US20200378389A1 - Electric supercharger - Google Patents

Electric supercharger Download PDF

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Publication number
US20200378389A1
US20200378389A1 US16/326,640 US201716326640A US2020378389A1 US 20200378389 A1 US20200378389 A1 US 20200378389A1 US 201716326640 A US201716326640 A US 201716326640A US 2020378389 A1 US2020378389 A1 US 2020378389A1
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US
United States
Prior art keywords
compressor impeller
electric supercharger
side casing
rotational shaft
surface side
Prior art date
Legal status (The legal status 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 status listed.)
Abandoned
Application number
US16/326,640
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English (en)
Inventor
Naomichi SHIBATA
Byeongil An
Akihiro Sugiyama
Yutaka Fujita
Tadashi Kanzaka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Mitsubishi Heavy Industries Engine and Turbocharger Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Mitsubishi Heavy Industries Engine and Turbocharger Ltd
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
Publication date
Application filed by Mitsubishi Heavy Industries Ltd, Mitsubishi Heavy Industries Engine and Turbocharger Ltd filed Critical Mitsubishi Heavy Industries Ltd
Assigned to MITSUBISHI HEAVY INDUSTRIES, LTD., Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. reassignment MITSUBISHI HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AN, BYEONGIL, FUJITA, YUTAKA, KANZAKA, Tadashi, SHIBATA, Naomichi, SUGIYAMA, AKIHIRO
Assigned to Mitsubishi Heavy Industries Engine & Turbocharger, Ltd., MITSUBISHI HEAVY INDUSTRIES, LTD. reassignment Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. CHANGE OF ADDRESS Assignors: AN, BYEONGIL, FUJITA, YUTAKA, KANZAKA, Tadashi, SHIBATA, Naomichi, SUGIYAMA, AKIHIRO
Publication of US20200378389A1 publication Critical patent/US20200378389A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
    • F02B39/10—Non-mechanical drives, e.g. fluid drives having variable gear ratio electric
    • 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
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • 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
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
    • 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
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/122—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors

Definitions

  • the present disclosure relates to an electric supercharger.
  • an exhaust turbine is driven by exhaust gas discharged from the engine to coaxially drive a compressor disposed in an intake passage and compress intake gas supplied to engine, which is called “supercharging”.
  • turbo lag A known technique to make up for the response delay due to turbo lag is a two-stage supercharging system which includes a turbocharger driven by exhaust gas and an electric supercharger driven by an electric motor (see Patent Document 1).
  • the compressor is driven by a motor, unlike a turbocharger.
  • devices such as a motor and an inverter substrate are disposed behind the compressor (between the compressor impeller and the bearing).
  • the leakage flow may affect devices such as the motor and the inverter substrate.
  • An object of at least one embodiment of the present invention is to provide an electric supercharger capable of suppressing entry of a leakage flow to the bearing side via the gap between the back surface of the compressor impeller and the casing.
  • an electric supercharger includes: a compressor impeller; a motor configured to transmit a driving force to the compressor impeller via a rotational shaft; a back-surface side casing facing a back surface of the compressor impeller via a gap and surrounding the rotational shaft; a bearing disposed between the back-surface side casing and the rotational shaft so as to support the rotational shaft rotatably; and a mechanical seal positioned between the back surface of the compressor impeller and the bearing in an axial direction of the compressor impeller and configured to seal a gap between the rotational shaft and the back-surface side casing.
  • back-surface gap the gap between the back surface and the back-surface side casing
  • the mechanical seal includes: a stationary ring supported on the back-surface side casing; a rotary ring protruding from the rotational shaft toward an outer side in a radial direction of the compressor impeller and facing the stationary ring so as to be capable of being in contact with the stationary ring in the axial direction of the compressor impeller, the rotary ring being configured to rotate with the rotational shaft; and a biasing member configured to bias one of the rotary ring or the stationary ring toward the other one of the rotary ring or the stationary ring.
  • a groove is formed on a facing surface which is one of a surface of the rotary ring which faces the stationary ring or a surface of the stationary ring which faces the rotary ring.
  • the mechanical seal functions as a contact seal. Accordingly, it is possible to suppress entry of a leakage flow from the back-surface gap to the bearing, and suppress inflow of the leakage flow into electric devices such as the motor. Thus, it is possible to suppress occurrence of malfunction or the like of the electric devices, and operate the electric supercharger stably.
  • the pressure of gas inside the groove having a pressure increased by a centrifugal force separates the stationary ring and the rotary ring against the biasing force of the biasing member. Accordingly, the stationary ring and the rotary ring separate from each other (not in contact). Nevertheless, with the pressure of the space on the inner side of the facing surface being higher than the pressure of the space on the outer side of the facing surface, it is possible to suppress entry of a leakage flow from the back-surface gap to the bearing. Accordingly, it is possible to suppress inflow of the leakage flow to electric devices such as the motor. Thus, it is possible to suppress occurrence of malfunction or the like of the electric devices, and operate the electric supercharger stably.
