WO2020208765A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2020208765A1
WO2020208765A1 PCT/JP2019/015731 JP2019015731W WO2020208765A1 WO 2020208765 A1 WO2020208765 A1 WO 2020208765A1 JP 2019015731 W JP2019015731 W JP 2019015731W WO 2020208765 A1 WO2020208765 A1 WO 2020208765A1
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WO
WIPO (PCT)
Prior art keywords
end plate
swivel
fixed
axis
scroll
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/JP2019/015731
Other languages
English (en)
Japanese (ja)
Inventor
隆史 渡辺
央幸 木全
陽平 堀田
創 佐藤
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 Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems 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 Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Priority to EP19924154.8A priority Critical patent/EP3936723B1/fr
Priority to JP2021513105A priority patent/JP7216808B2/ja
Priority to PCT/JP2019/015731 priority patent/WO2020208765A1/fr
Publication of WO2020208765A1 publication Critical patent/WO2020208765A1/fr
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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/066—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with an intermediate piece sliding along perpendicular axes, e.g. Oldham coupling
    • 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base

Definitions

  • the present invention relates to a scroll compressor.
  • a scroll compressor used in an air conditioner, a refrigerating device, or the like to compress a refrigerant is generally known.
  • the refrigerant is compressed by turning the swivel scroll with respect to the fixed scroll by the old dam ring.
  • the present invention provides a scroll compressor capable of improving efficiency while supporting high pressure and increasing the capacity.
  • the scroll compressor includes a rotating shaft extending along an axis, a motor that rotates the rotating shaft, a scroll compression unit that compresses a refrigerant by rotating the rotating shaft, and the rotating shaft.
  • a fixed scroll comprising a motor and a housing for accommodating the scroll compression portion, the scroll compression portion having a fixed end plate fixed to the housing and a fixed wrap projecting from the fixed end plate in the axial direction.
  • a swivel end plate provided on the rotating shaft and arranged on the fixed end plate so as to face the direction of the axis, and a refrigerant protruding from the swivel end plate toward the fixed end plate and the fixed wrap.
  • a swivel scroll having a swivel lap forming a compression chamber of the above and the swivel scroll are interposed between the fixed end plate and the swivel end plate to support the swivel scroll so as to swivel with respect to the axis without rotating.
  • An old dam ring, the old dam ring has a ring body forming an annular shape so as to surround the axis, and a key provided on the swivel end plate and the fixed end plate so as to project from the surface of the ring body.
  • Each of the keys has a plurality of keys to be inserted into the grooves, and the swivel end plate is integrally formed with a thick portion having a disk shape and provided with the swivel wrap on the radial outer side of the thick portion. It is provided to form an annular shape, the thickness dimension in the direction of the axis is smaller than that of the thick portion, and the end face facing the fixed end plate side is located at a position away from the fixed end plate as compared with the thick portion. It has an arranged thin-walled portion, and the ring main body is placed and provided on the end face of the thin-walled portion.
  • the swivel end plate of the swivel scroll has a thick portion and a thin wall portion. Further, the thin portion is provided on the outer side in the radial direction of the swivel end plate. Therefore, the weight of the radial outer end of the swivel end plate can be reduced, and the moment of inertia when the swivel end plate swivels around the axis of the rotation axis can be reduced. Therefore, even if the swivel end plate is enlarged in order to cope with high pressure and increase the capacity of the scroll compressor, it is possible to suppress an increase in vibration and an increase in power.
  • the influence of the compressive load when compressing the refrigerant is smaller at the radial outer end of the swivel end plate than at the center of the swirl end plate, even if a thin portion is provided, a problem in terms of strength is unlikely to occur.
  • the thickness dimension in the direction of the axis of the old dam ring is increased, the amount of the old dam ring that protrudes to the fixed scroll side by placing the ring body of the old dam ring on the thin part of the swivel end plate. Can be reduced, and the fixed end plate can be brought closer to the swivel end plate. Therefore, while increasing the thickness dimension of the old dam ring to secure the strength, the dimension in the axial direction of the scroll compression portion can be reduced, and the scroll compression portion can be made compact.
