WO2024106362A1 - スラスト受機構 - Google Patents

スラスト受機構 Download PDF

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Publication number
WO2024106362A1
WO2024106362A1 PCT/JP2023/040690 JP2023040690W WO2024106362A1 WO 2024106362 A1 WO2024106362 A1 WO 2024106362A1 JP 2023040690 W JP2023040690 W JP 2023040690W WO 2024106362 A1 WO2024106362 A1 WO 2024106362A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure chamber
fluid
scroll
receiving mechanism
recess
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.)
Ceased
Application number
PCT/JP2023/040690
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
啓志 鈴木
雄一郎 徳永
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.)
Eagle Industry Co Ltd
Original Assignee
Eagle Industry Co 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 Eagle Industry Co Ltd filed Critical Eagle Industry Co Ltd
Priority to KR1020257006467A priority Critical patent/KR20250041053A/ko
Priority to EP23891509.4A priority patent/EP4621235A1/en
Priority to JP2024558843A priority patent/JPWO2024106362A1/ja
Priority to US19/106,562 priority patent/US20260022700A1/en
Priority to CN202380062022.8A priority patent/CN119790228A/zh
Publication of WO2024106362A1 publication Critical patent/WO2024106362A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • 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
    • F04C29/0028—Internal leakage control
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C2240/40—Electric motor
    • 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
    • F04C2240/50—Bearings