  • the back surface of the compressor impeller has a plurality of ribs disposed on the back surface at intervals in a circumferential direction of the compressor impeller.
  • each of the ribs is disposed to so as to extend along a direction which intersects with the circumferential direction of the compressor impeller.
  • the plurality of ribs extending in a direction orthogonal to the circumferential direction rotates with the compressor impeller, and thus it is possible to apply the centrifugal force toward the outer side in the radial direction effectively to air in the back-surface gap, and reduce the pressure of the radially inner part of the back-surface gap. Accordingly, it is possible to suppress entry of a leakage flow from the back-surface gap to the bearing, and suppress inflow of the leakage flow into electric devices such as the motor.
  • each of the ribs has an airfoil shape.
  • each of the ribs is disposed so as to extend in a direction inclined from a radial direction of the compressor impeller such that a radially outer end of the rib is positioned on an upstream side of a radially inner end of the rib with respect to a rotational direction of the compressor impeller.
  • the electric supercharger according to any one of the above (1) to (6) further includes, between the mechanical seal and the back surface of the compressor impeller, a rotary part protruding from the rotational shaft toward an outer side in a radial direction of the compressor impeller, the rotary part being configured to rotate together with the rotational shaft.
  • the electric supercharger according to any one of the above (1) to (7) further includes an abradable coating layer formed on at least a part of the back surface of the compressor impeller, or at least a part of a surface of the back-surface side casing which faces the back surface of the compressor impeller.
  • the abradable coating layer in a case where the abradable coating layer is formed on at least a part of the back surface of the compressor impeller, the abradable coating layer would be ground upon rotation of the compressor impeller even if the abradable coating layer formed on the back surface of the compressor impeller makes contact with a surface of the back-surface side casing that faces the back surface of the compressor impeller. Thus, it is possible to reduce the clearance between the back surface and the back-surface side casing.
  • the abradable coating layer is formed on at least a part of a surface of the back-surface side casing that faces the back surface of the compressor impeller, the abradable coating layer would be ground upon rotation of the compressor impeller even if the abradable coating layer formed on a facing surface of the back-surface side casing that faces the back surface of the compressor impeller makes contact with the back surface of the compressor impeller.
  • it is possible to reduce the clearance between the back surface and the back-surface side casing.
  • the compressor impeller receives a thrust force toward the upstream in the intake direction of air, in the axial direction, when air is compressed.
  • the compressor impeller receives a thrust force toward the upstream in the intake direction of air, in the axial direction, when air is compressed.
  • a ratio G/R of a size G of a gap between the back surface of the compressor impeller and the back-surface side casing to an outer diameter R of the compressor impeller is less than 0.5%.
  • the above electric supercharger (9) it is possible to promote a pressure decrease toward the inner side in the radial direction, in the back-surface gap, effectively.
  • the former when comparing a case where the abradable coating layer is provided and the ratio C/Ri is set to be 0.8% and a case where the abradable coating layer is not provided and C/Ri is set to be 0.25%, the former can reduce more pressure of the radially inner part of the back-surface gap by 26% compared to the latter.
  • the electric supercharger according to any one of the above (1) to (9) further includes an internal-pressure adjustment mechanism configured to adjust a pressure inside the back-surface side casing by bringing into communication an inside and an outside of the back-surface side casing.
  • an electric supercharger capable of suppressing entry of a leakage flow to the bearing side via the gap between the back surface of the compressor impeller and the casing.
  • FIG. 1 is a schematic diagram showing a schematic cross-sectional view of an electric supercharger 2 according to an embodiment.
  • FIG. 2 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 A) according to an embodiment, showing a configuration example of a mechanical seal 20 .
  • FIG. 3 is a view of a compressor impeller 4 in rotation, in the electric supercharger 2 ( 2 A) depicted in FIG. 2 .
  • FIG. 4 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 B) according to an embodiment.
  • FIG. 5 is a diagram showing a configuration example of the ribs 44 depicted in FIG. 4 , showing an example of arrangement of the ribs 44 in an axial-directional view.
  • FIG. 6 is a diagram showing a configuration example of the ribs 44 depicted in FIG. 4 , showing an example of arrangement of the ribs 44 in an axial-directional view.
  • FIG. 7 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 C) according to an embodiment.
  • FIG. 8 is a diagram showing a configuration example of the rotary part 50 depicted in FIG. 7 , showing an example of the shape of the rotary part 50 in an axial-directional view.