  • the ring is more than the distance in the axial direction between the end face of the thick portion facing the fixed end plate side and the end face of the thin portion facing the fixed end plate side.
  • the thickness dimension in the direction of the axis of the main body may be larger.
  • an old dam ring can be provided so that the ring body protrudes in the direction of the axis from the end face of the thick portion facing the fixed end plate side. Therefore, in order to improve the strength of the old dam ring, it is possible to increase the thickness dimension in the axial direction of the old dam ring.
  • the scroll compressor is provided in the housing to rotatably support the rotating shaft, and is a bearing arranged on the opposite side of the rotating end plate in the direction of the axis line from the compression chamber.
  • a thrust plate provided between the bearing and the swivel end plate to support the swivel end plate in the direction of the axis, and the thrust plate forms an annular shape so as to surround the axis.
  • At least a part may be arranged at a position supporting the thick portion.
  • the thrust plate By providing the thrust plate at such a position, it is possible to support the thick portion that receives a larger thrust load due to the compression load with the thrust plate. Therefore, even if the swivel end plate is provided with a thin wall portion, it can sufficiently cope with the compressive load.
  • the key groove in the swivel end plate into which the key is inserted may be provided over the thin portion and the thick portion.
  • the radial dimension of the key can be increased. Therefore, the surface pressure of the surface on which the key slides with respect to the key groove can be reduced, and the strength of the old dam ring can be improved. Further, even if the keyway extends to the thick portion, the thickness dimension in the axial direction of the thick portion is larger than that of the thin portion, so that a problem in strength is unlikely to occur.
  • the above scroll compressor can improve efficiency while supporting high pressure and increasing capacity.
  • FIG. 1 It is a vertical sectional view of the scroll compressor which concerns on embodiment of this invention. It is an enlarged figure which shows the scroll compression part in the scroll compressor which concerns on embodiment of this invention. It is a top view which shows the fixed scroll in the scroll compressor which concerns on embodiment of this invention. It is a top view which shows the swivel scroll in the scroll compressor which concerns on embodiment of this invention. It is a top view which shows the old dam ring in the scroll compressor which concerns on embodiment of this invention. It is a figure which shows the old dumb ring in the scroll compressor which concerns on embodiment of this invention, and is the AA sectional view of FIG. It is a figure which shows the old dam ring in the scroll compressor which concerns on embodiment of this invention, and is the BB sectional view of FIG.
  • the scroll compressor 1 according to the embodiment of the present invention will be described.
  • a vertical closed two-stage compressor having two compression units 4 and 5 will be described as the scroll compressor 1, but the scroll compressor 1 is not limited to such a compressor.
  • it may be a single-stage compressor having only one compression unit, or it may be a horizontal compressor.
  • the scroll compressor 1 includes a rotating shaft 2, a motor 3 that rotates the rotating shaft 2, and a rotary compression unit 4 and a scroll compressing unit 5 that compress the refrigerant by rotating the rotating shaft 2.
  • the scroll compressor 1 further includes a housing 6 that hermetically houses the rotary shaft 2, the motor 3, the rotary compression unit 4, and the scroll compression unit 5.
  • the rotating shaft 2 has a columnar shape centered on the axis O1 extending in the vertical direction.
  • an eccentric shaft 8 forming a columnar shape centered on the axis O2 arranged at a position displaced in the radial direction with respect to the axis O1 is integrally provided.
  • the housing 6 has a tubular shape extending in the vertical direction along the axis O1 of the rotating shaft 2.
  • the housing 6 is formed, for example, by casting.
  • the housing 6 has a cylindrical housing body 10, an upper lid 11 that closes an opening above the housing body 10, and a lower lid 12 that closes an opening below the housing body 10.
