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WO2017002536A1 - Compresseur à volutes - Google Patents

Compresseur à volutes Download PDF

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Publication number
WO2017002536A1
WO2017002536A1 PCT/JP2016/066651 JP2016066651W WO2017002536A1 WO 2017002536 A1 WO2017002536 A1 WO 2017002536A1 JP 2016066651 W JP2016066651 W JP 2016066651W WO 2017002536 A1 WO2017002536 A1 WO 2017002536A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
communication hole
counterweight
chamber
housing
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/JP2016/066651
Other languages
English (en)
Japanese (ja)
Inventor
立起 野村
藤田　洋
崇三郎 淺川
正幸 野邊
智一 宮治
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.)
Sanden Automotive Components Corp
Original Assignee
Sanden Automotive Components 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 Sanden Automotive Components Corp filed Critical Sanden Automotive Components Corp
Priority to US15/740,195 priority Critical patent/US20180187679A1/en
Priority to CN201680038468.7A priority patent/CN107923395A/zh
Publication of WO2017002536A1 publication Critical patent/WO2017002536A1/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
    • F04C18/063—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 with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F04C18/07—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 with coaxially-mounted members having continuously-changing circumferential spacing between them having crankshaft-and-connecting-rod type drive
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C27/009—Shaft sealings specially adapted for pumps
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/021—Control systems for the circulation of the lubricant
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • 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
    • 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
    • F04C2240/808—Electronic circuits (e.g. inverters) installed inside the machine

Definitions

  • the present invention relates to a scroll compressor, and more particularly to a scroll compressor used in a refrigeration circuit of a vehicle air conditioner.
  • Patent Document 1 includes a shaft seal mechanism in which a fixed scroll and a movable scroll are accommodated in a housing, a rotating shaft is supported by the housing via a bearing, and is fitted between the rotating shaft and the housing.
  • a scroll compressor is disclosed in which a communication passage is formed to communicate between a seal chamber and a refrigerant suction chamber.
  • the compressor has a structure in which a suction port is provided on the outer peripheral side of the scroll unit on the outer peripheral wall of the housing, the refrigerant introduced from the suction port can be immediately sucked into the scroll unit, so that the refrigerant compression efficiency is improved. Can be expected.
  • the compressor having such a structure the flow rate of the refrigerant flowing into a portion of the housing away from the suction port is reduced, and there has been a concern about deterioration of lubrication of a lip seal as a shaft seal mechanism or a sealing device.
  • a scroll compressor converts a scroll unit that compresses refrigerant by revolving orbiting a movable scroll relative to a fixed scroll, and converts the rotational motion of a rotating shaft into the orbiting revolving motion of the movable scroll.
  • a crank mechanism for transmitting the housing a housing in which the scroll unit is housed and having a refrigerant suction port on an outer peripheral wall located on the outer peripheral side of the scroll unit, and a sealing device for sealing between the housing and the rotating shaft, Includes a crank chamber in which the crank mechanism is positioned, a seal chamber in which the sealing device is positioned, a communication hole that communicates the crank chamber and the seal chamber, and a first hole that extends from the opening of the communication hole in the seal chamber to the vicinity of the sealing device. And a guide groove.
  • the housing further includes a second guide groove in which the opening of the communication hole in the crank chamber is positioned.
  • the crank mechanism includes a counterweight attached to the rotating shaft, and the communication hole is formed at a position that is intermittently covered with the counterweight as the counterweight turns.
  • the communication hole is inclined along the turning direction of the counterweight with respect to the radial direction of the rotating shaft.
  • the counterweight has an inclined surface inclined with respect to the axis of the rotation axis.
  • the counterweight has a step surface protruding in the radial direction of the rotation shaft.
  • the lubricating oil is actively guided to the sealing device, so that the compression efficiency of the compressor is improved and the wear of the sealing device is greatly reduced.
  • the remaining tightening allowance can be secured and the sealing performance of the compressor can be maintained over a long period of time.
