EP3696411A1 - Dispositif de compression d'air et procédé de fabrication de dispositif de compression d'air - Google Patents

Dispositif de compression d'air et procédé de fabrication de dispositif de compression d'air Download PDF

Info

Publication number
EP3696411A1
EP3696411A1 EP20156901.9A EP20156901A EP3696411A1 EP 3696411 A1 EP3696411 A1 EP 3696411A1 EP 20156901 A EP20156901 A EP 20156901A EP 3696411 A1 EP3696411 A1 EP 3696411A1
Authority
EP
European Patent Office
Prior art keywords
rotor
fan
compressor
air
compression device
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.)
Granted
Application number
EP20156901.9A
Other languages
German (de)
English (en)
Other versions
EP3696411B1 (fr
Inventor
Masaru Kuromitsu
Genpei TANAKA
Keita Kawabata
Takashi Kuga
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.)
Nabtesco Corp
Original Assignee
Nabtesco Corp
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 Nabtesco Corp filed Critical Nabtesco Corp
Publication of EP3696411A1 publication Critical patent/EP3696411A1/fr
Application granted granted Critical
Publication of EP3696411B1 publication Critical patent/EP3696411B1/fr
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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/066—Cooling by ventilation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B47/00—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps
    • F04B47/14—Counterbalancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/605—Balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight

