flow path 13 side.
  • the valve 20 has the inclined surface 24 at the time of the minimum opening.
  • the other end surface 20b becomes the inclined surface 24.
  • the opening degree is the minimum, the end of the inclined surface 24 closer to the discharge port 6a than the end of the compressor scroll flow path 13 (here, the same as the end 23) (here, the same as the end 22). Is closer to the center O of the discharge channel 6b. With the inclined surface 24, pressure loss is suppressed.
  • the valve 20 has a curved portion 25.
  • the curved portion 25 has a thickness from the end portion 23 on the compressor scroll passage 13 side to the end portion 22 on the discharge port 6a side when the flow passage cross-sectional area of the discharge flow passage 6b is maximum (hereinafter, referred to as a maximum opening). Increase.
  • the curved portion 25 has, for example, a streamline shape. With the curved portion 25, pressure loss is suppressed.
  • the bending portion 25 is provided on one end surface 20a and the other end surface 20b.
  • FIG. 5 is a view on arrow V in FIG.
  • the valve 20 is indicated by cross hatching, and the rotation axis of the compressor impeller 10 is indicated by a two-dot chain line.
  • the valve 20 has a throttle section 26.
  • the throttle section 26 When the throttle section 26 is at the minimum opening, the throttle section 26 has a compressor impeller 10 side (refer to FIG. 5) in a cross section of the discharge flow path 6b that is orthogonal to the direction in which the discharge flow path 6b extends. At the bottom).
  • valve impeller 10 side (hereinafter, simply referred to as a flow path cross section) of the discharge flow path 6b at right angles to the extending direction of the discharge flow path 6b (hereinafter, simply referred to as flow path cross section).
  • the whole is located on the lower side in FIG. 5).
  • the throttle portion 26 is located closer to the compressor impeller 10 than the center O of the cross section of the discharge flow channel 6b.
  • the throttle portion 26 may extend from the center O of the discharge passage 6b to a side (upper side in FIG. 5) apart from the compressor impeller 10.
  • the throttle unit 26 is configured by the valve 20. In other words, the valve 20 forms the throttle unit 26.
  • the flow velocity of the air flowing through the compressor scroll flow path 13 is higher on the radially outer side of the compressor impeller 10 than on the radially inner side when the air has a small flow rate.
  • the flow velocity of the air flowing into the discharge passage 6b is faster on the side separated from the compressor impeller 10 than on the compressor impeller 10 side.
  • the valve 20 is located on the compressor impeller 10 side, so that the flow of air having a higher flow rate is less likely to be hindered.
  • the air flowing through the compressor scroll passage 13 forms a swirling flow (flow in the direction of the dashed arrow in FIG. 2).
  • the swirling flow does not contribute to the flow velocity of the flow in the direction in which the discharge flow path 6b extends, resulting in a pressure loss.
  • rectification is performed by the valve 20, and the swirling flow is suppressed. Therefore, pressure loss is suppressed.
  • the velocity in the linear direction is increased by the valve 20, so that the proportion of the velocity component of the swirling flow in the flow velocity is reduced.
  • the cross-sectional shape of the discharge channel 6b is approximately circular.
  • the valve 20 is inclined with respect to the extending direction of the discharge channel 6b. Since the shape of the valve 20 is a semi-elliptical shape, the valve 20 can contact along the inner wall surface of the discharge flow path 6b at the minimum opening.
  • FIG. 6 is a cross-sectional view of a portion corresponding to FIG. 4 in the first modification.
  • FIG. 6 shows a case where the valve 120 has the minimum opening degree.
  • the valve 120 is at the maximum opening degree, the same figure as FIG. 2 is obtained.
  • the inclination direction of the valve 120 is different from the above-described embodiment.
  • FIG. 7 is a view taken in the direction of the arrow VII in FIG.
  • the rotation axis of the compressor impeller 10 is indicated by a two-dot chain line.