  • FIG. 10 is a diagram showing a configuration example of the rotary part 50 depicted in FIG. 7 , showing an example of the shape of the rotary part 50 in an axial-directional view.
  • FIG. 11 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 D) according to an embodiment.
  • FIG. 12 is a graph showing the relationship between the radial-directional position R and the gauge pressure P of the back-surface gap ‘g’.
  • the dotted line indicates an electric supercharger 2 ( 2 A) not including an abradable coating layer 90
  • the solid line indicates an electric supercharger 2 ( 2 D) including an abradable coating layer 90 formed on the facing surface 21 .
  • FIG. 13 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 E) according to an embodiment.
  • FIG. 14 is a diagram showing an example of arrangement of a communication hole 53 that serves as an internal-pressure adjustment mechanism.
  • FIG. 15 is a diagram showing an example of arrangement of a communication hole 53 that serves as an internal-pressure adjustment mechanism.
  • FIG. 16 is a schematic configuration diagram of an engine device 100 to which an electric supercharger 2 ( 2 A to 2 E) can be applied preferably.
  • FIG. 17 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 F) according to another embodiment.
  • FIG. 18 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 G) according to another embodiment.
  • FIG. 19 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 H) according to another embodiment.
  • FIG. 20 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 I) according to another embodiment.
  • FIG. 21 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 J) according to another embodiment.
  • FIG. 22 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 K) according to another embodiment.
  • FIG. 23 is a schematic configuration diagram of an engine device 100 to which an electric supercharger 2 ( 2 A to 2 K) can be applied.
  • an expression of relative or absolute arrangement such as “in a direction”, “along a direction”, “parallel”, “orthogonal”, “centered”, “concentric” and “coaxial” shall not be construed as indicating only the arrangement in a strict literal sense, but also includes a state where the arrangement is relatively displaced by a tolerance, or by an angle or a distance whereby it is possible to achieve the same function.
  • an expression of an equal state such as “same” “equal” and “uniform” shall not be construed as indicating only the state in which the feature is strictly equal, but also includes a state in which there is a tolerance or a difference that can still achieve the same function.
  • an expression of a shape such as a rectangular shape or a cylindrical shape shall not be construed as only the geometrically strict shape, but also includes a shape with unevenness or chamfered corners within the range in which the same effect can be achieved.
  • FIG. 1 is a schematic diagram showing a schematic cross-sectional view of an electric supercharger 2 according to an embodiment.
  • the electric supercharger 2 includes a compressor impeller 4 , a rotational shaft 6 , an impeller casing 8 , bearings 10 A, 10 B, a motor 12 , a back-surface side casing 14 (stationary member), and a mechanical seal 20 .
  • circumferential direction of the compressor impeller 4 is referred to as merely “circumferential direction”
  • radial direction of the compressor impeller 4 is referred to as merely “radial direction”
  • axial direction of the compressor impeller 4 is referred to as merely “axial direction”.
  • the impeller casing 8 is formed so as to surround the compressor impeller 4 , and is configured to guide intake air to the inlet of the compressor impeller 4 and discharge air compressed by the compressor impeller 4 .
  • the bearings 10 A, 10 B are configured as ball bearings that support the rotational shaft 6 rotatably, and as grease-lubrication type bearings which contain grease as a lubricating agent sealed around balls held between an inner race and an outer race which are not depicted.
  • the bearing 10 A is positioned between the mechanical seal 20 and the motor 12 in the axial direction, and is positioned between the back-surface side casing 14 and the rotational shaft 6 in the radial direction.
  • the bearing 10 B is positioned opposite to the bearing 10 A across the motor 12 in the axial direction, and is positioned between the back-surface side casing 14 and the rotational shaft 6 in the radial direction.
  • the motor 12 is configured to transmit a driving force to the compressor impeller 4 via the rotational shaft 6 .
  • the motor 12 is positioned between the bearing 10 A and the bearing 10 B in the axial direction.
  • the back-surface side casing 14 faces the back surface 16 of the compressor impeller 4 via a gap, and is configured to surround the mechanical seal 20 , the bearings 10 A, 10 B, and the motor 12 . Further, the back-surface side casing 14 includes an inverter housing portion 18 for housing an inverter (not depicted), on the opposite side from the motor 12 across the bearing 10 B.
  • the mechanical seal 20 is positioned between the back surface 16 of the compressor impeller 4 and the bearing 10 A in the axial direction, and is configured to seal the gap between the rotational shaft 6 and the back-surface side casing 14 .
  • FIG. 2 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 A) according to an embodiment, showing a configuration example of a mechanical seal 20 .
  • FIG. 3 is a view of a compressor impeller 4 in rotation, in the electric supercharger 2 ( 2 A) depicted in FIG. 2 .