  • the housing 6 has a sealed space S extending in the vertical direction inside. Oil (lubricating oil) is stored from the lower part of the housing body 10 to the bottom of the lower lid 12, and an oil pool OL is formed at this position.
  • a suction pipe 13 for introducing the refrigerant from the outside into the space S is connected to the lower part of the housing 6.
  • a discharge pipe 14 for discharging the refrigerant from the space S to the outside is connected to the upper part of the housing 6.
  • a rotary lower bearing 20, a rotary upper bearing 21, and a scroll bearing 22 that rotatably support the rotary shaft 2 with respect to the housing 6 are provided inside the housing 6, a rotary lower bearing 20, a rotary upper bearing 21, and a scroll bearing 22 that rotatably support the rotary shaft 2 with respect to the housing 6 are provided.
  • the rotary lower bearing 20 and the rotary upper bearing 21 are provided in the rotary compression section 4, and the scroll bearing 22 is provided in the scroll compression section 5.
  • the motor 3 is provided above the rotary upper bearing 21 and below the scroll bearing 22 in the space S of the housing 6 so as to be surrounded by the housing body 10.
  • a power supply (not shown) is connected to the motor 3 through a terminal 15 provided in the housing 6. The motor 3 rotates the rotating shaft 2 by the electric power from the power source.
  • the rotary compression unit 4 is provided below the motor 3 so as to be sandwiched between the rotary lower bearing 20 and the rotary upper bearing 21. More specifically, the rotary compression unit 4 has a cylinder 30 arranged above the rotary lower bearing 20 and below the rotary upper bearing 21. The cylinder 30 is arranged in the oil sump OL. A suction pipe 13 is connected to the cylinder 30. The cylinder 30 has a compression chamber C1 inside which compresses the refrigerant introduced from the suction pipe 13. A rotating shaft 2 is inserted through the compression chamber C1. A piston 31 is provided on the rotating shaft 2. The refrigerant is compressed by the rotation of the piston 31 in the compression chamber C1 with the rotation of the rotating shaft 2. The refrigerant compressed in the compression chamber C1 of the rotary compression unit 4 passes through the rotary upper bearing 21 and flows upward toward the motor 3 side.
  • the rotary compression unit 4 of the present embodiment has a twin rotary structure in which cylinders 30 are provided in two stages at the top and bottom, but for example, it has a single rotary structure in which only one cylinder 30 is provided. You may. Further, the connection position of the suction pipe 13 to the rotary compression unit 4 is not limited to the case shown in FIG.
  • the scroll compression unit 5 is arranged above the motor 3 in the space S. More specifically, as shown in FIG. 2, the scroll compression unit 5 is vertically sandwiched between the fixed scroll 40 fixed to the housing 6 above the scroll bearing 22 and the fixed scroll 40 and the scroll bearing 22. It has a swivel scroll 43 provided. Further, the scroll compression unit 5 has an old dam ring 50 that engages with the fixed scroll 40 and the swivel scroll 43.
  • the fixed scroll 40 has a fixed end plate 41 fixed to the housing 6 below the discharge pipe 14 and forming a disk shape centered on the axis O1, and a spiral that protrudes downward from the fixed end plate 41 and is based on the axis O1. It has a fixed wrap 42 in the shape of a shape.
  • the fixed end plate 41 has a mating surface 41a that faces downward in the direction of the axis O1 on the outer side in the radial direction of the fixed wrap 42 and is in surface contact with the scroll bearing 22.
  • An annular groove 41b forming an annular shape centered on the axis O1 is provided between the fixed wrap 42 and the mating surface 41a.
  • the annular groove 41b is recessed upward in the direction of the axis O1 with respect to the mating surface 41a and the cutting edge 42a at the tip of the fixed wrap 42.
  • the mating surface 41a of the fixed end plate 41 and the cutting edge 42a of the fixed wrap 42 are arranged on the same plane.
  • the mating surface 41a and the cutting edge 42a of the fixed lap 42 are not completely arranged on the same plane so as to allow this thermal elongation, and the fixed lap 42 is slightly fixed.