  • the valve 120 when the valve 120 is at the minimum opening, the valve 120 is located on the side separated from the compressor impeller 10 in the flow path cross section of the discharge flow path 6 b.
  • the throttle portion 126 of the valve 120 is located on the side of the discharge flow path 6b farther from the compressor impeller 10 than the center O of the flow path cross section of the discharge flow path 6b.
  • the throttle portion 126 may extend from the center O of the discharge passage 6b to the compressor impeller 10 side.
  • FIG. 8 is a cross-sectional view of a portion corresponding to a cross section taken along line VIII-VIII of FIG. 6 in the second modification. However, in FIG. 8, only the vicinity of the discharge port 6a is shown in cross section.
  • FIG. 8 shows a direction rotated 90 degrees counterclockwise with respect to FIG.
  • FIG. 9 is a view on arrow IX of FIG. 8 and 9, the rotation axis of the compressor impeller 10 is indicated by a two-dot chain line.
  • the throttle section 226 in the rotation axis direction of the compressor impeller 10 vertical direction in FIG. It is located on one side (the upper side in FIG. 8, the intake port 11 side).
  • the swirling flow is suppressed by the valves 120 and 220 when the opening degree is the minimum. Therefore, pressure loss is suppressed. Also at the maximum opening degree, since the speed in the linear direction (the extending direction of the discharge flow path 6b) is increased by the valves 120 and 220, the ratio of the velocity component of the swirling flow to the flow velocity is reduced.
  • valves 120 and 220 also have the inclined surface 24 and the curved portion 25 in the first modification and the second modification. Therefore, pressure loss is suppressed.
  • the cross-sectional shape of the discharge channel 6b is approximately circular.
  • the valves 120 and 220 have the minimum opening, they are inclined with respect to the extending direction of the discharge flow path 6b. Since the shape of the valves 120 and 220 is a semi-elliptical shape, the valves 120 and 220 can contact along the inner wall surface of the discharge flow path 6b at the minimum opening.
  • the inclined surface 24 is formed.
  • the inclined surface 24 may not be formed. That is, when the valves 20, 120, and 220 have the minimum opening degree, the valves 20, 120, and 220 may be in a direction orthogonal to the extending direction of the discharge channel 6 b.
  • the shapes of the valves 20, 120, and 220 may be semicircular. With the semicircular shape, the valves 20, 120, and 220 can contact along the inner wall surface of the discharge flow path 6b at the minimum opening degree.
  • valves 20, 120, and 220 rotate around the end 22 closer to the discharge port 6a (downstream) than the center 21 in the longitudinal direction.
  • valves 20, 120, and 220 may be rotated around the end 23 closer to the compressor scroll flow path 13 (upstream side) than the center 21 in the longitudinal direction.
  • FIG. 10 is a cross-sectional view of a portion corresponding to FIG. 4 in the third modification.
  • FIG. 11 is a view of the valve 320 as viewed from the discharge port 6a side. As shown in FIG. 11, the valve 320 has a main body 321 having a substantially semicircular shape. A protruding part 322 is provided in a middle part of the circumference of the main body part 321. The protruding portion 322 protrudes from the main body 321 outward in the radial direction of the main body 321.
  • the thickness of the valve 320 decreases from the tip 322 a of the protrusion 322 toward the end 321 a of the main body 321 opposite to the protrusion 322.
  • a through hole 6d is formed in the compressor housing 6.
  • the through hole 6d penetrates the wall 6e forming the discharge flow path 6b in parallel with the flow path cross section of the discharge flow path 6b (in the radial direction of the discharge flow path 6b).
  • the width of the through-hole 6d in the extending direction of the discharge channel 6b becomes smaller toward the discharge channel 6b (inner side).
  • the valve 320 is inserted into the through hole 6d from outside.
  • the main body 321 is located in the discharge channel 6b.
  • the protrusion 322 is located inside the through hole 6 d and outside the compressor housing 6.