Definitions

  • the scroll compressor shown in Patent Document 1 has a thrust bearing disposed on the back side of the movable scroll, and a ring-shaped plate is disposed on this thrust bearing.
  • a plurality of spiral groove mechanisms are formed independently in the circumferential direction on the surface of the ring-shaped plate facing the movable scroll.
  • Each spiral groove mechanism has a plurality of grooves arranged in a substantially radial pattern toward the land at the center of the spiral mechanism.
  • each groove extends radially from the land at an angle in the counterclockwise direction, with one end on the land side tapering and the other end opposite the land being wider than the one end.
  • the movable scroll moves from the other end of the groove to one end during eccentric rotation. This allows the fluid on the outer or inner diameter side of the ring-shaped plate to be drawn into the groove, generating dynamic pressure near one end of the groove. This increases slidability by forming a fluid film while floating the sliding surfaces between the movable scroll and the ring-shaped plate, and also presses the movable scroll against the fixed scroll, reducing refrigerant leakage from the axial gap between the two scrolls.
  • the present invention was made with an eye on these problems, and aims to provide a thrust receiving mechanism that makes it difficult for fluid in the high-pressure space to leak into the low-pressure space.
  • the recess may be in communication with the low pressure side. This allows the fluid in the recesses to be prevented from drying up, and stable sliding properties can be achieved.
  • FIG. 4 is a schematic diagram showing a sliding state between one dynamic pressure generating portion and a side seal in the state shown in FIG. 4 is a schematic diagram showing a sliding state between one dynamic pressure generating portion and a side seal in the state shown in FIG.
  • FIG. 11 is a schematic diagram showing a thrust plate according to a second embodiment of the present invention.
  • the thrust receiving mechanism of the present invention is applied to a rotary machine including an eccentric mechanism, for example, a scroll compressor C that sucks in, compresses, and discharges a refrigerant as a fluid used in air conditioning systems of automobiles, etc.
  • the refrigerant is a gas mixed with mist-like lubricating oil.
  • a discharge communication passage 13 is formed in the cover 12, which connects the refrigerant circuit (not shown) with the high pressure chamber 30. Also, a part of a back pressure communication passage 14 that connects the high pressure chamber 30 with the back pressure chamber 50 is formed in the cover 12 by branching off from the discharge communication passage 13.
  • the discharge communication passage 13 is provided with an oil separator 6 that separates lubricating oil from the refrigerant.
  • the inner casing 3 is fixed with its axial end abutting against the end plate 41a of the fixed scroll 41 that constitutes the scroll compression mechanism 4.
  • a suction communication passage 15 that penetrates radially is formed in the side wall of the inner casing 3.
  • the low pressure chamber 20 is formed from the outside of the inner casing 3 to the inside of the inner casing 3 via the suction communication passage 15. The refrigerant supplied to the inside of the inner casing 3 through the suction communication passage 15 is sucked into the scroll compression mechanism 4.
  • the scroll compression mechanism 4 is mainly composed of a fixed scroll 41 that is fixed in a sealed manner to the cover 12, and a movable scroll 42 that is housed inside the inner casing 3.
  • the fixed scroll 41 is made of metal and has a spiral wrap 41b that protrudes from the surface of the disk-shaped end plate 41a, i.e., the end plate 41a, towards the movable scroll 42.
  • the fixed scroll 41 also has a recess 41c formed on the back surface of the end plate 41a, i.e., the inner diameter side of the end face of the end plate 41a that abuts against the cover 12, which is recessed in the opposite direction to the cover 12, and the high-pressure chamber 30 is defined by this recess 41c and the cover 12.
  • the movable scroll 42 is made of metal and has a spiral wrap 42b that protrudes from the surface of a disk-shaped end plate 42a, i.e., the end plate 42a, towards the fixed scroll 41.
  • the movable scroll 42 also has a boss 42c that protrudes from the center of the back surface of the end plate 42a.
  • An eccentric portion 2a formed on the rotating shaft 2 is inserted into the boss 42c so as to be rotatable relative to the boss 42c.
  • the eccentric portion 2a of the rotating shaft 2 and the counterweight portion 2b that protrudes radially outward from the rotating shaft 2 form an eccentric mechanism that rotates the rotating shaft 2 eccentrically.
  • the eccentric portion 2a rotates eccentrically, and the movable scroll 42 slides relative to the fixed scroll 41 while maintaining its position with the eccentric rotation.
  • the movable scroll 42 rotates eccentrically relative to the fixed scroll 41, and with this rotation, the contact position of the wraps 41b, 42b moves sequentially in the direction of rotation, and the compression chamber 40 formed between the wraps 41b, 42b gradually shrinks as it moves toward the center.
  • the side seal 7 is made of resin, has a rectangular cross section and a circular ring shape when viewed in the axial direction, and is fixed to the back surface of the end plate 42a of the movable scroll 42.
  • the side seal 7 is formed with a sliding surface 7a that abuts against a sliding surface 8a (see FIG. 1) formed on the thrust plate 8.