  • the cutting edge 42a of 42 may be arranged above the mating surface 41a.
  • the fixed end plate 41 is provided with a pair of fixed side key grooves 41c at intervals of 180 degrees in the circumferential direction.
  • the fixed side key groove 41c extends radially from a position close to the fixed wrap 42 to a position in the middle of the mating surface 41a.
  • the fixed side key groove 41c is formed so as to be recessed upward in the direction of the axis O1 from the annular groove 41b.
  • Each fixed-side key groove 41c has a rectangular cross section orthogonal to the radial direction.
  • Each fixed-side key groove 41c has a key sliding surface 41d which is a pair of planes arranged in parallel at intervals in the circumferential direction and extending along the direction and the radial direction of the axis O1.
  • the fixed end plate 41 is formed with a pair of suction flow paths 41e that communicate with the compression chamber C2, which will be described later, formed by the fixed wrap 42.
  • the pair of suction flow paths 41e are provided at positions between the pair of fixed side key grooves 41c so as not to interfere with each other. That is, each discharge flow path 41e is provided one by one between each fixed side key groove 41c at a position separated from the pair of fixed side key grooves 41c in the circumferential direction.
  • Each suction flow path 41e is recessed further upward than the annular groove 41b in the direction of the axis O1, extends from the fixed wrap 42 through the annular groove 41b to the mating surface 41a, and opens on the outer peripheral surface of the fixed end plate 41. are doing.
  • the swivel scroll 43 is arranged below the fixed end plate 41 and faces the swivel end plate 44 in the direction of the axis O1 with respect to the fixed end plate 41, and the swivel scroll 43 and the fixed end upward in the direction of the axis O1 from the swivel end plate 44. It has a swivel lap 45 that projects toward the plate 41.
  • the swivel end plate 44 has a disk shape centered on the axis O2 of the eccentric shaft 8 and is attached to the eccentric shaft 8. As shown in FIGS. 2 and 4, the swivel end plate 44 has a thick portion 44a forming a disk shape centered on the axis O2 of the eccentric shaft 8 and a thick portion 44a that is radially outward from the thick portion 44a. It has a flange-shaped thin-walled portion 44b protruding from the surface.
  • the thick portion 44a is rotatably connected to the eccentric shaft 8 with respect to the eccentric shaft 8. Specifically, a cylindrical portion 46 that covers the eccentric shaft 8 from the outer circumference is integrally provided below the thick portion 44a. As shown in FIG. 1, a bearing 46a is provided inside the cylindrical portion 46 so that the thick portion 44a rotates together with the cylindrical portion 46 around the axis O2 of the eccentric shaft 8.
  • the thin portion 44b has an annular shape centered on the axis O2 of the eccentric axis 8.
  • the thin portion 44b has a smaller thickness dimension in the axes O1 and O2 than the thick portion 44a, and the end surface (upper surface) facing the fixed end plate 41 side is smaller than the thick portion 44a. It is located away from.
  • the swivel end plate 44 has a surface facing the radial direction at the outer end portion in the radial direction, and a step is provided at the radial outer end portion of the swivel end plate 44.
  • the swivel end plate 44 is provided with a pair of swivel side key grooves 44c at intervals of 180 degrees in the circumferential direction.
  • the swivel-side key groove 44c opens on the outer peripheral surface of the thin-walled portion 44b and extends from the outer peripheral surface of the thin-walled portion 44b to the thick-walled portion 44a in the radial direction. Therefore, the swivel side key groove 44c is provided between the thin portion 44b and the thick portion 44a.
  • the swivel-side key groove 44c penetrates the thin-walled portion 44b in the direction of the axis O1 and has the same thickness dimension in the axis line O1 direction as the thickness dimension in the axis line O1 direction of the thin-walled portion 44b, up to the thick-walled portion 44a. It extends in the radial direction. Therefore, when the swivel end plate 44 is viewed from above, the swivel side key groove 44c is provided so as to slip into the back side of the thick portion 44a.
