EP3489484B1 - Electrically driven supercharger - Google Patents

Electrically driven supercharger Download PDF

Info

Publication number
EP3489484B1
EP3489484B1 EP17904301.3A EP17904301A EP3489484B1 EP 3489484 B1 EP3489484 B1 EP 3489484B1 EP 17904301 A EP17904301 A EP 17904301A EP 3489484 B1 EP3489484 B1 EP 3489484B1
Authority
EP
European Patent Office
Prior art keywords
compressor impeller
electric supercharger
stationary ring
rotational shaft
gap
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.)
Active
Application number
EP17904301.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3489484A4 (en
EP3489484A1 (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
Publication of EP3489484A1 publication Critical patent/EP3489484A1/en
Publication of EP3489484A4 publication Critical patent/EP3489484A4/en
Application granted granted Critical
Publication of EP3489484B1 publication Critical patent/EP3489484B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • 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
    • 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 JP 2015-537162 A ).
  • WO 2016/000934 A1 discloses an electric compressor for an internal combustion engine comprising an electric motor arranged in a motor space, and an impeller which is fastened on a drive shaft arranged to be driven by the electric motor.
  • a back-surface side casing faces a back surface of the impeller with a gap and surrounds the rotational shaft.
  • a bearing is disposed between the back-surface side casing and the rotational shaft so as to support the drive shaft.
  • a mechanical seal is positioned between the back surface of the impeller and the bearing in an axial direction of the impeller and is configured to seal a gap between the drive shaft and the back-surface side casing.
  • the mechanical seal furthermore includes a stationary ring supported on the back-surface side casing and a rotary ring protruding from the drive shaft to a radial outer side and spline-connected to the drive shaft so as to co-rotate with it.
  • the rotary ring seems to be tightly arranged between the bearing and the impeller.
  • the stationary ring contacts the radial inner and radial outer sides of a small axial groove formed in a contact surface of the rotary ring facing the stationary ring and thus tightly seals the groove.
  • the stationary ring and the rotary ring are in contact with each other, there is no communication of that groove with a space on a radial inner side of the facing surface and between the stationary ring and the drive shaft because the groove is tightly sealed.
  • 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 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 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 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 10A, 10B, 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 10A, 10B 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 10A 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 10B is positioned opposite to the bearing 10A 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 10A and the bearing 10B 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 10A, 10B, 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 10B.
  • the mechanical seal 20 is positioned between the back surface 16 of the compressor impeller 4 and the bearing 10A 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 (2A) 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 (2A) 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.
  • 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 (2B) 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.
  • 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 10A, 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 (2C) 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 (2D) 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 (2A) not including an abradable coating layer 90, and the solid line indicates an electric supercharger 2 (2D) 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 (2E) 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 (2A) not including an abradable coating layer 90
  • the solid line indicates an electric supercharger 2 (2D) 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 (2D) 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 (2A).
  • 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 10A and thus it is possible to suppress entry of a leakage flow toward the bearing 10A (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 (2A to 2E) 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 (2A to 2E) 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 10A, 10B, 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 10A, 10B and the motor 12.
  • the back-surface side casing 14 may surround only the mechanical seal 20 and the bearing 10A, and a casing other than the back-surface side casing 14 may surround the bearing 10B and the motor 12.
  • the electric supercharger 2 may not necessarily include the mechanical seal 20 in another example which is not acccording tot he invention as claimed.
  • 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 (2F) according to another example.
  • 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 (2G) according to another example.
  • 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 (2H) according to another example.
  • 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 (21) according to another example.
  • 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 (2J) according to another example.
  • 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 (2K) according to another example.
  • the basic configuration of the electric supercharger 2 (2F to 2K) 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 (2F to 2H) 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 (21) includes a seal unit 9 instead of the mechanical seal 20 of the electric supercharger 2 (2B) 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 example, 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 (2J) includes a seal unit 9 instead of the mechanical seal 20 of the electric supercharger 2 (2D) 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 example).
  • 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 (2J) 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 (2K) includes a seal unit 9 instead of the mechanical seal 20 of the electric supercharger 2 (2E) 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 (2K) 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 (2A to 2E) 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 (2A to 2K) 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.

Landscapes

  • 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)
EP17904301.3A 2017-03-29 2017-03-29 Electrically driven supercharger Active EP3489484B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/012938 WO2018179144A1 (ja) 2017-03-29 2017-03-29 電動過給機

Publications (3)

Publication Number Publication Date
EP3489484A1 EP3489484A1 (en) 2019-05-29
EP3489484A4 EP3489484A4 (en) 2020-01-15
EP3489484B1 true EP3489484B1 (en) 2021-05-05

Family

ID=63674622

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17904301.3A Active EP3489484B1 (en) 2017-03-29 2017-03-29 Electrically driven supercharger

Country Status (5)

Country Link
US (1) US20200378389A1 (ja)
EP (1) EP3489484B1 (ja)
JP (1) JP6618651B2 (ja)
CN (1) CN109563772B (ja)
WO (1) WO2018179144A1 (ja)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE102021212662A1 (de) * 2021-11-10 2023-05-11 Robert Bosch Gesellschaft mit beschränkter Haftung Radialverdichter und Verfahren zum Betreiben eines Radialverdichters