  • the mechanical seal 20 includes a stationary ring 22 , a rotary ring 24 , and a biasing member 26 .
  • the stationary ring 22 is formed to have an annular shape along the circumferential direction, and is supported on the back-surface side casing 14 .
  • the stationary ring 22 is at a position that is between the rotary ring 24 and the back-surface side casing 14 , and between the back-surface side casing 14 and the rotational shaft 6 .
  • the rotary ring 24 is disposed between the back surface 16 of the compressor impeller 4 and the stationary ring 22 , and is configured to have an annular shape along the circumferential direction so as to face the stationary ring 22 so as to be capable of being in contact with the stationary ring 22 .
  • the rotary ring 24 is configured to protrude toward an outer side from the rotational shaft 6 in the radial direction, and rotate together with the rotational shaft 6 .
  • the biasing member 26 is configured to bias one of the stationary ring 22 or the rotary ring 24 toward the other one of the stationary ring 22 or the rotary ring 24 .
  • the biasing member 26 includes an elastic member (e.g., coil spring, disc spring, or rubber), and is interposed between the stationary ring 22 and the back-surface side casing 14 so as to bias the stationary ring 22 toward the rotary ring 24 .
  • a groove 34 is formed on a facing surface 32 , which is one of a surface 28 of the rotary ring 24 that faces the stationary ring 22 , or a surface 30 of the stationary ring 22 that faces the rotary ring 24 (in the depicted embodiment, the facing surface 32 is the surface 28 of the rotary ring 24 facing the stationary ring 22 ). As depicted in FIG.
  • the groove 34 on the facing surface 32 is formed so as to be in communication with a space 36 on the inner side of the facing surface 32 in the radial direction (space between the stationary ring 22 and the rotational shaft 6 ), and so as not to be in communication with the space 38 on the outer side of the facing surface 32 in the radial direction (of the back-surface gap ‘g’ between the back surface 16 and the back-surface side casing 14 , the outer portion of the stationary ring 22 ), in a state where the stationary ring 22 and the rotary ring 24 are in contact.
  • the groove 34 is disposed from a position on the inner side, in the radially direction, of the radially inner end 40 of the contact portion between the stationary ring 22 and the rotary ring 24 on the facing surface 32 to a position that does not reach the radially outer end 42 of the contact portion between the stationary ring 22 and the rotary ring 24 , on the facing surface 32 .
  • the mechanical seal 20 functions as a contact seal. Accordingly, it is possible to suppress entry of a leakage flow from the back-surface gap ‘g’ to the bearing 10 A, and suppress inflow of the leakage flow into electric devices such as the motor 12 . Thus, it is possible to suppress occurrence of malfunction or the like of the electric devices, and operate the electric supercharger stably.
  • FIG. 4 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 B) according to an embodiment.
  • FIG. 5 is a diagram showing a configuration example of the ribs 44 depicted in FIG. 4 , showing an example of arrangement of the ribs 44 in an axial-directional view.
  • FIG. 6 is a diagram showing a configuration example of the ribs 44 depicted in FIG. 4 , showing an example of arrangement of the ribs 44 in an axial-directional view.
  • a plurality of ribs 44 are disposed at intervals in the circumferential direction, on the back surface 16 of the compressor 4 .
  • a centrifugal force toward the outer side in the radial direction is applied to air in the back-surface gap ‘g’ upon rotation of the compressor impeller 4 , and thereby it is possible to decrease the pressure of the radially inner part of the back-surface gap ‘g’. Accordingly, it is possible to suppress entry of a leakage flow from the back-surface gap ‘g’ to the bearing 10 A, and suppress inflow of the leakage flow into electric devices such as the motor.
  • each of the ribs 44 is formed to extend along a direction that intersects with the circumferential direction. Further, in the embodiment depicted in FIG. 5 , the plurality of ribs 44 are disposed so as to extend in a radial fashion along a direction orthogonal to the circumferential direction (radial direction).
  • the plurality of ribs 44 extending in a direction orthogonal to the circumferential direction rotates with the compressor impeller 4 , and thus it is possible to apply the centrifugal force toward the outer side in the radial direction effectively to air in the back-surface gap ‘g’, and reduce the pressure of the radially inner part of the back-surface gap ‘g’. Accordingly, it is possible to suppress entry of a leakage flow from the back-surface gap ‘g’ to the bearing 10 A, and suppress inflow of the leakage flow into electric devices such as the motor.
  • each of the ribs 44 has an airfoil shape.
  • each rib 44 is disposed so as to extend in a direction inclined from the radial direction, such that the radially outer end 46 of the rib 44 is positioned on the upstream side of the radially inner end 48 of the rib 44 , with respect to the rotational direction of the compressor impeller 4 .