Definitions

  • the present invention relates to an air compression device and a method for manufacturing the air compression device.
  • JP 2012-062846 A describes an air compressor which is integrated with an electric motor and has a compressor body driven by the electric motor.
  • the air compressor includes a motor, a compressor body that compresses air by reciprocating a piston in a cylinder by the motor, a first fan arranged at a tip of a drive shaft integrated with a rotor of the motor, and a second fan provided in a motor case.
  • the first fan and the second fan are coupled to the drive shaft integrated with the rotor of the motor.
  • the rotor of the motor, the first fan, and the second fan are individually subjected to balance adjustment processing for reducing the unbalance amount.
  • the adjustment processing is performed individually, the total residual unbalance amount increases due to the accumulation of the residual unbalance amount of each member after balance adjustment.
  • the present invention has been made in view of these problems, and an object of the present invention is to provide an air compression device capable of reducing the residual unbalance amount while suppressing an increase in processing man-hours.
  • an air compression device includes: a compressor that compresses air; a motor that drives the compressor; a fan that rotates integrally with a rotor of the motor; an intermediate member that is arranged between the rotor and the fan and that rotates integrally with the rotor; and balance adjusting units that are provided in the intermediate member and are subjected to a process of reducing an unbalance amount in a total rotation of the intermediate member, the rotor, and the fan.
  • Another aspect of the present invention is a method for manufacturing an air compression device.
  • the method includes: integrating a rotor of a motor that drives a compressor that compresses air, a fan that rotates integrally with the rotor, and an intermediate member arranged between the rotor and the fan; and performing a process of reducing an unbalance amount on an intermediate member integrated with the rotor and the fan.
  • the air compression device can be provided which can reduce the residual unbalance amount while suppressing the increase in processing man-hours.
  • FIG. 1 is a system diagram schematically illustrating a configuration of the air compression device 100.
  • Fig. 2 is a schematic view illustrating a state in which the air compression device 100 is installed in the railway vehicle 90.
  • a part of a bearing holder 38 and a multiblade fan 16 is fractured, and a blower fan 28 is shown smaller than an actual ratio.
  • the air compression device 100 of the present embodiment includes a compressor 10, a compressor driving part 14, a multiblade fan 16, a cooler 22, a dehumidifier 24, an air introduction unit 26, a blower fan 28, an air suction part 32, a compressed air delivery part 34, an inverter control device 40, and a housing case 36.
  • the air compression device 100 compresses the air sucked from the air suction part 32 with the compressor 10, cools the air with the cooler 22, dehumidifies the air with the dehumidifier 24, delivers the air out from the compressed air delivery part 34, and supplies the air to the vehicle 90.
  • the compressor driving part 14 drives the compressor 10.
  • the inverter control device 40 drives the motor 12 of the compressor driving part 14.
  • the multiblade fan 16 is driven by the motor 12 to generate an air flow used for cooling by the cooler 22.
  • the air introduction unit 26 introduces compressed air to the motor 12, and the blower fan 28 generates an air flow that cools the compressor 10.
  • the direction along the central axis La of the rotary shaft 10a of the compressor 10 is referred to as "axial direction", and the circumferential direction and the radial direction of the circle centered on the central axis La are respectively “circumferential direction” and "radial direction”.
  • one side (a right side in the drawing) in the axial direction is referred to as an input side
  • the other side (a left side in the drawing) is referred to as a non-input side.
  • the motor 12 is provided on the input side of the compressor 10
  • the compressor 10 is provided on the non-input side of the motor 12.
  • the air suction part 32 is installed in the housing case 36 and functions as a mechanism for sucking air (outside air) compressed by the compressor 10.
  • the air suction part 32 is formed so as to communicate with the compressor 10 through the suction pipe 32b.
  • the air suction part 32 is provided with a suction filter 32a that suppresses the passage of dust such as sand dust when the suction air passes.
  • the suction filter 32a may be a filter using a mesh.
  • the compressed air delivery part 34 functions as a mechanism that delivers the compressed air Ar10d cooled by the cooler 22 described later and dehumidified by the dehumidifier 24.
  • the compressed air delivery part 34 supplies the generated compressed air Ar10d to the compressed air reservoir 92 installed outside the housing case 36.
  • the compressed air delivery part 34 may include a valve mechanism 34d provided in a path that allows the dehumidifier 24 and the compressed air reservoir 92 to communicate with each other.
  • the valve mechanism 34d may be a check valve that allows the compressed air Ar10d to pass toward the compressed air reservoir 92 side and prevent backflow from the compressed air reservoir 92 when the dehumidifier 24 side is equal to or higher than a predetermined pressure.
  • Fig. 3 is a side sectional view schematically illustrating the periphery of the compressor driving part 14 and the multiblade fan 16.
  • Fig. 4 is an enlarged side sectional view illustrating the periphery of the labyrinth portion 12f of the compressor driving part 14.
  • the compressor driving part 14 mainly includes a motor 12 that rotationally drives the compressor 10 and a balance weight 15.
  • the motor 12 includes an output shaft 12a, a rotor 12k, a stator 12s, a casing 12c, and a labyrinth portion 12f.