  • FIG. 6 It is a longitudinal section of the scroll compressor concerning a 1st embodiment of the present invention. It is the longitudinal cross-sectional view of the scroll compressor which expanded a part of crank chamber and seal chamber of FIG. It is the top view which looked at the front housing of FIG. 1 from the opening end side. It is the top view which showed another form of FIG. It is the top view which showed the further another form of FIG. It is the longitudinal cross-sectional view of the scroll compressor which expanded some crank chambers and seal chambers concerning 2nd Embodiment of this invention. It is the top view which looked at the front housing of FIG. 6 from the opening end side. It is the top view which looked at the front housing which concerns on 3rd Embodiment of this invention from the opening end side. It is the side view shown in the state where the counterweight which concerns on 4th Embodiment of this invention was mounted
  • FIG. 1 is a longitudinal sectional view of a scroll compressor 1 according to the first embodiment of the present invention.
  • the compressor 1 is incorporated in, for example, a refrigeration circuit of a vehicle air conditioner mounted on a vehicle, and is used for compressing a refrigerant circulating in the refrigeration circuit.
  • the compressor 1 includes a rear housing (housing) 2 and a front housing (housing) 4, and a scroll unit 6 is disposed in the rear housing 2.
  • the scroll unit 6 includes a fixed scroll 8 fixed to the rear housing 2 and a movable scroll 10 assembled so as to mesh with the fixed scroll 8.
  • the fixed scroll 8 includes an end plate 8a and a fixed spiral body 8b formed integrally with the end plate 8a
  • the movable scroll 10 includes an end plate 10a and a movable spiral body 10b formed integrally with the end plate 10a.
  • the fixed spiral body 8b and the movable spiral body 10b are engaged with each other.
  • a discharge chamber 12 is formed between the end wall 2 a of the rear housing 2 and the fixed scroll 8.
  • the discharge chamber 12 is connected to a compression chamber 18 formed between the fixed scroll 8 and the movable scroll 10 via a reed valve type discharge valve 16 in a discharge hole 14 formed in the end plate 8 a of the fixed scroll 8. Communication is possible.
  • a discharge port 20 is formed on the outer peripheral wall 2b of the rear housing 2 at a position close to the end wall 2a, and the discharge chamber 12 is communicated with the refrigerant circulation path of the refrigeration circuit via the discharge port 20.
  • the outer peripheral wall 2b of the rear housing 2 is provided with a refrigerant suction port 22 on the outer peripheral side of the scroll unit 6, and the refrigerant introduced from the refrigerant circulation path via the suction port 22 is quickly sucked into the scroll unit 6. Is done.
  • a rotary shaft 24 is disposed in the front housing 4, and the rotary shaft 24 has a large-diameter shaft portion 24a and a small-diameter shaft portion 24b.
  • the front housing 4 has a large diameter inner circumferential surface 4b, a medium diameter inner circumferential surface 4c, and a small diameter in order from the opening end 4a located on the rear housing 2 side by gradually reducing the inner circumference of the front housing 4.
  • An inner peripheral surface 4d is formed.
  • the large-diameter shaft portion 24a is rotatably supported with respect to the medium-diameter inner peripheral surface 4c of the front housing 4 via a bearing 26 that is a needle bearing, and the small-diameter shaft portion 24b is front-mounted via a bearing 28 that is a ball bearing.
  • a small-diameter inner peripheral surface 4d of the housing 4 is rotatably supported.
  • a lip seal (sealing device) 30 is disposed between the small diameter shaft portion 24 b and the small diameter inner peripheral surface 4 d of the front housing 4.
  • the outer peripheral side of the lip seal 30 is mounted on a small-diameter inner peripheral surface 4d, and the lip portion located on the inner peripheral side functions as a sealing device by contacting the rotating small-diameter shaft portion 24b, so that the front housing 4 is hermetically sealed. Partition.