  • This sliding surface 7a is flat and constitutes the rear sliding surface of the movable scroll 42.
  • the thrust plate 8 is made of metal and has a circular ring shape.
  • the thrust plate 8 is composed of a plurality of dynamic pressure generating portions 81 (16 in this embodiment) and a plurality of connecting portions 82 (16 in this embodiment).
  • the dynamic pressure generating portions 81 that are adjacent in the circumferential direction are connected by connecting portions 82.
  • the connecting portions 82 have the same thickness as the base portions 83 of the dynamic pressure generating portions 81, and have a smaller radial width than the base portions 83.
  • the dynamic pressure generating portions 81 bulge outwardly toward the inner diameter side and the outer diameter side of the thrust plate 8 more than the connecting portions 82.
  • the dynamic pressure generating portions 81 and the connecting portions 82 form steps on the inner diameter side and the outer diameter side, respectively.
  • steps between the dynamic pressure generating portions 81 and the connecting portions 82 will be simply referred to as "steps between the dynamic pressure generating portions 81 and the connecting portions 82."
  • the dynamic pressure generating section 81 comprises a base 83, a recess 84 as a buffer space, a first group of inclined grooves 85 as first grooves, and a second group of inclined grooves 86 as second grooves.
  • the recess 84, the first group of inclined grooves 85, and the second group of inclined grooves 86 are small in size, they are omitted from illustration in FIG. 1 for ease of explanation.
  • the recess 84 is a bottomed hole, for ease of explanation, a dot is added to the recess 84 in the enlarged portion of FIG. 2.
  • the base 83 has a circular shape when viewed in the axial direction.
  • the recess 84 is formed in the center of the base 83, that is, between the inner diameter end and the outer diameter end of the thrust plate 8, and opens toward the sliding surface 8a.
  • the recess 84 is a bottomed recess that is circular when viewed in the axial direction.
  • the first inclined groove group 85 is provided on the sliding surface 8a side of the base 83, closer to the low pressure chamber 20 than the recess 84.
  • the first inclined groove group 85 is composed of a plurality of first inclined grooves 851 (eight in this embodiment).
  • the first inclined groove 851 extends from one end 851a on the low pressure chamber 20 side to the other end 851b on the back pressure chamber 50 side while inclining toward one circumferential side (counterclockwise in FIG. 2 in this embodiment).
  • the one end 851a is connected to the low pressure chamber 20, and the other end 851b is a closed end.
  • the other end 851b of the first inclined groove 851 and the recess 84 are partitioned by a land.
  • the second inclined groove group 86 is provided on the sliding surface 8a side of the base 83, closer to the back pressure chamber 50 than the recess 84.
  • the second inclined groove group 86 is composed of a plurality of second inclined grooves 861 (eight in this embodiment).
  • the second inclined groove 861 extends from one end 861a on the low pressure chamber 20 side to the other end 861b on the back pressure chamber 50 side, inclining toward one circumferential side (counterclockwise in FIG. 2 in this embodiment).
  • One end 861a is connected to the recess 84, and the other end 861b is a closed end.
  • the other end 861b of the second inclined groove 861 is partitioned from the back pressure chamber 50 and the second inclined groove 861 by a land. That is, each second inclined groove 861 is not connected to the back pressure chamber 50.
  • the thrust plate 8 is fitted into the installation groove 3b provided in the inner casing 3.
  • the inner wall that constitutes the installation groove 3b has a shape that is slightly larger than and similar to the outer shape of the thrust plate 8, and the steps of the dynamic pressure generating part 81 and the connecting part 82 engage with the inner wall, restricting the circumferential rotation of the thrust plate 8.
  • a seal ring 43 (see Figure 1) is fixed to the back surface of the thrust plate 8.
  • the seal ring 43 abuts against the bottom surface of the installation groove 3b of the inner casing 3. This allows the thrust plate 8 to function as a thrust bearing mechanism that receives the axial load of the movable scroll 42 via the side seal 7.
  • the side seal 7 and the seal ring 43 divide the inside of the inner casing 3 into a low pressure chamber 20 formed on the outer diameter side of the movable scroll 42 and a back pressure chamber 50 formed on the back side of the movable scroll 42.
  • the back pressure chamber 50 is formed as an enclosed space by sealing between the rotating shaft 2 inserted into the through hole 3a by a seal ring 44 fixed to the inner circumference of the through hole 3a provided in the center of the inner casing 3.
  • the inner casing 3 is provided with a pressure relief hole 16 that penetrates radially and connects the low pressure chamber 20 and the back pressure chamber 50, and a pressure adjustment valve 45 is provided in the pressure relief hole 16. The pressure adjustment valve 45 opens when the pressure in the back pressure chamber 50 exceeds a set value.
  • the boss 42c of the movable scroll 42 is inserted into the central through hole 8b of the thrust plate 8.
  • the through hole 8b is formed with a diameter large enough to allow eccentric rotation by the eccentric portion 2a of the rotating shaft 2 inserted into the boss 42c.