  • valve 320 is moved in the through direction of the through hole 6d (in the radial direction of the discharge flow path 6b) by an actuator (not shown) as indicated by a double arrow in FIG.
  • FIG. 10 shows a case where the valve 320 has the minimum opening degree.
  • the discharge flow path 6b has the maximum opening.
  • FIG. 12 is a cross-sectional view of a portion corresponding to FIG. 4 in the fourth modification.
  • the valve 420 of the fourth modification is different from the valve 320 of the third modification in that the plate thickness is substantially constant.
  • the width of the through hole 46d in the extending direction of the discharge flow path 6b is substantially constant.
  • the shape of the valve 420 as viewed from the discharge port 6a is the same as that of the valve 320.
  • Valve 420 operates similarly to valve 320.
  • FIG. 13 is a sectional view of a portion corresponding to FIG. 4 in the fifth modification.
  • the valve 520 of the fifth modified example is constituted by, for example, a ball valve.
  • a casing 500 is provided on the outer periphery of the wall 6e forming the discharge flow path 6b.
  • An actuator (not shown) is attached to the casing 500.
  • the valve 520 has a main body 521 having a substantially spherical shape. A part of the casing 500 and a part of the wall 6e of the compressor housing 6 are cut out to form a fitting hole 510 into which the valve 520 is fitted. The valve 520 is rotatably supported by the fitting hole 510. The rotation axis of the valve 520 is, for example, parallel to the rotation axis of the compressor impeller 10.
  • a communication hole 522 is formed in the main body 521.
  • the communication hole 522 penetrates the main body 521.
  • the communication hole 522 passes through the center of the main body 521.
  • the opening on the discharge port 6a side (downstream side) of the communication hole 522 is the same as the cross-sectional shape of the discharge flow path 6b.
  • the opening of the communication hole 522 on the compressor scroll flow path 13 side (upstream side) is larger than the flow path cross-sectional shape of the discharge flow path 6b.
  • the communication hole 522 narrows from upstream to downstream.
  • the inner wall surface 522a (inclined surface) of the communication hole 522 on the lower side (compressor impeller 10 side) in FIG. 13 is continuous with the inner wall surface of the discharge passage 6b.
  • the upstream side of the inner wall surface 522b on the upper side (discharge channel 6b side) in FIG. 13 is separated outward from the inner wall surface of the discharge channel 6b.
  • the downstream side of the upper inner wall surface 522b in FIG. 13 is continuous with the inner wall surface of the discharge channel 6b.
  • FIG. 14 is a diagram for explaining a state at the time of the minimum opening in the fifth modification.
  • the valve 520 is rotated by an actuator (not shown) in the direction of the arrow (counterclockwise) in FIG.
  • the opening degree is the minimum
  • the upper inner wall surface 522b of the communication hole 522 in FIG. 14 is located outside the inner wall surface of the discharge flow path 6b.
  • the upstream side of the lower inner wall surface 522a (inclined surface) in FIG. 14 is separated outward from the inner wall surface of the discharge flow path 6b.
  • the throttle portion 526 is formed in the valve 520.
  • the throttle opening 526 is located on the compressor impeller 10 side (the lower side in FIG. 14) in the flow path cross section of the discharge flow path 6b (that is, the view as viewed from the discharge port 6a). Thereby, the flow path cross-sectional area of the discharge flow path 6b is reduced.
  • the throttle portion 526 is located on the compressor impeller 10 side, so that the flow of the air having the higher flow rate is not easily disturbed.
  • the throttle portion 526 is at the maximum opening degree, it is not located in the discharge channel 6b and does not hinder the flow.
  • FIG. 15 is a view for explaining a state at the time of the maximum opening degree in the sixth modification.
  • the inner wall surface 622b (inclined surface) on the upper side of the communication hole 622 in FIG. 15 is continuous with the inner wall surface of the discharge channel 6b.