  • the small-diameter shaft portion 24b of the rotary shaft 24 protrudes from the front housing 4, and the protruding end is connected to a drive pulley 32 having a built-in electromagnetic clutch.
  • the drive pulley 32 is rotatably supported by the front housing 4 via a bearing 34 that is a ball bearing.
  • the drive pulley 32 is connected to an output pulley on the engine side of the vehicle via a belt, and is rotated by receiving power from the engine.
  • crank pin 24c protrudes from the large diameter shaft portion 24a of the rotating shaft 24 toward the movable scroll 10.
  • the crank pin 24 c is provided at a position eccentric from the axis of the rotary shaft 24, and is inserted into and fitted into a crank pin hole 38 formed in the eccentric bush 36.
  • the crank pin 24c supports the eccentric bush 36 by its base end 24c1. Further, the eccentric bush 36 supports the boss 41 of the movable scroll 10 via a bearing 40 which is a needle bearing.
  • a counterweight 42 is attached to the crank pin 24c so as to be sandwiched between the eccentric bush 36 and the large diameter shaft portion 24a.
  • the counterweight 42 is configured by superimposing a plurality of large and small arc-shaped plates 42 a in the axial direction of the rotary shaft 24, counteracts the centrifugal force acting on the rotary shaft 24 as the movable scroll 10 rotates and revolves. Balances the revolution.
  • crank pin 44c, the eccentric bush 36, the boss 41, and the counterweight 42 described above constitute the crank mechanism 44 that converts the rotational motion of the rotary shaft 24 into the revolving orbiting motion of the movable scroll 10 and transmits it.
  • a ball coupling type rotation prevention mechanism 46 is disposed between the end plate 10 a of the movable scroll 10 and the opening end 4 a of the front housing 4. The rotation prevention mechanism 46 prevents the rotation of the movable scroll 10 without hindering the revolving turning motion of the movable scroll 10 relative to the fixed scroll 8.
  • a refrigerant compression chamber 18 containing lubricating oil is defined between the fixed spiral body 8b and the movable spiral body 10b.
  • the volume of the movable spiral body 10b is reduced while the movable spiral body 10b moves toward the center of the fixed spiral body 8b by the revolving orbiting motion of the movable scroll 10 relative to the fixed scroll 8, and the refrigerant is compressed.
  • the compressed refrigerant is discharged into the discharge chamber 12 through the discharge hole 14 and sent out from the discharge port 20 to the refrigerant circulation path.
  • the front housing 4 has a crank chamber 48 defined inside the large-diameter inner peripheral surface 4b.
  • the crank chamber 48 is a space in the front housing 4 in which the crank mechanism 44 is positioned, and smooth revolving of the counterweight 42 accompanying the rotation of the rotating shaft 24 is allowed.
  • an annular belt-like pedestal surface 48a that is substantially orthogonal to the axis of the rotary shaft 24 is formed as a step surface between the large-diameter inner peripheral surface 4b and the medium-diameter inner peripheral surface 4c of the front housing 4.
  • the pedestal surface 48a is a patent agent who is a patent attorney with a low educational background that does not have language skills and skills of the counterweight 42? Is a patented agent a low-level attorney without language skills or skills?
  • An arcuate plate 42a is positioned in close proximity.
  • a seal chamber 50 is defined in the front housing 4 from the inside of the medium diameter inner peripheral surface 4c to the inside of the small diameter inner peripheral surface 4d.
  • the seal chamber 50 is a space in which the lip portion of the lip seal 30 is positioned, and is substantially orthogonal to the axis of the rotary shaft 24 as a stepped surface between the medium diameter inner peripheral surface 4c and the small diameter inner peripheral surface 4d of the front housing 4.
  • An annular belt-like pedestal surface 50a is formed, and a bearing 26 mounted on the inner diameter inner peripheral surface 4c is positioned adjacent to the pedestal surface 50a.