  • Each swivel side keyway 44c has a rectangular cross section orthogonal to the radial direction.
  • Each of the swing-side key grooves 44c has a key sliding surface 44d which is a pair of planes arranged in parallel at intervals in the circumferential direction and extending along the direction and the radial direction of the axis O1.
  • the swivel lap 45 is provided so as to overlap the fixed lap 42 in the radial direction so as to face the fixed lap 42 in the radial direction.
  • the space between the swirling lap 45 and the fixed lap 42 is a compression chamber C2 in which the refrigerant is compressed.
  • the refrigerant flowing out of the compression chamber C1 of the rotary compression unit 4 is introduced into the compression chamber C2 after passing around the motor 3 and the scroll bearing 22.
  • the Oldam ring 50 has a ring main body 51 forming an annular shape so as to surround the axis O1 of the rotating shaft 2, a pair of fixed side keys 52 provided on the ring main body 51, and a pair of swivel side keys 53.
  • the ring body 51 has a substantially constant thickness, that is, a substantially constant dimension in the axis O1 direction.
  • the ring main body 51 is placed on an end surface (upper surface) of the thin portion 44b of the swivel end plate 44 facing the fixed end plate 41 side.
  • the surface (upper surface) of the ring body 51 facing the fixed end plate 41 is the surface of the thick portion 44a facing the fixed end plate 41 (the surface). Since it is located above the upper surface), a part of the ring body 51 protrudes upward from the thick portion 44a.
  • a part of the ring body 51 protruding upward from the thick portion 44a is arranged in the annular groove 41b of the fixed end plate 41. Further, since a minute gap SS is provided between the surface (upper surface) of the ring body 51 facing the fixed end plate 41 side and the bottom surface of the annular groove 41b, the surface of the ring body 51 and the bottom surface of the annular groove 41b are provided. Are provided at intervals.
  • the pair of fixed-side keys 52 are members having a rectangular cross section that protrude upward from the surface of the ring body 51 that faces upward at intervals of 180 degrees in the circumferential direction.
  • Each fixed-side key 52 has a radial dimension equivalent to the radial width dimension of the ring main body 51, and is provided integrally with the ring main body 51 in a radial direction so as not to protrude from the ring main body 51. ing.
  • the pair of fixed-side keys 52 are inserted into and engaged with the pair of fixed-side key grooves 41c provided in the fixed end plate 41, respectively.
  • Each fixed-side key 52 has planar side surfaces 52a that slide with respect to the key sliding surface 41d of the fixed-side key groove 41c on both sides in the circumferential direction. The fixed side key 52 reciprocates in the radial direction within the fixed side key groove 41c.
  • the pair of swivel-side keys 53 have a cross section that projects downward from the downward-facing surface of the ring body 51 at a position that is 180 degrees apart in the circumferential direction and 90 degrees away from the fixed-side key 52 in the circumferential direction. It is a rectangular member.
  • Each swivel side key 53 has a radial dimension larger than the radial width dimension of the ring body 51, and is provided integrally with the ring body 51 in a state of protruding inward in the radial direction from the ring body 51. ..
  • the radial outer end face of each swivel side key 53 and the radial outer end face of the ring body 51 are arranged at substantially the same position.
  • each turning side key 53 is provided on the ring main body 51 so as not to protrude radially outward from the ring main body 51.
  • the pair of swivel-side keys 53 are inserted into and engaged with the pair of swivel-side key grooves 44c provided in the swivel end plate 44, respectively.
  • Each swivel side key 53 has planar side surfaces 53a that slide with respect to the key sliding surface 44d of the swivel side key groove 44c on both sides in the circumferential direction.
  • the swivel side key 53 reciprocates in the radial direction within the swivel side key groove 44c.