  • FIG. 7 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 C) according to an embodiment.
  • FIG. 8 is a diagram showing a configuration example of the rotary part 50 depicted in FIG. 7 , showing an example of the shape of the rotary part 50 in an axial-directional view.
  • FIG. 9 is a diagram showing a configuration example of the rotary part 50 depicted in FIG. 7 , showing an example of the shape of the rotary part 50 in an axial-directional view.
  • FIG. 10 is a diagram showing a configuration example of the rotary part 50 depicted in FIG. 7 , showing an example of the shape of the rotary part 50 in an axial-directional view.
  • the electric supercharger further includes a rotary part 50 which protrudes outward in the radial direction from the rotational shaft 6 , between the mechanical seal 20 and the back surface 16 of the compressor impeller 4 , and which is configured to rotate together with the rotational shaft 6 .
  • the shape of the rotary part 50 is not particularly limited.
  • the rotary part 51 may have an annular shape as depicted in FIG. 8 , or may have a plurality of protrusions 52 (four protrusions 52 in the depicted embodiment) protruding outward in the radial direction from the annular shape as depicted in FIGS. 9 and 10 .
  • the protrusions 52 may protrude in a radial fashion along the radial direction as depicted in FIG. 9 for instance, or may have a tapered shape protruding diagonally with respect to the radial direction as depicted in FIG. 10 .
  • FIG. 11 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 D) according to an embodiment.
  • FIG. 12 is a graph showing the relationship between the radial-directional position R and the gauge pressure P of the back-surface gap ‘g’.
  • the dotted line indicates an electric supercharger 2 ( 2 A) not including an abradable coating layer 90
  • the solid line indicates an electric supercharger 2 ( 2 D) including an abradable coating layer 90 formed on the facing surface 21 .
  • FIG. 13 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 E) according to an embodiment.
  • an abradable coating layer 90 is formed on at least a part of the facing surface 21 facing the back surface 16 of the compressor impeller 4 (the entire facing surface 21 in the depicted embodiment).
  • the abradable coating layer 90 would be ground upon rotation of the compressor impeller 4 even if the abradable coating layer 90 formed on the facing surface 21 makes contact with the back surface 16 of the compressor impeller 4 .
  • FIG. 12 is a graph schematically showing the relationship between the radial-directional position R and the gauge pressure P of the back-surface gap ‘g’.
  • the dotted line indicates an electric supercharger 2 ( 2 A) not including an abradable coating layer 90
  • the solid line indicates an electric supercharger 2 ( 2 D) including an abradable coating layer 90 formed on the facing surface 21 .
  • the clearance C between the back surface 16 and the back-surface side casing 14 of the electric supercharger 2 ( 2 D) is set to be smaller than the clearance between the back surface 16 and the back-surface side casing 14 of the electric supercharger 2 ( 2 A).
  • the pressure decreases in the back-surface gap g, toward the inner side in the radial direction. Particularly in a region where the radial-directional position R is small, the pressure in the back-surface gap ‘g’ in the electric supercharger 2 ( 2 D) is reduced considerably compared to that in the electric supercharger 2 ( 2 A).
  • the electric supercharger 2 by promoting the pressure decrease toward the inner side in the radial direction in the back-surface gap ‘g’, it is possible to reduce the axial-directional pressure difference between the pressure of the radially inner part (pressure near the mechanical seal 20 ) of the back-surface gap ‘g’ and the pressure near the bearing 10 A and thus it is possible to suppress entry of a leakage flow toward the bearing 10 A (toward the mechanical seal 20 ) from the back-surface gap ‘g’. Accordingly, it is possible to suppress inflow of the leakage flow into electric devices such as the motor 12 and an inverter (not depicted). Thus, it is possible to suppress occurrence of malfunction or the like of the electric devices, and operate the electric supercharger 2 stably.
  • the compressor impeller 4 receives a thrust force toward the upstream in the intake direction of air (left side in the drawing), in the axial direction, when air is compressed.
  • the above electric supercharger 2 it is possible to reduce the pressure in the back-surface gap ‘g’ for the compressor impeller 4 , and thus it is possible to reduce the thrust force in the axial direction.
  • the ratio C/Ri of the clearance C between the back surface 16 of the compressor impeller 4 and the back-surface side casing 14 to the outer diameter Ri of the compressor impeller 4 is less than 0.5%.
  • the former when comparing a case where the abradable coating layer 90 is provided and the ratio C/Ri is set to be 0.8% and a case where the abradable coating layer 90 is not provided and C/Ri is set to be 0.25%, the former can reduce more pressure of the radially inner part of the back-surface gap ‘g’ by 26% compared to the latter.