  • FIG. 2 is an enlarged cross-sectional view of a part of the crank chamber 48 and the seal chamber 50
  • FIG. 3 is a plan view of the front housing 4 as viewed from the opening end 4a side.
  • the two communication holes 52 that communicate the crank chamber 48 and the seal chamber 50 with the front housing 4 are in symmetrical positions sandwiching the rotation shaft 24 on one diagonal line. It is penetrated.
  • Each communication hole 52 is inclined with respect to the axis of the rotary shaft 24 and extends linearly along the radial direction of the rotary shaft 24, and is opened in the pedestal surface 48 a in the crank chamber 48. It is formed at a position that is intermittently covered by the arc-shaped plate 42a.
  • each communication hole 52 is opened near the pedestal surface 50a of the inner diameter inner peripheral surface 4c.
  • the openings of the communication holes 52 on the crank chamber 48 side and the seal chamber 50 side are substantially positioned on the diameter line of the rotating shaft 24.
  • a guide groove (first guide groove) 54 is formed on the pedestal surface 50a, which is the inner wall of the seal chamber 50, from the communication hole 52 opened in the inner diameter inner peripheral surface 4c to the vicinity of the lip portion of the lip seal 30. Is recessed.
  • the guide groove 54 is formed with a bottom inclined in an arc shape with respect to the axis of the rotary shaft 24, and extends from the communication hole 52 opened in the inner diameter inner peripheral surface 4 c to the vicinity of the lip portion of the lip seal 30. It extends linearly along the radial direction of the rotating shaft 24.
  • the refrigerant containing lubricating oil also flows on the back surface 10c side of the end plate 10a of the movable scroll 10.
  • the lubricating oil that has flowed into the crank chamber 48 together with the refrigerant lubricates the rotation prevention mechanism 46, the bearing 40, the bearing 26, and thus the lip seal 30.
  • the refrigerant flowing into the crank chamber 48 has no language ability or technology due to the counterweight 42 turning in the direction of the two-dot chain line arrow.
  • Is a low-educated patent attorney a patent agent Is a patented agent a low-level attorney without language skills or skills? Compression is temporarily performed in a minute gap formed between the arc-shaped plate 42a and the pedestal surface 48a adjacent to the arc-shaped plate 42a.
  • the refrigerant compressed in the crank chamber 48 is pushed out by the differential pressure from the communication hole 52 to the seal chamber 50 having a lower pressure.
  • the refrigerant that has flowed into the seal chamber 50 from the crank chamber 48 through the communication hole 52 is guided to the lip seal 30 through the guide groove 54.
  • the lip seal 30 is lubricated by the lubricating oil contained in the refrigerant. Is suitably lubricated.
  • the refrigerant flowing into the seal chamber 50 passes through the bearing 26 and returns to the crank chamber 48.
  • the bearing 26 is preferably used by the lubricating oil contained in the refrigerant. Lubricated.
  • a lubricating oil circulation path is formed between the crank chamber 48 and the seal chamber 50.
  • the suction port 22 is provided on the outer peripheral side of the scroll unit 6 as in the compressor 1, the refrigerant introduced from the suction port 22 is contained in the scroll unit 6. Therefore, it is possible to expect to improve the compression efficiency of the refrigerant.
  • the compressor 1 having such a structure the flow rate of the refrigerant flowing into a portion of the front housing 4 away from the suction port 22 is reduced, and there has been a concern about deterioration of the lip seal 30 in particular.
  • the communication hole 52 and the guide groove 54 are formed in the front housing 4, and the lubricating oil circulation path is formed between the crank chamber 48 and the seal chamber 50, so that the lubricating oil is lip sealed. 30 can be actively guided. Therefore, the wear of the lip seal 30 can be greatly reduced while increasing the compression efficiency of the compressor 1, and as a result, the remaining tightening margin of the lip seal 30 with respect to the small diameter shaft portion 24b can be secured, and for a long period of time. The sealing performance of the compressor 1 can be maintained.