  • the reciprocating movement of the turning side key 53 and the turning side key groove 44c and the reciprocating movement of the fixed side key 52 and the fixed side key groove 41c cause the turning scroll 43 to turn around the axis O1 of the rotating shaft 2 without rotating.
  • the refrigerant in the compression chamber C2 is compressed by the relative movement between the fixed lap 42 and the swirling lap 45.
  • the swivel end plate 44 of the swivel scroll 43 has a thick portion 44a and a thin wall portion 44b. Further, the thin portion 44b is provided on the outer side in the radial direction of the swivel end plate 44. Therefore, the weight of the radial outer end of the swivel end plate 44 can be reduced, and the moment of inertia when the swivel end plate 44 swivels around the axis O1 of the rotating shaft 2 can be reduced. Therefore, even if the swivel end plate 44 is enlarged in order to cope with high pressure and increase the capacity of the scroll compressor 1, it is possible to suppress the increase in size of the motor 3. As a result, it is possible to improve the efficiency of the scroll compressor 1 while supporting high pressure and increasing the capacity.
  • the influence of the compressive load is smaller at the radial outer end of the swivel end plate 44 than at the central portion of the swivel end plate 44. Therefore, even if the swivel end plate 44 is provided with the thin portion 44b, there is little problem in terms of strength.
  • the ring body 51 of the old dam ring 50 is placed on the thin portion 44b of the swivel end plate 44 to provide the old dam ring 50.
  • the amount of the scroll protruding from the swivel end plate 44 toward the fixed scroll 40 can be reduced. Therefore, the fixed end plate 41 can be brought closer to the swivel end plate 44.
  • the dimension of the scroll compression unit 5 in the direction of the axis O1 can be reduced, and the scroll compression unit 5 can be made compact. Therefore, it is possible to make the entire scroll compressor 1 compact while supporting high pressure and increasing the capacity.
  • the old dam ring 50 is provided so that the ring body 51 protrudes in the direction of the axis O1 from the end surface of the thick portion 44a facing the fixed end plate 41 side, and further, the ring body 51 is provided in the annular groove 41b of the fixed end plate 41. A part of the ring body 51 is arranged. Therefore, even if the thickness dimension of the old dam ring 50 in the direction of the axis O1 is increased in order to cope with high pressure and increase the capacity, the fixed end plate 41 can be arranged closer to the swivel end plate 44. Therefore, the scroll compression unit 5 can be made more compact in the direction of the axis O1.
  • the lubricating oil when the lubricating oil is introduced into the scroll compression unit 5, the lubricating oil can be held in the annular groove 41b, the operation of the scroll compression unit 5 can be smoothed, and the efficiency can be further improved.
  • the thrust plate 47 since at least a part of the thrust plate 47 is provided at a position to support the thick portion 44a of the swivel end plate 44, the thick portion 44a that receives more thrust load due to the compression load is supported by the thrust plate 47. can do. Therefore, even if the swivel end plate 44 is provided with the thin-walled portion 44b, the load does not act only on the thin-walled portion 44b, and the compressive load can be sufficiently coped with.
  • the swivel side key groove 44c extends to the thick portion 44a, but since the thickness dimension of the thick portion 44a in the direction of the axis O1 is larger than that of the thin portion 44b, a problem in terms of strength is unlikely to occur. ..
  • the fixed side key groove 41c is provided so as to extend from the annular groove 41b to the radial outside of the annular groove 41b of the fixed end plate 41. Therefore, for example, when a hole is drilled in the fixed end plate 41 at a position on the radial outer side of the annular groove 41b and an end mill is inserted into the hole to provide the fixed side key groove 41c, the machining start point of the end mill is set. It is formed in an arc shape following the outer shape of the drill.
  • the key sliding surface 41d of the fixed side key groove 41c can be formed in a planar shape along the radial direction in the annular groove 41b. .. Therefore, a flat key sliding surface 41d can be easily formed in the annular groove 41b.