  • the abradable coating layer 90 is formed on at least a part of the back surface 16 of the compressor impeller 4 . Furthermore, the ratio C/Ri of the clearance C between the back surface 16 of the compressor impeller 4 and the back-surface side casing 14 to the outer diameter Ri of the compressor impeller 4 is less than 0.5%.
  • the abradable coating layer 90 would be ground upon rotation of the compressor impeller 4 even if the abradable coating layer 90 formed on the back surface 16 of the compressor impeller 4 makes contact with the facing surface 21 of the back-surface side casing 14 .
  • the electric supercharger 2 ( 2 A to 2 E) further includes a communication hole 53 serving as an internal-pressure adjustment mechanism, configured to adjust the pressure inside the back-surface side casing 14 by bringing the inside and the outside of the back-surface side casing 14 into communication.
  • the communication hole 53 may be disposed on the compressor side of the back-surface side casing 14 as depicted in FIG. 14 , or on the inverter side as depicted in FIG. 15 , or on both sides.
  • the position, shape, and dimension like hole diameter of the communication hole 53 are to be designed to be optimum in accordance with the size of the electric supercharger 2 . Further, in the embodiment depicted in FIGS.
  • a waterproof ventilation filter 55 is disposed, which protects the inside of the back-surface side casing 14 from dust, water, oil, and the like while adjusting the pressure and the temperature inside the back-surface side casing 14 .
  • FIG. 16 is a schematic configuration diagram of an engine device 100 to which the above described electric supercharger 2 ( 2 A to 2 E) can be applied preferably.
  • FIG. 16 is a diagram of an embodiment of an engine device 100 in a case where the electric supercharger 2 is used as a high-pressure stage supercharger of a two-stage supercharging system.
  • the engine device 100 depicted in FIG. 16 includes, as depicted in the drawing, an engine 54 , an intake passage 56 through which intake gas to be supplied to the engine 54 flows, an exhaust passage 58 through which exhaust gas discharged from the engine 54 flows, a turbocharger 60 , and the above described electric supercharger 2 .
  • the turbocharger 60 includes an exhaust turbine 64 disposed in the exhaust passage 58 , a compressor 62 disposed in the intake passage 56 , and an exhaust turbine shaft 63 coupling the exhaust turbine 64 and the compressor 62 .
  • the turbocharger 60 is configured such that the exhaust turbine 64 is driven by exhaust gas discharged from the engine 54 , and thereby the compressor 62 is coaxially driven via the turbine shaft 63 , so as to supercharge intake gas flowing through the intake passage 56 .
  • the electric supercharger 2 is disposed on the downstream side of the compressor 62 in the intake passage 56 , and intake gas compressed by the compressor 62 of the turbocharger 60 is supplied to the compressor impeller 4 of the electric supercharger 2 .
  • the engine device 100 of the present embodiment is configured as a two-stage supercharging system in which the turbocharger 60 is provided as a low-pressure stage supercharger and the electric supercharger 2 is provided as a high-pressure stage supercharger.
  • a bypass intake passage 66 bypassing the electric supercharger 2 is connected to the intake passage 56 .
  • a bypass valve 68 is disposed in the bypass intake passage 66 . Further, by adjusting the valve opening degree of the bypass valve 68 , the flow rate of intake gas flowing into the electric supercharger 2 is controlled.
  • an intermediate cooler 70 for cooling intake gas to be supplied to the engine 54 is disposed.
  • the engine device 100 includes an EGR passage 72 that connects the downstream side of the exhaust turbine 64 in the exhaust passage 58 and the upstream side of the compressor 62 in the intake passage 56 .
  • An EGR valve 74 is disposed in the EGR passage 72 . Further, by adjusting the valve opening degree of the EGR valve 74 , exhaust gas having a flow rate corresponding to the valve opening degree returns to the intake passage 56 . Further, intake gas containing the recirculated exhaust gas is supplied to the compressor impeller 4 of the electric supercharger 2 .
  • the bypass valve 68 is closed when the engine rotates at a low speed.
  • the intake gas pressurized by the turbocharger 60 serving as a low-pressure stage supercharger is supplied to the electric supercharger 2 serving as a high-pressure stage supercharger as indicated by the arrow ‘a’, to be pressurized further.
  • the differential pressure between the radially outer part and the radially inner part of the compressor in the electric supercharger 2 becomes high, and high-temperature and high-pressure intake air enters the above described back-surface gap ‘g’.
  • the bypass valve 68 is open and the electric supercharger 2 is stopped when the engine rotates at a high speed.
  • the intake gas pressurized by the turbocharger 60 serving as a low-pressure stage supercharger is supplied to the downstream side of the electric supercharger 2 through the bypass intake passage 66 , as indicated by the arrow ‘b’.