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB452019A (en) * 1935-02-14 1936-08-14 Watkins & Watson Ltd Improvements in and connected with centrifugal pumps, fans and blowers
US2679412A (en) * 1950-03-24 1954-05-25 Read Standard Corp Seal
JPS58106521U (ja) * 1982-01-12 1983-07-20 日産自動車株式会社 タ−ボ過給機の軸封装置
JPS60107332U (ja) * 1983-12-21 1985-07-22 日産自動車株式会社 排気タ−ビン過給機
JPS62183036U (ja) * 1986-05-13 1987-11-20
US4820115A (en) * 1987-11-12 1989-04-11 Dresser Industries, Inc. Open impeller for centrifugal compressors
JP4028923B2 (ja) * 1997-12-10 2008-01-09 株式会社協立 滑り部材付きターボチャージャ
FR2827919B1 (fr) * 2001-07-26 2004-03-05 Thermodyn Garniture d'etancheite pour compresseur et compresseur centrifuge pourvu d'une telle garniture
JP2005163643A (ja) * 2003-12-03 2005-06-23 Koyo Seiko Co Ltd 電動駆動式過給機
JP2005226470A (ja) * 2004-02-10 2005-08-25 Kyoritsu:Kk ターボチャージャ
JP2007309101A (ja) * 2006-05-16 2007-11-29 Toyota Motor Corp 電動機付き過給機の冷却構造
JP2011021545A (ja) * 2009-07-16 2011-02-03 Ihi Corp ターボチャージャのコンプレッサ構造
JP2011052558A (ja) * 2009-08-31 2011-03-17 Toyota Motor Corp 過給機
JP5433643B2 (ja) * 2011-07-15 2014-03-05 三菱重工業株式会社 電動過給装置及び多段過給システム
JP5535992B2 (ja) * 2011-07-15 2014-07-02 三菱重工業株式会社 電動過給圧縮機、その組立方法及び内燃機関
KR101429846B1 (ko) * 2013-02-06 2014-08-12 한승주 자기 구동 공기충전장치
DE102015106640A1 (de) * 2014-07-02 2016-01-07 Pierburg Gmbh Elektrischer Verdichter für eine Verbrennungskraftmaschine
JP2016180337A (ja) * 2015-03-23 2016-10-13 株式会社デンソー 過給装置
CN209875297U (zh) * 2019-04-01 2019-12-31 中国科学院合肥物质科学研究院 一种新型一体式电子涡轮增压器

Also Published As

Publication number Publication date
JPWO2018179144A1 (ja) 2019-07-18
EP3489484A4 (en) 2020-01-15
JP6618651B2 (ja) 2019-12-11
CN109563772A (zh) 2019-04-02
CN109563772B (zh) 2021-01-26
EP3489484A1 (en) 2019-05-29
US20200378389A1 (en) 2020-12-03
WO2018179144A1 (ja) 2018-10-04

Similar Documents

Publication Publication Date Title
US9963998B2 (en) Assembly with bearings and spacer
US20070036664A1 (en) Supercharger with electric motor
US9874217B2 (en) Turbomachine shaft sealing arrangement
US9695708B2 (en) Turbocharger spring assembly
EP3489484B1 (en) Electrically driven supercharger
WO2012036122A1 (ja) 固定翼式ターボチャージャ
WO2013106303A1 (en) Sealing system and turbocharger incorporating the same
CN106050332B (zh) 涡轮增压器轴承组件
US20140003908A1 (en) Gas pressure biased sealing method for an actuating shaft
EP3441577B1 (en) Turbocharger with gas and liquid flow paths
US11732606B2 (en) Cooling structure and turbocharger
US11686244B2 (en) Variable-capacity turbocharger
JP6899232B2 (ja) 電動過給機
US9267441B1 (en) Multi-piece piston ring for a turbocharger shaft assembly
KR101532439B1 (ko) 배기 가스 터보 과급기용 스러스트 베어링 시일
US20230287806A1 (en) Turbine housing
US11946381B2 (en) Stator support for a fan shaft driven by a reduction gearbox in a turbomachine
US20220106893A1 (en) Shaft Seal System, Turbomachine with Shaft Seal System, and Method of Sealing a Shaft
JPS6316134A (ja) 軸封装置

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20190219

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIC1 Information provided on ipc code assigned before grant

Ipc: F04D 25/06 20060101ALI20190905BHEP

Ipc: F04D 29/10 20060101ALI20190905BHEP

Ipc: F02B 33/40 20060101ALI20190905BHEP

Ipc: F04D 29/28 20060101ALI20190905BHEP

Ipc: F02B 39/10 20060101ALI20190905BHEP

Ipc: F04D 29/056 20060101ALI20190905BHEP

Ipc: F04D 29/12 20060101AFI20190905BHEP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 602017038374

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F02B0039100000

Ipc: F04D0029120000

A4 Supplementary search report drawn up and despatched

Effective date: 20191217

RIC1 Information provided on ipc code assigned before grant

Ipc: F04D 25/06 20060101ALI20191211BHEP

Ipc: F04D 29/10 20060101ALI20191211BHEP

Ipc: F04D 29/056 20060101ALI20191211BHEP

Ipc: F02B 33/40 20060101ALI20191211BHEP

Ipc: F04D 29/28 20060101ALI20191211BHEP

Ipc: F04D 29/12 20060101AFI20191211BHEP

Ipc: F02B 39/10 20060101ALI20191211BHEP

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20201026

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1390149

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210515

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602017038374

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1390149

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210505

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210805

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210805

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210906

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210905

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210806

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20210505

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602017038374

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20220208

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210905

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20220329

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20220331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220329

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220331

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220329

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220329

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220331

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20170329

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210505

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240130

Year of fee payment: 8