  • the wall thickness in the direction of the axis O1 of the fixed end plate 41 is the direction of the axis O1 at the position where the annular groove 41b is formed. It is larger than the wall thickness of. Therefore, even if the fixed side key groove is formed so as to extend outward in the radial direction of the annular groove 41b, a problem in strength is unlikely to occur.
  • the bottom surface of the annular groove 41b and the surface of the ring body 51 are provided at intervals in the direction of the axis O1. Therefore, it becomes difficult for the surface of the ring body 51 to come into contact with the bottom surface of the annular groove 41b during the operation of the scroll compressor 1. Therefore, the friction loss between the old dam ring 50 and the fixed end plate 41 can be reduced.
  • the ring body 51 of the Oldam ring 50 may have a size that does not protrude upward in the direction of the axis O1 from the thick portion 44a.
  • the swivel side key groove 44c may be formed only in the thin wall portion 44b.
  • the fixed side key groove may be formed only in the annular groove.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un compresseur à spirale (1) dans lequel : une plaque d'extrémité orbitale (44) d'une spirale orbitale (43) comprend : une partie épaisse (44a) qui forme une forme de disque et est pourvue d'une enveloppe orbitale (45) ; et une partie mince (44b) qui est intégrée à la partie épaisse (44a) sur l'extérieur dans la direction radiale de manière à former une forme d'anneau, qui a une dimension d'épaisseur plus petite dans la direction d'un axe (O1) que la partie épaisse (44a), et qui a une face d'extrémité faisant face à un côté plaque d'extrémité fixe (41), ladite face d'extrémité étant positionnée plus loin de la plaque d'extrémité fixe (41) que la partie épaisse (44a). Un corps annulaire (51) d'une bague d'Oldham (50) est monté sur la face d'extrémité dans la partie mince (44b).
PCT/JP2019/015731 2019-04-11 2019-04-11 Compresseur à spirale Ceased WO2020208765A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP19924154.8A EP3936723B1 (fr) 2019-04-11 2019-04-11 Compresseur à spirale
JP2021513105A JP7216808B2 (ja) 2019-04-11 2019-04-11 スクロール圧縮機
PCT/JP2019/015731 WO2020208765A1 (fr) 2019-04-11 2019-04-11 Compresseur à spirale

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/015731 WO2020208765A1 (fr) 2019-04-11 2019-04-11 Compresseur à spirale

Publications (1)

Publication Number Publication Date
WO2020208765A1 true WO2020208765A1 (fr) 2020-10-15

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CN120140217A (zh) * 2025-04-30 2025-06-13 珠海凌达压缩机有限公司 一种动涡旋盘、泵体组件和涡旋压缩机

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JP2009030514A (ja) 2007-07-26 2009-02-12 Denso Corp スクロール型圧縮機
US20130089450A1 (en) * 2011-10-05 2013-04-11 Taemin EARMME Scroll compressor with oldham ring
JP2019027406A (ja) * 2017-08-02 2019-02-21 三菱重工サーマルシステムズ株式会社 オルダムリング、スクロール圧縮機

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JPH0874759A (ja) * 1994-09-07 1996-03-19 Sanyo Electric Co Ltd スクロール型流体機械
JP2009030514A (ja) 2007-07-26 2009-02-12 Denso Corp スクロール型圧縮機
US20130089450A1 (en) * 2011-10-05 2013-04-11 Taemin EARMME Scroll compressor with oldham ring
JP2019027406A (ja) * 2017-08-02 2019-02-21 三菱重工サーマルシステムズ株式会社 オルダムリング、スクロール圧縮機

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN120140217A (zh) * 2025-04-30 2025-06-13 珠海凌达压缩机有限公司 一种动涡旋盘、泵体组件和涡旋压缩机

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EP3936723B1 (fr) 2024-10-09
EP3936723A4 (fr) 2022-03-23
EP3936723C0 (fr) 2024-10-09
JP7216808B2 (ja) 2023-02-01
JPWO2020208765A1 (fr) 2020-10-15

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