  • the output shaft 12a of the motor 12 is provided integrally with the rotary shaft 10a of the compressor 10.
  • the rotor 12k includes a magnet 12m having a plurality of magnetic poles in the circumferential direction and is fixed to the outer periphery of the output shaft 12a.
  • the rotor 12k is fixed to an input side of a rotor fixing part 15d of the balance weight 15 described later by a fastener such as a bolt (not illustrated).
  • An adhesive may be used in combination for these fixations.
  • the stator 12s includes a stator core 12j that surrounds the rotor 12k via a magnetic gap and a coil 12g that is wound around the stator core 12j.
  • the outer periphery of the stator 12s is fixed to the inner peripheral surface of the casing 12c.
  • the casing 12c includes a cylindrical portion 12d and a bottom portion 12e, and functions as an outer shell that surrounds the rotor 12k and the stator 12s.
  • the casing 12c has a bottomed cylindrical shape in which the non-input side is opened and the bottom portion 12e is provided on the input side.
  • the bottom portion 12e is provided with an introduction port 12h for taking in air from the air introduction unit 26.
  • the labyrinth portion 12f is provided so as to cover the non-input side of the cylindrical portion 12d, and has a disc shape in this example.
  • the labyrinth portion 12f includes a rotating body portion 12n fixed to the output shaft 12a and a stationary body portion 12p fixed to the cylindrical portion 12d.
  • the stationary body portion 12p is a donut-shaped disc member in which a stationary body side labyrinth forming part 12q is provided on the outer periphery of the non-input side end surface.
  • the stationary body side labyrinth forming part 12q includes a stationary body side concave portion 12t and a stationary body side convex portion 12u.
  • the labyrinth convex portion 15h enters the stationary body side concave portion 12t.
  • the stationary body side convex portion 12u enters a labyrinth concave portion 15g described later.
  • the stationary body side convex portion 12u is an annular wall provided on the inner peripheral side of the stationary body side concave portion 12t.
  • the rotating body portion 12n also serves as the balance weight 15 described later.
  • a labyrinth 12r is provided between the rotating body portion 12n and the stationary body portion 12p.
  • the labyrinth 12r is a maze that combines bended spaces.
  • the labyrinth portion 12f includes the labyrinth 12r to reduce the intrusion of dust into the motor 12.
  • the compressed air Ar10e introduced from the introduction port 12h flows outward from the labyrinth 12r, the dust in the labyrinth 12r is easily discharged outside by this air flow.
  • the motor 12 generates a field magnetic field in the magnetic gap when a drive current is provided to the coil 12g of the stator 12s from an inverter control device 40 (drive circuit) described later.
  • the motor 12 generates a rotational driving force on the rotor 12k and the output shaft 12a due to the field magnetic field and the magnet 12m of the rotor 12k.
  • the rotational driving force of the output shaft 12a drives the multiblade fan 16 and the compressor 10 through the rotary shaft 10a.
  • the bearing that supports the rotary shaft 10a is provided in the bearing holder 38 outside the compressor driving part 14, and is not provided in the compressor driving part 14.
  • Fig. 5 is a perspective view illustrating a periphery of the multiblade fan 16. This drawing illustrates the balance weight 15 integrated with the rotor 12k and the multiblade fan 16.
  • the multiblade fan 16 is arranged between the compressor 10 and the motor 12 in the axial direction.
  • the multiblade fan 16 functions as a fan that rotates integrally with the rotor 12k of the motor 12.
  • the multiblade fan 16 functions as a blower that collects and sends the air flow generated from the central portion toward the outer periphery in a delivery duct 16d.
  • the multiblade fan 16 may be referred to as a sirocco fan.
  • the multiblade fan 16 includes a disc portion 16b and a plurality of blades 16c.
  • the disc portion 16b is a donut-shaped disc member of which the inner peripheral side is fixed to the rotary shaft 10a via a balance weight 15.
  • the disc portion 16b is fixed to a fan fixing part 15c provided on the non-input side end surface of the balance weight 15 with a fastener such as a bolt (not illustrated).
  • An adhesive may be used in combination for these fixations.
  • the plurality of blades 16c extend from the disc portion 16b to the non-input side in the vicinity of the outer periphery of the disc portion 16b.
  • the plurality of blades 16c are arranged at predetermined angles in the circumferential direction.
  • the plurality of blades 16c function as an air flow generation part that generates an air flow toward the outer periphery by rotating.
  • the casing 16e is a cylindrical member that surrounds the disc portion 16b and the plurality of blades 16c.
  • the disc portion 16b is arranged on the non-input side end surface of the motor 12 with an axial gap 16g interposed therebetween.
  • the width W16 of the axial gap 16g may be narrower than the thickness H16 of the disc portion 16b.
  • the blade 16c overlaps a second bearing 13e in the axial direction.
  • the delivery duct 16d is a cylindrical member extending from the casing 16e to the cooler 22.
  • a lower portion 16h of the delivery duct 16d is a substantially rectangular tube-shaped portion extending upward from the upper portion of the casing 16e.
  • An upper portion 16j of the delivery duct 16d is a portion that communicates with the lower portion of the cooler 22 from the upper portion of the lower portion 16h.
  • the upper portion 16j has a substantially quadrangular pyramid shape with a wide upper side.
  • the multiblade fan 16 may overlap with at least a part of a bearing 38j that supports the rotary shaft 10a of the compressor 10 in the axial direction. In this case, the axial length of the air compression device 100 can be shortened compared to the case where the multiblade fan 16 does not overlap the bearing 38j.