  • the upstream side of the lower inner wall surface 622a in FIG. 15 is separated outward from the inner wall surface of the discharge flow path 6b.
  • the downstream side of the lower inner wall surface 622a in FIG. 15 is continuous with the inner wall surface of the discharge channel 6b.
  • the wall of the valve 620 does not enter the discharge flow path 6b, and the flow is not hindered by the valve 620.
  • FIG. 16 is a diagram for explaining a state at the minimum opening degree in the sixth modification.
  • the valve 620 is rotated by an actuator (not shown) in the direction of the arrow (clockwise) in FIG.
  • the lower inner wall surface 622a in FIG. 16 of the communication hole 622 is located outside the inner wall surface of the discharge flow path 6b.
  • the upstream side of the upper inner wall surface 622b in FIG. 16 is separated outward from the inner wall surface of the discharge flow path 6b.
  • the downstream side of the upper inner wall surface 622b in FIG. 16 projects inside the discharge flow path 6b.
  • the throttle 626 is formed in the valve 620.
  • the throttle portion 626 is located on the side (upper side in FIG. 14) separated from the compressor impeller 10 in the flow path cross section of the discharge flow path 6b (that is, the view from the discharge port 6a). Thereby, the flow path cross-sectional area of the discharge flow path 6b is reduced.
  • the throttle portion 626 suppresses the swirling flow when the opening degree is the minimum.
  • the throttle portion 626 has the maximum opening degree, it is not located in the discharge channel 6b and does not hinder the flow.
  • FIG. 17 is a view for explaining a state at the time of the maximum opening degree in the seventh modification.
  • the communication hole 722 of the valve 720 has a substantially constant cross-sectional shape from upstream to downstream.
  • the cross-sectional shape of the communication hole 722 is substantially equal to the cross-sectional shape of the discharge channel 6b.
  • FIG. 18 is a view for explaining a state at the time of the minimum opening in the seventh modification.
  • the valve 720 is rotated by an actuator (not shown) in the direction of an arrow (counterclockwise) in FIG.
  • the upstream side of the lower inner wall surface 722a (inclined surface) in FIG. 18 is located outside the discharge channel 6b, and the downstream side is inside the discharge channel 6b. Protrude.
  • the end on the compressor scroll flow path 13 side of the lower inner wall surface 722a (inclined surface) in FIG. 6b it is located outside the inner wall surface on the upstream side (compressor scroll passage 13 side) of the end of the inner wall surface 722a.
  • the downstream side of the upper inner wall surface 722b in FIG. 18 is located outside the discharge channel 6b, and the upstream side protrudes inside the discharge channel 6b.
  • the valve 720 may be rotated in the opposite direction (clockwise) to the arrow in FIG. 17 to reach the minimum opening.
  • the upstream side of the lower inner wall surface 722a in FIG. 18 protrudes inside the discharge channel 6b, and the downstream side is located outside the discharge channel 6b.
  • the downstream side of the upper inner wall surface 722b in FIG. 18 protrudes inside the discharge channel 6b, and the upstream side is located outside the discharge channel 6b.
  • FIG. 19 is a view for explaining a state at the time of the maximum opening in the eighth modification.
  • the channel width in the discharge channel 6b, the channel width (inner diameter, channel cross-sectional area) increases toward the discharge port 6a.
  • the flow path width in the communication hole 822 of the valve 820, the flow path width (inner diameter, flow path cross-sectional area) increases from upstream to downstream. At the maximum opening, the inner wall surface of the communication hole 822 is flush with the inner wall surface of the discharge channel 6b.
  • FIG. 20 is a diagram for explaining a state at the minimum opening degree in the eighth modification.
  • the valve 820 is rotated by an actuator (not shown) in the direction of an arrow (counterclockwise) in FIG.
  • the upstream side is located outside the discharge channel 6b, and the downstream side is inside the discharge channel 6b in FIG. Protrude.