  • the numbers of the communication holes 52 and the guide grooves 54 are not particularly limited. For example, as shown in FIG. 4, two sets of the communication holes 52 and the guide grooves 54 are formed at two symmetrical positions sandwiching the rotating shaft 24 on two diagonal lines. Alternatively, as shown in FIG. 5, only one set of the communication hole 52 and the guide groove 54 may be formed.
  • Second Embodiment 6 is an enlarged cross-sectional view of a part of the crank chamber 48 and the seal chamber 50 according to the second embodiment of the present invention
  • FIG. 7 is a plan view of the front housing 4 of FIG. 6 viewed from the opening end 4a side. It is.
  • symbol may be attached
  • the pedestal surface 48 a of the front housing 4 of the present embodiment has two guide grooves (seconds) at a position sandwiching the rotation shaft 24 on the same diagonal as the guide groove 54 of the pedestal surface 50 a.
  • the guide groove 56 is recessed.
  • Each guide groove 56 extends linearly along the radial direction of the rotary shaft 24 from the vicinity of the large-diameter inner peripheral surface 4 b to the vicinity of the medium-diameter inner peripheral surface 4 c, and the communication hole 52 is formed at the bottom of the guide groove 56. ing.
  • the guide groove 56 similar to the guide groove 54 of the pedestal surface 50a is formed on the pedestal surface 48a at the opening position of the communication hole 52, so that the solid line arrows in FIGS.
  • the lubricating oil adhering to the pedestal surface 48 a can be efficiently guided from the guide groove 56 to the communication hole 52, and the lubricating oil can be further actively guided to the lip seal 30. Accordingly, while further improving the compression efficiency of the compressor 1, the wear of the lip seal 30 is further greatly reduced, the remaining tightening margin of the lip seal 30 is secured, and the sealing performance of the compressor 1 is maintained for a long period of time. Can do.
  • FIG. 8 is a plan view of the front housing 4 according to the third embodiment of the present invention as viewed from the opening end 4a side. This embodiment will be described as another embodiment of FIG. 5 shown in the first embodiment, and the same configuration as the first embodiment will be described in the specification or the drawings with the same name and the same reference numeral. May be omitted.
  • the front housing 4 is formed with one communication hole 58 that allows the crank chamber 48 and the seal chamber 50 to communicate with each other.
  • the communication hole 58 is inclined with respect to both the axial line and the radial direction of the rotating shaft 24 and extends linearly.
  • the inclination of the rotating shaft 24 with respect to the radial direction is a direction along the turning direction of the counterweight 42. That is, the opening of the communication hole 58 on the crank chamber 48 side and the seal chamber 50 side is positioned so as to be inclined with respect to the diameter line of the rotating shaft 24.
  • the communication hole 58 having a shape different from that of the communication hole 52 of the first and second embodiments is formed, so that it flows into the communication hole 58 as shown by the solid line arrow in FIG.
  • the lubricating oil can be guided to the lip seal 30 more efficiently and quickly using the force in the turning direction of the counterweight 42 acting on the refrigerant and the lubricating oil. Accordingly, while further improving the compression efficiency of the compressor 1, the wear of the lip seal 30 is further greatly reduced, the remaining tightening margin of the lip seal 30 is secured, and the sealing performance of the compressor 1 is maintained for a long period of time. Can do.
  • FIG. 9 is a side view showing a state in which the counterweight 60 according to the fourth embodiment of the present invention is attached to the rotary shaft 24.
  • symbol may be attached
  • the radial end surface 60a1 of each arc-shaped plate 60a is inclined with respect to the axis of the rotating shaft 24, and a flat inclined surface 62 is formed.
  • the inclined surface 62 is inclined from the crank pin 24c side toward the large-diameter shaft portion 24a in a direction approaching the axis, and is attached to the radial end surface 60a1 of each arc-shaped plate 60a as the counterweight 60 turns.