  • the balance weight 15 will be described with reference to Figs. 6 and 7 .
  • Fig. 6 is a front view illustrating the periphery of the balance weight 15.
  • Fig. 7 is a rear view illustrating the periphery of the balance weight 15.
  • the balance weight 15 also functions as an intermediate member arranged between the rotor 12k and the multiblade fan 16.
  • the balance weight 15 is a disc-shaped member made of metal such as brass, and also serves as the rotating body portion 12n of the labyrinth portion 12f as described above.
  • the balance weight 15 includes balance adjusting units 15a and 15b, a fan fixing part 15c, a rotor fixing part 15d, a shaft fastening part 15f, and a labyrinth forming part 15e.
  • the fan fixing part 15c is an annular portion in which the multiblade fan 16 is fixed on the non-input side end surface.
  • the rotor fixing part 15d is an annular portion to which the rotor 12k is fixed on the input side end surface, and in this example, has a cylindrical outer shape protruding from the outer periphery to the input side.
  • the shaft fastening part 15f is a through hole into which the output shaft 12a is inserted and fixed.
  • the labyrinth forming part 15e is a portion where the labyrinth concave portion 15g and the labyrinth convex portion 15h are provided in the outer periphery of the input side end surface.
  • the labyrinth concave portion 15g is an annular concave portion formed on the non-input side in the labyrinth forming part 15e.
  • the stationary body side convex portion 12u enters the labyrinth concave portion 15g through a gap.
  • the labyrinth convex portion 15h is a portion that enters the stationary body side concave portion 12t through a gap.
  • the labyrinth convex portion 15h in this example is an annular wall provided so as to surround the outer peripheral side of the labyrinth concave portion 15g.
  • the balance adjusting units 15a and 15b are portions that are subjected to processing for reducing the total unbalance amount of the balance weight 15, the rotor 12k, and the multiblade fan 16. That is, in a state where the multiblade fan 16 and the rotor 12k are fixed and integrated with the balance weight 15, the balance adjusting units 15a and 15b are subjected to balance adjustment for reducing the total unbalance amount.
  • the balance adjusting units 15a and 15b may be provided only on one end surface of the balance weight 15. However, in the present embodiment, the balance adjusting units 15a and 15b are provided on both end surfaces.
  • the balance adjusting units 15a and 15b include a fan side adjusting part 15a provided on the radially inner side from the fan fixing part 15c and a rotor side adjusting part 15b provided on the radially outer side from the rotor fixing part 15d.
  • the balance adjusting unit 15a may be provided on the radially inner side from the air flow generation part of the multiblade fan 16.
  • the balance adjusting unit 15a is provided on the radially inner side from the plurality of blades 16c.
  • the balance adjusting units 15a and 15b in this example are flat annular portions in the radial intermediate region of the balance weight 15.
  • the compressor 10 will be described with reference to Figs. 2 and 8 to 10 .
  • FIG. 8 is a front view schematically illustrating the compressor 10 and the blower fan 28.
  • Fig. 9 illustrates a state where a fixed scroll portion 10j is removed.
  • Fig. 10 illustrates a back space 10g with an orbiting scroll portion 10h removed.
  • the compressor 10 of the present embodiment is a scroll type air compressor which includes a rotary shaft 10a, a body portion 10b, a suction port 10c, a discharge port 10e, an air cooling fin 10f, an orbiting scroll portion 10h, a fixed scroll portion 10j, and a back space 10g.
  • the suction port 10c communicates with the air suction part 32, and compresses the air Ar32 sucked into the pump space 10d from the air suction part 32 through the suction pipe 32b.
  • the valve mechanism 32d is provided between the air suction part 32 and the suction port 10c of the compressor 10. The valve mechanism 32d opens when the compressor 10 is operated and the compressor 10 side becomes negative pressure.
  • the discharge port 10e communicates with the cooler 22, and the compressed air is discharged from the discharge port 10e to the cooler 22.
  • the body portion 10b is a circumferential outer peripheral wall that defines the pump space 10d.
  • the body portion 10b surrounds a fixed scroll 10m and an orbiting scroll 10n in the pump space 10d.
  • the fixed scroll portion 10j includes a fixed disc portion 10k provided with a plurality of air cooling fins 10f on the outside and a fixed scroll 10m fixed inside the fixed disc portion 10k.
  • the discharge port 10e is provided at the center of the fixed disc portion 10k.
  • the orbiting scroll portion 10h includes an orbiting disc portion 10p and an orbiting scroll 10n fixed to the orbiting disc portion 10p.
  • the rotary shaft 10a extending to the input side is fixed at the center of the orbiting disc portion 10p.
  • the back space 10g is provided on the input side of the orbiting disc portion 10p, that is, on the back side of the orbiting scroll portion 10h. Cooling air is introduced from the blower fan 28 into the back space 10g, and the orbiting disc portion 10p and the rotary shaft 10a are forcibly cooled by air.
  • the blower fan 28 will be described later.
  • the orbiting scroll 10n and the fixed scroll 10m are spiral bodies having the same shape.
  • the compressor 10 compresses air when the volume of the compression space is changed by orbiting the orbiting scroll 10n integrally with the rotary shaft 10a with respect to the fixed scroll 10m.
  • the compressor 10 sucks air from the outer periphery and performs compression toward the center.
  • the compressor 10 may be an oil-free type.
  • the blower fan 28 will be described with reference to Figs. 2 and 8 to 10 .