  • the end of the lower inner wall surface 822a (inclined surface) on the compressor scroll flow channel 13 side in FIG. 6b it is located outside the inner wall surface on the upstream side (the compressor scroll flow path 13 side) of the end of the inner wall surface 822a.
  • the downstream side of the upper inner wall surface 822b in FIG. 20 is located outside the discharge passage 6b, and the upstream side protrudes inside the discharge passage 6b.
  • the valve 820 may be rotated in the opposite direction (clockwise) to the arrow in FIG.
  • the upstream side of the lower inner wall surface 822a in FIG. 20 protrudes inside the discharge channel 6b, and the downstream side is located outside the discharge channel 6b.
  • the downstream side of the upper inner wall surface 822b in FIG. 20 projects inside the discharge channel 6b, and the upstream side is located outside the discharge channel 6b.
  • valves 520, 620, 720, 820 of the fifth, sixth, seventh, and eighth modifications described above the inner wall surfaces 522a, 622b, 722a of the communication holes 522, 622, 722, 822, 822b functions as the inclined surface 24. With the inclined surface 24, pressure loss is suppressed.
  • the compressor C is incorporated in the supercharger TC.
  • the compressor C may be incorporated in a device other than the supercharger TC, or may be a single unit.
  • one end 23 of the valve 20 on the compressor scroll flow path 13 side contacts the inner wall surface of the discharge flow path 6b when the flow path cross-sectional area of the discharge flow path 6b is minimum.
  • the one end 23 of the inclined surface 24 on the compressor scroll passage 13 side is connected to the one end 23 of the discharge passage 6b when the passage cross-sectional area of the discharge passage 6b is minimum. It may be located outside the inner wall surface on the upstream side (compressor scroll passage 13 side).
  • the first modification, the fifth modification, the sixth modification, the seventh modification, and the eighth modification the case where the inclined surface 24 is provided has been described.
  • the inclined surface 24 is not an essential component.
  • the present disclosure can be used for compressors and superchargers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)

Abstract

Cette invention concerne un compresseur, comprenant : un carter dans lequel est logée un rouet ; un passage d'écoulement à spirale qui est formé à l'intérieur du carter, et qui est disposé davantage vers le côté radialement externe du rouet que le rouet ; un passage d'écoulement de refoulement (6b) s'étendant à partir du passage d'écoulement à spirale vers un orifice de refoulement (6a) formé dans le carter ; et un clapet (20) disposé dans le passage d'écoulement de refoulement (6b) et ayant une partie d'étranglement (26), laquelle, lorsque l'aire de section de passage d'écoulement du passage d'écoulement de refoulement (6b) est la plus petite, est positionnée sur le côté rouet du passage d'écoulement de refoulement (6b) dans une section transversale de passage d'écoulement orthogonale à la direction dans laquelle s'étend le passage d'écoulement de refoulement (6b).
PCT/JP2019/035892 2018-09-19 2019-09-12 Compresseur et compresseur d'alimentation WO2020059631A1 (fr)

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JP2018174848 2018-09-19
JP2018-174848 2018-09-19

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WO2020059631A1 true WO2020059631A1 (fr) 2020-03-26

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3176704A (en) * 1961-11-20 1965-04-06 Universal Oil Prod Co Carburetor throttle valve
JPS6128799A (ja) * 1984-07-19 1986-02-08 Nissan Motor Co Ltd 遠心圧縮機
JP2005155496A (ja) * 2003-11-26 2005-06-16 Aisin Seiki Co Ltd コンプレッサ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3176704A (en) * 1961-11-20 1965-04-06 Universal Oil Prod Co Carburetor throttle valve
JPS6128799A (ja) * 1984-07-19 1986-02-08 Nissan Motor Co Ltd 遠心圧縮機
JP2005155496A (ja) * 2003-11-26 2005-06-16 Aisin Seiki Co Ltd コンプレッサ

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