  • the boost pressure of the turbocharger 60 creates a differential pressure between the radially outer part and the radially inner part of the compressor in the electric supercharger 2 , and causes intake air to enter the above described back-surface gap ‘g’.
  • the back-surface side casing 14 surrounds the mechanical seal 20 , the bearings 10 A, 10 B, and the motor 12 .
  • the configuration of the back-surface side casing 14 is not limited to this.
  • the back-surface side casing 14 may surround only the mechanical seal 20 , and a casing other than the back-surface side casing 14 may surround the bearings 10 A, 10 B and the motor 12 .
  • the back-surface side casing 14 may surround only the mechanical seal 20 and the bearing 10 A, and a casing other than the back-surface side casing 14 may surround the bearing 10 B and the motor 12 .
  • the electric supercharger 2 ( 2 A to 2 E) includes the mechanical seal 20
  • the electric supercharger 2 may not necessarily include the mechanical seal 20 in another embodiment.
  • FIG. 17 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 F) according to another embodiment.
  • FIG. 18 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 G) according to another embodiment.
  • FIG. 19 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 H) according to another embodiment.
  • FIG. 20 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 I) according to another embodiment.
  • FIG. 21 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 J) according to another embodiment.
  • FIG. 22 is a schematic diagram showing a schematic cross-sectional view in the vicinity of a back surface 16 of a compressor impeller 4 of an electric supercharger 2 ( 2 K) according to another embodiment.
  • the basic configuration of the electric supercharger 2 ( 2 F to 2 K) is similar to that of the electric supercharger 2 depicted in FIG. 1 , except that the mechanical seal 20 is not provided.
  • the same configurations are associated with the same reference numerals to omit description, and the characteristic configurations of the respective modified examples will be mainly described.
  • the electric supercharger 2 ( 2 F to 2 H) further includes a rotary part 76 which protrudes outward in the radial direction from the rotational shaft 6 , between the back-surface side casing 14 and the back surface 16 of the compressor impeller 4 , and which is configured to rotate together with the rotational shaft 6 . Further, the radially outer end 78 of the rotary part 76 is positioned on the outer side of the radially inner end 80 of the back-surface side casing 14 in the radial direction.
  • the shape of the rotary part 76 is not particularly limited, the respective shapes of the rotary part 50 described with reference to FIGS. 8 to 10 may be applied. Furthermore, the rotary part 76 may be disposed at a distance from the back surface 16 of the compressor impeller 4 as depicted in FIG. 17 , or in contact with the back surface 16 of the compressor impeller 4 as depicted in FIGS. 18 and 19 , or integrally with the compressor impeller 4 or a non-depicted sleeve engaged with the rotational shaft 6 . Further, as depicted in FIGS. 18 and 19 , the rotary part 76 may protrude toward the back surface 16 past the facing surface 21 of the back-surface side casing 14 that faces the back surface 16 .
  • the rotary part 76 may include a protruding portion 84 protruding in the axial direction so as to enter the inside of the recessed portion 82 as depicted in FIG. 19 .
  • the electric supercharger 2 ( 2 I) includes a seal unit 9 instead of the mechanical seal 20 of the electric supercharger 2 ( 2 B) depicted in FIG. 4 .
  • a plurality of ribs 44 are disposed at intervals in the circumferential direction, on the back surface 16 of the compressor 4 .
  • the seal unit 9 includes a sleeve 86 and at least one piston ring 88 (in the depicted embodiment, two piston rings 88 ).
  • the sleeve 86 is disposed such that an end side of the sleeve 86 is in contact with the back surface 16 of the compressor impeller 4 , in a state where the sleeve 86 is engaged with the rotational shaft 6 .
  • the piston ring 88 is engaged with an annular groove disposed on the outer peripheral surface of the sleeve 86 and is in contact with the back-surface side casing 14 , thereby sealing the gap between the rotational shaft 6 and the back-surface side casing 14 .
  • the electric supercharger 2 ( 2 J) includes a seal unit 9 instead of the mechanical seal 20 of the electric supercharger 2 ( 2 D) depicted in FIG. 11 .
  • an abradable coating layer 90 is formed on at least a part of the facing surface 21 facing the back surface 16 of the compressor impeller 4 (the entire facing surface 21 in the depicted embodiment).
  • the compressor impeller 4 receives a thrust force toward the upstream in the intake direction of air (left side in the drawing), in the axial direction, when air is compressed.
  • the above electric supercharger 2 ( 2 J) it is possible to reduce the pressure in the back-surface gap ‘g’ for the compressor impeller 4 , and thus it is possible to reduce the thrust force in the axial direction.