  • the blower fan 28 is a blower mechanism that delivers cooling air (hereinafter referred to as a cooling air Ar28) to the compressor 10.
  • the blower fan 28 supplies the cooling air Ar28 to the back space 10g on the back side of the orbiting scroll portion 10h to mainly cool the orbiting scroll portion 10h.
  • the blower fan 28 of the present embodiment is an electric axial flow blower having a propeller 28b. As illustrated in Fig. 10 , the blower fan 28 is arranged on the side of the compressor 10 so that the rotation axis L28 of the propeller 28b is orthogonal to the rotary shaft 10a of the compressor 10. An outside air filter 28a formed of a wire mesh or the like is provided on the upstream side of the blower fan 28. A blower duct 28g for guiding the cooling air Ar28 to the central portion of the orbiting scroll portion 10h is provided on the downstream side of the blower fan 28.
  • the blower duct 28g has a substantially quadrangular frustum shape of which the cross-sectional area decreases toward the compressor 10.
  • the cooling air Ar28 is throttled along the inner surface of the blower duct 28g and cools the central portion of the orbiting scroll portion 10h intensively. Since the temperature at the central portion of the orbiting scroll portion 10h is the highest, the cooling effect can be enhanced by intensively cooling the center portion.
  • An exhaust duct 28h is provided on the downstream side of the back space 10g. In this example, the upstream side of the exhaust duct 28h faces the blower duct 28g, and the downstream side is directed downward.
  • the cooler 22 will be described with reference to Figs. 2 , 3 , 11 , and 12 .
  • the cooler 22 cools the compressed air supplied from the compressor 10 at a high temperature (for example, 200°C to 250°C) to a temperature slightly higher than the room temperature (for example, 40°C to 50°C) and supplies the compressed air to the dehumidifier 24.
  • the cooler 22 may be configured as a single cooler. However, in the present embodiment, a plurality of coolers are connected in series.
  • the cooler 22 of the present embodiment includes a first cooler 18 that primarily cools the compressed air from the compressor 10 and a second cooler 20 that secondarily cools the compressed air cooled by the first cooler 18.
  • the first cooler 18 and the second cooler 20 have bent pipes 18p and 20p and pipe housing parts 18c and 20c for housing the pipes, respectively.
  • the bent pipes 18p and 20p meander to have a plurality of bent portions, and compressed air flows from one end of the pipe toward the other end.
  • the pipe housing parts 18c and 20c have vertically thin rectangular tube-shaped outer walls, and function as a wind tunnel for allowing a cooling air to flow vertically.
  • Wire mesh portions 18m and 20m for supporting the bent pipes 18p and 20p are fixed to the lower portions of the pipe housing parts 18c and 20c.
  • the upper surface of the pipe housing part 20c is opened, and the wire mesh portion 20n is fixed to the upper surface of the pipe housing part 18c.
  • the pipe housing parts 18c and 20c have a configuration in which the air flow easily passes vertically.
  • the first introduction part 18b provided at one end of the bent pipe 18p protrudes outside from the side wall of the pipe housing part 18c of the first cooler 18.
  • the first introduction part 18b communicates with the discharge port 10e of the compressor 10.
  • a first lead-out part 18e provided at the other end of the bent pipe 18p protrudes outside from the side wall of the pipe housing part 18c of the first cooler 18.
  • the first lead-out part 18e communicates with a second introduction part 20b.
  • the second introduction part 20b provided at one end of the bent pipe 20p protrudes outside from the bottom of the pipe housing part 20c of the second cooler 20.
  • the second introduction part 20b communicates with the first lead-out part 18e.
  • a second lead-out part 20e provided at the other end of the bent pipe 20p protrudes outside from the side wall of the pipe housing part 20c of the second cooler 20.
  • the second lead-out part 20e communicates with the dehumidifier 24.
  • the pipe housing part 18c is arranged on the upper side of the pipe housing part 20c.
  • the air flow Ar16a delivered from the multiblade fan 16 is supplied to the lower surface of the pipe housing part 20c through the duct 16d.
  • the air flow Ar16a flows through the gap of the wire mesh portion 20m and the gap of the bent pipe 20p, and is discharged from the upper surface of the pipe housing part 20c. As the air flow Ar16a passes through the outer peripheral surface of the bent pipe 20p, the compressed air of the bent pipe 20p is cooled.
  • the air flow Ar16b discharged from the pipe housing part 20c is supplied to the lower surface of the pipe housing part 18c.
  • the air flow Ar16b flows through the gap of the wire mesh portion 18m, the gap of the bent pipe 18p, and the gap of the wire mesh portion 20n, and is discharged from the upper surface of the pipe housing part 18c.
  • the compressed air Ar20c of the bent pipe 18p is cooled by the air flow Ar16b passing through the outer peripheral surface of the bent pipe 18p.
  • the air discharged from the pipe housing part 18c is diffused into the atmosphere.
  • the air flow Ar16a delivered from the multiblade fan 16 is supplied to the second cooler 20 first and is used for secondary cooling of the compressed air after the primary cooling.
  • the air flow Ar16b discharged from the second cooler 20 is supplied to the first cooler 18 and is used for primary cooling of the compressed air.
  • the temperature difference between the compressed air and the cooling air in the secondary cooling becomes large, so that the cooling efficiency can be increased.
  • the cooler 22 may be arranged anywhere as long as a desired cooling effect is obtained.
  • the cooler 22 of the present embodiment is arranged above the center of the air compression device 100 in the vertical direction.
  • the cooler 22 is arranged between the multiblade fan 16 and the floor of the railway vehicle 90.