  • the sliding surface 7a of the side seal 7 is able to slide relative to the sliding surface 8a of the thrust plate 8 with eccentric rotation due to the eccentric rotation of the rotating shaft 2 (see FIG. 3).
  • Fig. 3(a) to (d) show the states where the boss 42c has rotated 90 degrees, 180 degrees, and 270 degrees, respectively, with Fig. 3(a) as the reference in the counterclockwise direction, among the rotation trajectory indicated by the black arrow of the boss 42c when viewed from the fixed scroll 41 side.
  • the sliding area between the sliding surface 7a of the side seal 7 and the sliding surface 8a of the thrust plate 8 is shown by dots.
  • the eccentric portion 2a of the rotating shaft 2 that is inserted into the boss 42c is shown, and the counterweight portion 2b and other parts that make up the eccentric mechanism are not shown.
  • the thrust plate 8 has a sliding surface 8a that slides relative to the sliding surface 7a of the eccentrically rotating side seal 7.
  • an elastic member 9 (see FIG. 1) is inserted between the side seal 7 and the scroll compression mechanism 4, more specifically, between the side seal 7 and the movable scroll 42, and absorbs the difference in axial position in the circumferential phase due to the dynamic pressure generated between the side seal 7 and the thrust plate 8, in other words, prevents the movable scroll 42 from tilting.
  • the elastic member 9 may be a deformable material such as an O-ring, or a deformable shape like a spring.
  • Figures 4 and 5 the sliding state between one dynamic pressure generating portion 81A located at 12 o'clock on the thrust plate 8 in Figure 3 and the side seal 7 will be described as an example.
  • Figure 4 shows the state when the side seal 7 moves from the state in Figure 3(a) to the state in Figure 3(b) relative to one dynamic pressure generating portion 81A.
  • Figure 5 shows the state when the side seal 7 moves from the state in Figure 3(c) to the state in Figure 3(d) relative to one dynamic pressure generating portion 81A.
  • the side seal 7 overlaps with the first inclined groove group 85 in one dynamic pressure generating portion 81A in the axial direction. At this time, the side seal 7 slides counterclockwise relative to the dynamic pressure generating portion 81A.
  • the fluid F1 that flows out from the other end 851b between the sliding surfaces 7a, 8a moves toward the back pressure chamber 50.
  • the fluid F2 in the back pressure chamber 50 is pushed back toward the back pressure chamber 50, making it difficult for it to flow between the sliding surfaces 7a, 8a (see the white arrow in Figure 4).
  • a portion of the fluid F1 and a portion of the fluid F2 are stored in the recess 84.
  • the side seal 7 overlaps with the second inclined groove group 86 in one dynamic pressure generating portion 81A in the axial direction. At this time, the side seal 7 slides counterclockwise relative to the dynamic pressure generating portion 81A.
  • each second inclined groove 861 of the second inclined groove group 86 moves from one end 861a to the other end 861b (see the black arrow in Figure 5).
  • the recess 84 gradually becomes disconnected from the back pressure chamber 50 and gradually becomes connected to the low pressure chamber 20, so that the fluid supplied from the recess 84 to the second inclined groove 861 gradually becomes more fluid F1 from the low pressure chamber 20, and in the state shown in FIG. 5, almost all of the fluid F1 is being supplied.
  • the fluid F1 that flows out from the other end 861b between the sliding surfaces 7a and 8a moves toward the back pressure chamber 50.
  • the fluid F2 in the back pressure chamber 50 is pushed back toward the back pressure chamber 50, making it difficult for it to flow between the sliding surfaces 7a and 8a (see the white arrow in Figure 5).
  • the thrust plate 8 has a dynamic pressure generating section 81 equipped with a first group of inclined grooves 85 located on the low pressure chamber 20 side and a second group of inclined grooves 86 located on the back pressure chamber 50 side, and the second inclined grooves 861 of the second group of inclined grooves 86 are not connected to the back pressure chamber 50 side.
  • a recess 84 is formed as a buffer space, so that the fluid F1 that flows out from the first inclined groove group 85 between the sliding surfaces 7a and 8a can be stored in the recess 84, and the fluid F1 can be supplied from the recess 84 to the second inclined groove group 86.
  • the fluid F1 can be stored without being affected by the distance between the sliding surfaces 7a, 8a, i.e., the axial positions of the thrust plate 8 and the side seal 7, so that the fluid F1 in the recess 84 can generate dynamic pressure in the second inclined groove group 86.
  • one end 861a of the second inclined groove 86 of the second inclined groove group 86 is connected to the recess 84. This allows the fluid F1 to be smoothly supplied from the recess 84 to the second inclined groove 861 of the second inclined groove group 86.
  • one end 851a of the first inclined groove 851 of the first inclined groove group 85 is connected to the low pressure chamber 20, so that the fluid F1 can be smoothly supplied from the low pressure chamber 20 to the first inclined groove 851.
  • the thrust plate 8 is configured with multiple dynamic pressure generating portions 81 connected in an annular manner so that each second inclined groove group 86 is located on the back pressure chamber 50 side. This makes it possible to prevent the fluid F2 in the back pressure chamber 50 from leaking circumferentially to the low pressure chamber 20 side.