  • the electric supercharger 2 ( 2 K) includes a seal unit 9 instead of the mechanical seal 20 of the electric supercharger 2 ( 2 E) depicted in FIG. 13 .
  • the abradable coating layer 90 is formed on at least a part of the back surface 16 of the compressor impeller 4 .
  • the compressor impeller 4 receives a thrust force toward the upstream in the intake direction of air (left side in the drawing), in the axial direction, when air is compressed.
  • the above electric supercharger 2 ( 2 K) it is possible to reduce the pressure in the back-surface gap ‘g’ for the compressor impeller 4 , and thus it is possible to reduce the thrust force in the axial direction.
  • the electric supercharger 2 ( 2 A to 2 E) is described as preferably applicable as a high-pressure stage supercharger of a two-stage supercharging system in the embodiment depicted in FIG. 16
  • the electric supercharger 2 ( 2 A to 2 K) may be used as a low-pressure stage supercharger of a two-stage supercharging system as depicted in FIG. 23 .
  • the electric supercharger 2 is disposed on the upstream side of the compressor 62 in the intake passage 56 , and intake gas compressed by the electric supercharger 2 is supplied to the compressor 62 of the turbocharger 60 .
  • the engine device 110 is configured as a two-stage supercharging system in which the turbocharger 60 is provided as a high-pressure stage supercharger and the electric supercharger 2 is provided as a low-pressure stage supercharger.
  • a bypass intake passage 66 bypassing the electric supercharger 2 is connected to the intake passage 56 .
  • a bypass valve 68 is disposed in the bypass intake passage 66 . Further, by adjusting the valve opening degree of the bypass valve 68 , the flow rate of intake gas flowing into the electric supercharger 2 is controlled.
  • an intermediate cooler 70 for cooling intake gas to be supplied to the engine 54 is disposed.
  • the engine device 110 includes an EGR passage 72 that connects the downstream side of the exhaust turbine 64 in the exhaust passage 58 and the upstream side of the electric supercharger 2 in the intake passage 56 .
  • An EGR valve 74 is disposed in the EGR passage 72 . Further, by adjusting the valve opening degree of the EGR valve 74 , exhaust gas having a flow rate corresponding to the valve opening degree returns to the intake passage 56 . Further, intake gas containing the recirculated exhaust gas is supplied to the compressor impeller 4 of the electric supercharger 2 .
  • the bypass valve 68 is closed when the engine rotates at a low speed.
  • the intake gas pressurized by the electric supercharger 2 serving as a low-pressure stage supercharger is supplied to the compressor 62 of the turbocharger 60 serving as a high-pressure stage supercharger as indicated by the arrow ‘c’, to be pressurized further.
  • the boost pressure of the electric supercharger 2 is applied to the gap between the radially outer part and the radially inner part of the compressor in the electric supercharger 2 , and causes intake air to enter the above described back-surface gap ‘g’.
  • the bypass valve 68 is open and the electric supercharger 2 is stopped when the engine rotates at a high speed.
  • intake gas is supplied to the compressor 62 through the bypass intake passage 66 , and thus substantially no intake air enters the back-surface gap ‘g’ of the electric supercharger 2 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)
US16/326,640 2017-03-29 2017-03-29 Electric supercharger Abandoned US20200378389A1 (en)

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PCT/JP2017/012938 WO2018179144A1 (ja) 2017-03-29 2017-03-29 電動過給機

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US (1) US20200378389A1 (ja)
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JP (1) JP6618651B2 (ja)
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WO (1) WO2018179144A1 (ja)

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US20200408220A1 (en) * 2019-06-28 2020-12-31 Trane International Inc. Impeller with external blades
EP4050217A1 (de) * 2021-02-26 2022-08-31 BMTS Technology GmbH & Co. KG Gasverdichter
WO2023083588A1 (de) * 2021-11-10 2023-05-19 Robert Bosch Gmbh Radialverdichter und verfahren zum betreiben eines radialverdichters

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US11598347B2 (en) * 2019-06-28 2023-03-07 Trane International Inc. Impeller with external blades
EP4050217A1 (de) * 2021-02-26 2022-08-31 BMTS Technology GmbH & Co. KG Gasverdichter
WO2023083588A1 (de) * 2021-11-10 2023-05-19 Robert Bosch Gmbh Radialverdichter und verfahren zum betreiben eines radialverdichters

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EP3489484A4 (en) 2020-01-15
JP6618651B2 (ja) 2019-12-11
WO2018179144A1 (ja) 2018-10-04
JPWO2018179144A1 (ja) 2019-07-18
EP3489484A1 (en) 2019-05-29
CN109563772B (zh) 2021-01-26
EP3489484B1 (en) 2021-05-05
CN109563772A (zh) 2019-04-02

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