  • the dehumidifier 24 is provided in a path that allows the cooler 22 and the compressed air delivery part 34 to communicate with each other.
  • the dehumidifier 24 is a hollow fiber membrane type dehumidifier that dehumidifies the cooled compressed air Ar10c.
  • the dehumidifier 24 may include a filter element that includes a desiccant.
  • final dehumidification is performed on the compressed air Ar10d delivered from the compressed air delivery part 34.
  • the compressed air Ar10d is delivered to the compressed air reservoir 92 via the compressed air delivery part 34.
  • the air introduction unit 26 introduces the compressed air Ar10d dehumidified by the dehumidifier 24 into the casing 12c of the motor 12.
  • the air introduction unit 26 delivers the compressed air Ar10d to the introduction port 12h provided in the bottom portion 12e.
  • the air introduction unit 26 is provided with a valve mechanism 26d on a path for guiding the compressed air Ar10d from the dehumidifier 24 to the casing 12c.
  • the valve mechanism 26d may be a check valve that allows the compressed air Ar10d to pass to the casing 12c side and block backflow from the casing 12c to the dehumidifier 24 when the dehumidifier 24 side is equal to or higher than a predetermined pressure.
  • the bearing holder 38 will be described with reference to Figs. 2 and 3 .
  • the bearing holder 38 is a portion that is provided on the input side of the compressor 10 and supports bearings 38h and 38j that rotatably support the rotary shaft 10a.
  • the bearing holder 38 has a hollow cylindrical portion 38a and a plurality of fins 38f extending radially outward from the cylindrical portion 38a.
  • the fin 38f has a triangular shape of which radially outer end extends radially outward as it approaches the compressor 10 in the axial direction. In this example, four fins 38f are provided at 90° intervals in the circumferential direction on the outer periphery of the cylindrical portion 38a.
  • the bearing holder 38 also has a function of dissipating heat generated in the compressor 10 to suppress an excessive temperature rise of the bearings 38h and 38j.
  • the bearings 38h and 38j include a first bearing 38h arranged near the compressor 10 and a second bearing 38j arranged near the motor 12.
  • the first and second bearings 38h and 38j rotatably support the rotary shaft 10a.
  • the first and second bearings 38h and 38j are held in the hollow portion of the cylindrical portion 38a while being separated in the axial direction.
  • a part of the bearing holder 38 enters the inner peripheral portion of the multiblade fan 16 in the axial direction. Further, at least a part of the bearing 38j that supports the rotary shaft 10a of the compressor 10 overlaps the multiblade fan 16 in the axial direction. In this case, the axial space can be used more effectively than the case of no overlap.
  • the inverter control device 40 will be described with reference to Figs. 1 and 2 .
  • the inverter control device 40 functions as an inverter power supply device for driving and controlling the motor 12.
  • the inverter control device 40 is protected from dust or rainwater by being stored in the storage box 42.
  • the storage box 42 may be made of metal.
  • the inverter control device 40 includes electronic components (all not illustrated) such as a switching power module and a smoothing capacitor for supplying a drive current to the coil 12g.
  • the storage box 42 is provided on the path of the suction air Ar32 between the air suction part 32 and the suction port 10c of the compressor 10.
  • the storage box 42 is provided between the air suction part 32 and the valve mechanism 32d. That is, part or all of the suction air Ar32 passes through the storage box 42 and is delivered to the compressor 10 side.
  • the suction air Ar32 passes through the storage box 42, the inside of the box is forcibly ventilated, and the electronic components of the inverter control device 40 are air-cooled. In this case, the rise of the inner temperature of the storage box 42 is suppressed, and the lifetime of the electronic component is extended.
  • the housing case 36 houses the compressor 10, the compressor driving part 14, the multiblade fan 16, the cooler 22, the dehumidifier 24, the air introduction unit 26, the blower fan 28, the air suction part 32, the compressed air delivery part 34, and the storage box 42 of the inverter control device 40.
  • An air compression device 100 includes: a compressor 10 that compresses air; a motor 12 that drives the compressor 10; a multiblade fan 16 that rotates integrally with a rotor 12k of the motor 12; a balance weight 15 that is arranged between the rotor 12k and the multiblade fan 16 and that rotates integrally with the rotor 12k; and balance adjusting units 15a and 15b that are provided in the balance weight 15 and are subjected to a process of reducing an unbalance amount in a total rotation of the balance weight 15, the rotor 12k, and the multiblade fan 16.
  • the balance weight 15 may include the fan fixing part 15c to which the multiblade fan 16 is fixed and the rotor fixing part 15d to which the rotor 12k is fixed.
  • the rotor 12k and the multiblade fan 16 can be easily integrated with the balance weight 15.
  • the number of parts is reduced as compared with the case where separate members for fixing the multiblade fan 16 and the rotor 12k are provided, which is advantageous in terms of cost and assembly man-hours.
  • reliability is improved by reducing the number of fastening portions.
  • the balance adjusting units 15a and 15b may include the rotor side adjusting part 15b provided on the radially outer side from the rotor fixing part 15d. In this case, since the rotor side adjusting part 15b is positioned outside the rotor fixing part 15d, the rotor 12k does not become an obstacle during balance adjustment, and adjustment work is facilitated.
  • the balance adjusting units 15a and 15b may include the fan side adjusting part 15a provided on the radially inner side from the fan fixing part 15c.