  • the thrust plate 28 of this embodiment 2 is provided with a communication groove 287 that connects the recess 284 with the low pressure chamber 20.
  • the communication groove 287 is a recessed groove that opens on the sliding surface 28a side.
  • the recess 284 can constantly take in the fluid F1 from the low pressure chamber 20 through the communication groove 287, so the fluid F1 in the recess 284 does not run out and stable sliding properties can be achieved.
  • the communication groove 287 is a recessed groove that opens on the sliding surface 28a side, but this is not limited to this, and it may be a hole that communicates between the side of the recess 284 on the low pressure chamber 20 side and the side of the thrust plate 28 on the low pressure chamber 20 side.
  • all of the second inclined grooves 861 in the second inclined groove group 86 are not connected to the back pressure chamber 50, but some of the second inclined grooves 861 may be connected to the back pressure chamber.
  • the number of inclined grooves not connected to the back pressure chamber is greater than the number of inclined grooves connected to the back pressure chamber.
  • first and second grooves are inclined grooves, but they do not have to be inclined grooves.
  • any groove capable of generating dynamic pressure may be used, and any known structure capable of generating dynamic pressure may be used, such as grooves extending parallel to the circumferential direction or grooves with an inclined bottom surface.
  • the thrust plate in the first and second embodiments is exemplified as having a ring-shaped configuration in which multiple dynamic pressure generating parts are connected in the circumferential direction, but it is sufficient that at least one dynamic pressure generating part is provided. Note that the thrust plate is not limited to being ring-shaped.
  • a recess is formed in the thrust plate as a buffer space, but a buffer space such as a recess may be formed on the side seal side. Furthermore, a buffer space does not have to be provided between the first inclined groove group and the second inclined groove group.
  • the inclined grooves of the second inclined groove group are shown to be in communication with the recesses, but they may be dimples or the like that do not communicate with the recesses.
  • the inclined grooves of the first group of inclined grooves are shown to be in communication with the low pressure chamber, but they may be dimples or the like that do not communicate with the low pressure chamber.
  • a thrust plate is applied as a thrust receiving mechanism to a scroll compressor C used in an air conditioning system of an automobile or the like, but the present invention is not limited to this and may be applied to any rotary machine that includes an eccentric mechanism, such as a scroll expansion and compression machine that has an expander and compressor integrated together.
  • the outer diameter side of the thrust plate is described as the low pressure side and the inner diameter side as the high pressure side, but the outer diameter side of the thrust plate may be the high pressure side and the inner diameter side may be the low pressure side.
  • the fluid present in the space inside and outside the sliding surface of the thrust receiving mechanism may be either gas, liquid, or a mixture of gas and liquid.
  • the side seals having the sliding surfaces that slide relative to each other are described as being made of resin, and the thrust plate is described as being made of metal, but the material of the thrust receiving mechanism may be freely selected according to the usage environment, etc.
  • the thrust plate is fitted into an installation groove provided in the inner casing, thereby restricting rotation.
  • the thrust plate may be fixed to the inner casing with a bolt or the like so that it cannot rotate.
  • Scroll compression mechanism 7 Side seal 7a Sliding surface (back side sliding surface) 8 Thrust plate (thrust receiving mechanism) 8a Sliding surface 20 Low pressure chamber (low pressure side) 28 Thrust plate 28a Sliding surface 41 Fixed scroll 42 Movable scroll 50 Back pressure chamber (high pressure side) 81, 81A Dynamic pressure generating portion 84 Recess 85 First inclined groove group 86 Second inclined groove group 284 Recess 287 Communication groove 851 First inclined groove 861 Second inclined groove C Scroll compressors F1, F2 Fluid

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
PCT/JP2023/040690 2022-11-17 2023-11-13 スラスト受機構 Ceased WO2024106362A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
KR1020257006467A KR20250041053A (ko) 2022-11-17 2023-11-13 스러스트 수용 기구
EP23891509.4A EP4621235A1 (en) 2022-11-17 2023-11-13 Thrust support mechanism
JP2024558843A JPWO2024106362A1 (https=) 2022-11-17 2023-11-13
US19/106,562 US20260022700A1 (en) 2022-11-17 2023-11-13 Thrust receiving mechanism
CN202380062022.8A CN119790228A (zh) 2022-11-17 2023-11-13 推力支承机构

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022-184400 2022-11-17
JP2022184400 2022-11-17

Publications (1)

Publication Number Publication Date
WO2024106362A1 true WO2024106362A1 (ja) 2024-05-23

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PCT/JP2023/040690 Ceased WO2024106362A1 (ja) 2022-11-17 2023-11-13 スラスト受機構

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Country Link
US (1) US20260022700A1 (https=)
EP (1) EP4621235A1 (https=)
JP (1) JPWO2024106362A1 (https=)
KR (1) KR20250041053A (https=)
CN (1) CN119790228A (https=)
WO (1) WO2024106362A1 (https=)

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