  • the lubricating oil is guided toward the communication hole 52 or the communication hole 58 as indicated by the solid line arrow.
  • the counterweight 60 has the inclined surface 62, so that the lubricating oil attached to the radial end surface 60a1 of each arc-shaped plate 60a is efficiently guided to the communication hole 52 or the communication hole 58.
  • the lubricating oil can be guided to the lip seal 30 more actively. Accordingly, while further improving the compression efficiency of the compressor 1, the wear of the lip seal 30 is further greatly reduced, the remaining tightening margin of the lip seal 30 is secured, and the sealing performance of the compressor 1 is maintained for a long period of time. Can do.
  • an inclined surface 64 may be formed by inclining only the radial end surface 60a1 of one arc-shaped plate 60a closest to the large-diameter shaft portion 24a.
  • the step surface 66 may be formed from the radial end surface 60a1 of each arcuate plate 60a by projecting one of each arcuate plate 60a in the radial direction of the rotating shaft 24. In these cases, as indicated by solid arrows in FIGS. 10 and 11, the lubricating oil adhering to the counterweight 60 can be efficiently flowed or dropped into the communication hole 52 or the communication hole 58 to be guided.
  • the present invention is not limited to the above-described embodiments, and various modifications can be made.
  • the engine-driven scroll compressor 1 incorporated in the vehicle air conditioner has been described.
  • the present invention can be applied to an integrated electric motor-driven scroll compressor and scroll compressors in various fields using various working fluids.
  • Scroll compressor Rear housing (housing) 2b Outer wall 4 Front housing (housing) 6 Scroll Unit 8 Fixed Scroll 10 Movable Scroll 22 Suction Port 24 Rotating Shaft 30 Lip Seal (Sealing Device) 42, 60 Counterweight 44 Crank mechanism 48 Crank chamber 50 Seal chamber 52 Communication hole 54 Guide groove (first guide groove) 56 Guide groove (second guide groove) 62, 64 Inclined surface 66 Step surface

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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 volutes (1), lequel compresseur comporte : une unité de volute (6) ; un mécanisme de vilebrequin (44) ; un boîtier (2, 4), dans lequel l'unité de volute (6) est logée, et qui a un orifice d'aspiration de réfrigérant (22) situé dans une surface périphérique externe (2b) située sur le côté périphérique externe de l'unité de volute (6) ; et un dispositif d'étanchéité (30) qui réalise une étanchéité entre un arbre rotatif (24) et le boîtier (2, 4). Le boîtier (2, 4) a : une chambre de vilebrequin (48), dans laquelle le mécanisme de vilebrequin (44) est positionné ; une chambre d'étanchéité (50), dans laquelle le dispositif d'étanchéité (30) est positionné ; un trou de communication (52, 58) qui relie la chambre de vilebrequin (48) et la chambre d'étanchéité (50) ; et une première rainure de guidage (54) qui s'étend à partir de l'ouverture du trou de communication (52, 58) dans la chambre d'étanchéité (50) à proximité du dispositif d'étanchéité (30).
PCT/JP2016/066651 2015-07-01 2016-06-03 Compresseur à volutes Ceased WO2017002536A1 (fr)

Priority Applications (2)

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JP6917845B2 (ja) * 2017-09-21 2021-08-11 サンデン・オートモーティブコンポーネント株式会社 スクロール型流体機械
CN114439747B (zh) * 2021-12-24 2023-11-10 珠海格力节能环保制冷技术研究中心有限公司 涡旋压缩机轴系润滑结构、涡旋压缩机、空调器
KR102684109B1 (ko) 2022-05-09 2024-07-12 엘지전자 주식회사 스크롤 압축기
JP2025150850A (ja) * 2024-03-27 2025-10-09 株式会社豊田自動織機 スクロール型圧縮機

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US20180187679A1 (en) 2018-07-05
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JP6633305B2 (ja) 2020-01-22

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