  • the fan side adjusting part 15a since the fan side adjusting part 15a is positioned on the inner side of the fan fixing part 15c, the multiblade fan 16 does not become an obstacle during balance adjustment, and the adjustment work is facilitated.
  • the fan side adjusting part 15a may be provided on the radially inner side from the plurality of blades 16c. In this case, since the fan side adjusting part 15a is positioned inside the plurality of blades 16c, the blade 16c does not become an obstacle during balance adjustment, and the adjustment work is facilitated.
  • the multiblade fan 16 may be arranged between the compressor 10 and the motor 12 in the axial direction. In this case, since the multiblade fan 16 and the compressor 10 can be connected to the output shaft 12a protruding to one side of the motor 12, the other side of the casing 12c can be closed, so as to reduce the intrusion of dust to the motor 12.
  • the multiblade fan 16 may overlap at least a part of the bearing that supports the rotation of the compressor 10 when viewed in the radial direction.
  • the axial length of the air compression device 100 can be shortened corresponding to the overlap.
  • the multiblade fan 16 may generate an air flow for cooling the air compressed by the compressor 10. In this case, the compressed air from the compressor 10 can be cooled.
  • the compressor 10 is a scroll type compressor having the orbiting scroll 10n, and the rotor 12k and the orbiting scroll 10n may be coupled to a single rotary shaft. In this case, the air compression device with less vibration can be provided with the low unbalance of the rotor 12k and the multiblade fan 16.
  • the air compression device 100 may be a railway vehicle air compression device arranged below the floor of the railway vehicle 90.
  • the compressed air can be supplied to the railway vehicle 90, and the longitudinal length of the device is shortened so as to provide room in a space under the floor of the railway vehicle 90.
  • the manufacturing method S100 of the present embodiment includes: step S102 of integrating a rotor 12k of a motor 12 that drives a compressor 10 that compresses air, a multiblade fan 16 that rotates integrally with the rotor 12k, and a balance weight 15 arranged between the rotor 12k and the multiblade fan 16; and step S104 of performing a process of reducing an unbalance amount on the balance weight 15 integrated with the rotor and the multiblade fan 16.
  • the rotor 12k may be fixed to the input side of the rotor fixing part 15d of the balance weight 15 by a fastener such as a bolt.
  • the multiblade fan 16 may be fixed to the fan fixing part 15c of the non-input side end surface of the balance weight 15 by a fastener such as a bolt.
  • An adhesive may be applied to these fixing parts.
  • the process of reducing the unbalance amount in step S104 is performed using the balance weight 15 integrated with the rotor 12k and the multiblade fan 16 as a workpiece.
  • the unbalance amount of the workpiece is specified by the balance inspection device, and mass is added to or deleted from the balance adjusting units 15a and 15b according to the specification result.
  • the balance can be adjusted by forming concave portions in the balance adjusting units 15a and 15b with a drill or the like or by attaching a mass body to the balance adjusting units 15a and 15b.
  • the present embodiment compared with the case where the rotor 12k, the multiblade fan 16 and the balance weight 15 are individually adjusted, balance adjustment with high accuracy is possible, and the total unbalance amount can be reduced. Further, since the man-hours for individual adjustment can be saved, the total man-hours for adjustment are reduced, which is advantageous in terms of cost.
  • FIG. 14 is a front view illustrating the periphery of the compressor 10 and corresponds to Fig. 8 .
  • the compressor 10 since the outer periphery has a negative pressure, it is easy to suck dust due to a pressure difference between the outside and the inside.
  • the compressor 10 is provided with a face seal (not illustrated) that seals the outer peripheral surface.
  • the face seal has a gap called a joint portion, and dust enters through this gap.
  • the supercharger 210 is provided at the suction port 10c of the compressor 10.
  • the supercharger 210 is not particularly limited as long as the supercharger can increase the internal pressure of the compressor 10.
  • the supercharger 210 of this modification has an impeller 210b that is rotated by a motor 210m.
  • the supercharger 210 pressurizes the upstream air, makes the downstream air equal to or higher than the atmospheric pressure, and supplies the air to the suction port 10c of the compressor 10.
  • the supercharger 210 is provided in the path between the valve mechanism 32d and the suction port 10c.
  • the output shaft 12a of the motor 12 is integrated with the rotary shaft 10a of the compressor 10, but the invention is not limited to this.
  • the output shaft of the motor may be separated from the rotary shaft of the compressor and connected by a coupling or the like.
  • valve mechanism 26d is a check valve, but the invention is not limited to this.
  • the valve mechanism 26d may be a secondary pressure adjusting valve (pressure reducing valve) capable of adjusting the pressure on the secondary side.
  • the motor 12 is a surface magnet type DC brushless motor, but the invention is not limited to this.
  • the motor may be a magnet embedded motor.
  • the compressor 10 is a scroll type, but the invention is not limited to this.
  • the compressor may be any compressor as long as the compressor can generate compressed air.
  • the compressor may be another type of air compressor such as a screw type or a reciprocating type.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)
EP20156901.9A 2019-02-12 2020-02-12 Dispositif de compression d'air et procédé de fabrication de dispositif de compression d'air Active EP3696411B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2019023061A JP7403955B2 (ja) 2019-02-12 2019-02-12 空気圧縮装置、空気圧縮装置の製造方法

Publications (2)

Publication Number Publication Date
EP3696411A1 true EP3696411A1 (fr) 2020-08-19
EP3696411B1 EP3696411B1 (fr) 2023-05-03

Family

ID=69581879

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20156901.9A Active EP3696411B1 (fr) 2019-02-12 2020-02-12 Dispositif de compression d'air et procédé de fabrication de dispositif de compression d'air

Country Status (3)

Country Link
EP (1) EP3696411B1 (fr)
JP (1) JP7403955B2 (fr)
CN (1) CN111550409A (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0335362A1 (fr) * 1988-03-30 1989-10-04 Dürr-Dental GmbH & Co. KG Compresseur
EP1275849A2 (fr) * 2001-07-10 2003-01-15 Kabushiki Kaisha Toyota Jidoshokki Compresseur avec équilibrage des forces
JP2003106272A (ja) * 2001-09-28 2003-04-09 Fujitsu General Ltd スクロール圧縮機
JP2012062846A (ja) 2010-09-17 2012-03-29 Hitachi Industrial Equipment Systems Co Ltd モータ及び圧縮機
US20150200579A1 (en) * 2014-01-10 2015-07-16 Samsung Electro-Mechanics Co., Ltd. Motor rotor and method for manufacturing the same

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2490329Y (zh) * 2001-07-17 2002-05-08 鞍山腾飞空压机有限公司 一种直联便携式往复活塞全无油润滑空气压缩机
JP4855788B2 (ja) * 2006-01-31 2012-01-18 株式会社日立産機システム 往復動圧縮機
CN101737296A (zh) * 2010-01-08 2010-06-16 浙江鸿友压缩机制造有限公司 低噪声结构无油空气压缩机
JP5606181B2 (ja) * 2010-06-30 2014-10-15 株式会社日立産機システム 圧縮機
CN201874832U (zh) * 2010-11-17 2011-06-22 广东美芝制冷设备有限公司 旋转式压缩机的排气结构
CN201851363U (zh) * 2010-11-19 2011-06-01 南车资阳机车有限公司 一种大排量螺杆空气压缩机组
US20140124231A1 (en) * 2012-11-06 2014-05-08 Milwaukee Electric Tool Corporation Electric motor for a power tool
JP5933042B2 (ja) * 2013-01-16 2016-06-08 三菱電機株式会社 密閉形圧縮機及びこの密閉形圧縮機を備えた蒸気圧縮式冷凍サイクル装置
JP6425230B2 (ja) * 2016-01-15 2018-11-21 ミネベアミツミ株式会社 ファン装置及びそのファン装置の製造方法
CN107435635A (zh) * 2017-08-31 2017-12-05 广东美芝制冷设备有限公司 压缩机和具有其的制冷装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0335362A1 (fr) * 1988-03-30 1989-10-04 Dürr-Dental GmbH & Co. KG Compresseur
EP1275849A2 (fr) * 2001-07-10 2003-01-15 Kabushiki Kaisha Toyota Jidoshokki Compresseur avec équilibrage des forces
JP2003106272A (ja) * 2001-09-28 2003-04-09 Fujitsu General Ltd スクロール圧縮機
JP2012062846A (ja) 2010-09-17 2012-03-29 Hitachi Industrial Equipment Systems Co Ltd モータ及び圧縮機
US20150200579A1 (en) * 2014-01-10 2015-07-16 Samsung Electro-Mechanics Co., Ltd. Motor rotor and method for manufacturing the same

Also Published As

Publication number Publication date
JP7403955B2 (ja) 2023-12-25
CN111550409A (zh) 2020-08-18
EP3696411B1 (fr) 2023-05-03
JP2020133403A (ja) 2020-08-31

Similar Documents

Publication Publication Date Title
EP3570417A1 (fr) Moteur de ventilateur
KR20010023891A (ko) 내부 냉각 기류를 이용하는 모터-구동 원심 에어 컴프레서
JP6931774B2 (ja) 温度調和システム、車両
EP2853748A1 (fr) Pompe à vide
KR102552016B1 (ko) 모터용 로터 조립체
JP6678302B2 (ja) 温度調和ユニット、温度調和システム、車両
CN109026684A (zh) 一种双级涡旋空气压缩机
EP3696411A1 (fr) Dispositif de compression d'air et procédé de fabrication de dispositif de compression d'air
JP2020070953A (ja) 冷却システム
EP3696415A1 (fr) Dispositif de compression d'air et procédé de prévention de poussière pour moteur
CN109477486B (zh) 电动机集成型流体机械
JP2004274800A (ja) 電動モータの冷却機構
EP3696421A1 (fr) Dispositif de compression d'air
CN107614883B (zh) 离心式送风机
JP2015081596A (ja) 送風装置
EP3696409A1 (fr) Dispositif de compression d'air
JP5389191B2 (ja) 送風機及びこの送風機を搭載した空気調和装置
US20200191159A1 (en) Electric compressor
JP2016044868A (ja) 室外機及びこの室外機を備えた空気調和機
JP2009257110A (ja) パッケージ型空冷式スクリュー圧縮機
CN108964314A (zh) 一种散热效果好的横向电机
JP7153834B2 (ja) 温度調和ユニット
CN209800255U (zh) 一种同轴风扇无油涡旋压缩机
JP2007023958A (ja) ベーンロータリ型空気ポンプ
JP2023069205A (ja) 電動圧縮機

Legal Events

Date Code Title Description
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: 20200212

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

RBV Designated contracting states (corrected)

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

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: 20221129

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: DE

Ref legal event code: R096

Ref document number: 602020010228

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1564807

Country of ref document: AT

Kind code of ref document: T

Effective date: 20230515

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230413

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20230503

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1564807

Country of ref document: AT

Kind code of ref document: T

Effective date: 20230503

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

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: 20230503

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: 20230904

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: 20230803

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: 20230503

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: 20230503

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: 20230503

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

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: 20230503

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: 20230503

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: 20230503

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: 20230503

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: 20230903

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: 20230503

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: 20230804

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: 20230503

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: 20230503

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

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: 20230503

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: 20230503

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: 20230503

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: 20230503

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: 20230503

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: 20230503

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602020010228

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: 20240206

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

Ref country code: DE

Payment date: 20240219

Year of fee payment: 5

Ref country code: GB

Payment date: 20240219

Year of fee payment: 5

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

Ref country code: SI

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: 20230503

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

Ref country code: SI

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: 20230503

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: 20230503

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

Ref country code: FR

Payment date: 20240222

Year of fee payment: 5