US20180187679A1 - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
- Publication number
- US20180187679A1 US20180187679A1 US15/740,195 US201615740195A US2018187679A1 US 20180187679 A1 US20180187679 A1 US 20180187679A1 US 201615740195 A US201615740195 A US 201615740195A US 2018187679 A1 US2018187679 A1 US 2018187679A1
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- United States
- Prior art keywords
- scroll
- rotary shaft
- communication hole
- counterweight
- 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.)
- Abandoned
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Classifications
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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 particularly to a scroll compressor for use in a refrigeration circuit of an air conditioner for vehicles.
- Patent Document 1 discloses a scroll compressor including: a fixed scroll and a movable scroll accommodated in a housing, the housing supporting a rotary shaft via a bearing; and a shaft seal mechanism fitted between the rotary shaft and the housing, in which a communication passage for communicating the seal chamber with the side of a suction chamber of refrigerant is formed as lubricating means of the shaft seal mechanism.
- Patent Document 1 Japanese Patent No. 2868998
- a compressor has a structure in which a suction port is provided on an outer peripheral side of a scroll unit in an outer peripheral wall of a housing, since a refrigerant introduced from the suction port can be immediately sucked into the scroll unit, improvement of compression efficiency of the refrigerant can be expected.
- the flow rate of the refrigerant flowing into a portion apart from the suction port in the housing is reduced and thus, particularly, deterioration of lubrication of a shaft seal mechanism or a lip seal which is a sealing device, has conventionally been a concern.
- the present invention has been made in view of the above-mentioned problems, and has its object to provide a scroll compressor which allows to significantly reduce wear of the sealing device while enhancing the compression efficiency of the compressor by actively guiding lubricating oil to the sealing device and, by extension, ensures a residual fastening margin of the sealing device with respect to the rotary shaft, thereby maintaining the sealing performance of the compressor over a long period of time.
- a scroll compressor of the present invention includes: a scroll unit for compressing a refrigerant by orbiting of a movable scroll relative to a fixed scroll; a crank mechanism for converting rotary motion of a rotary shaft into orbiting motion of the movable scroll and transferring the orbiting motion; a housing for accommodating the scroll unit, the housing including a suction port of the refrigerant on an outer peripheral wall located on an outer peripheral side of the scroll unit; and a sealing device for sealing between the housing and the rotary shaft, wherein the housing includes: a crank chamber in which the crank mechanism is positioned, a seal chamber in which the sealing device is positioned, a communication hole for communicating the crank chamber with the seal chamber, and a first guide groove extending from an opening of the communication hole in the seal chamber to a vicinity of the sealing device.
- the housing further includes a second guide groove in which an opening of the communication hole in the crank chamber is positioned.
- the crank mechanism includes a counterweight attached to the rotary shaft, and the communication hole is formed at a position which is intermittently covered by the counterweight as the counterweight circles.
- the communication hole is inclined along a circling direction of the counterweight with respect to a radial direction of the rotary shaft.
- the counterweight has an inclined surface inclined with respect to an axis of the rotary shaft.
- the counterweight has a stepped surface protruding in a radial direction of the rotary shaft.
- the scroll compressor of the present invention it is possible to significantly reduce wear of the sealing device while enhancing the compression efficiency of the compressor by actively guiding lubricating oil to the sealing device and, by extension, ensure a residual fastening margin of the sealing device with respect to the rotary shaft, thereby maintaining the sealing performance of the compressor over a long period of time.
- FIG. 1 is a vertical cross-sectional view of a scroll compressor according to a first embodiment of the present invention.
- FIG. 2 is a vertical cross-sectional view of a scroll compressor with parts of the crank chamber and the seal chamber of FIG. 1 being enlarged.
- FIG. 3 is a plan view of the front housing of FIG. 1 as viewed from its opening end side.
- FIG. 4 is a plan view showing a variant of FIG. 3 .
- FIG. 5 is a plan view showing a further variant of FIG. 3 .
- FIG. 6 is a vertical cross-sectional view of a scroll compressor with parts of the crank chamber and the seal chamber according to the second embodiment of the present invention being enlarged.
- FIG. 7 is a plan view of the front housing of FIG. 6 as viewed from its opening end side.
- FIG. 8 is a plan view of a front housing according to a third embodiment of the present invention as viewed from its opening end side.
- FIG. 9 is a side view showing a counterweight according to a fourth embodiment of the present invention, with the counterweight being mounted on a rotary shaft.
- FIG. 10 is a side view showing a variant of FIG. 9 .
- FIG. 11 is a side view illustrating a further variant of FIG. 9 .
- FIG. 1 is a vertical cross-sectional view of a scroll compressor 1 according to a first embodiment of the present invention.
- This compressor 1 is incorporated, for example, in a refrigeration circuit of a vehicle air-conditioner mounted on a vehicle and is used for compressing refrigerant circulating in a 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 is made up of a fixed scroll 8 fixed to the rear housing 2 , and a movable scroll 10 assembled so as to engage with the fixed scroll 8 .
- the fixed scroll 8 includes an end plate 8 a , and a fixed spiral body 8 b integrally formed with the end plate 8 a
- the movable scroll 10 includes an end plate 10 a , and a movable spiral body 10 b integrally molded with the end plate 10 a , and the fixed spiral body 8 b and the movable spiral body 10 b are engaged with each other.
- An ejection chamber 12 is formed between an end wall 2 a of the rear housing 2 and the fixed scroll 8 in the rear housing 2 .
- This ejection chamber 12 can communicate an ejection hole 14 formed in the end plate 8 a of the fixed scroll 8 with a compression chamber 18 formed between the fixed scroll 8 and the movable scroll 10 via an ejection valve 16 of a reed valve type.
- an ejection port 20 is formed at a position proximal to the end wall 2 a , and the ejection chamber 12 is communicated with a refrigerant circulation passage of the refrigeration circuit via the ejection port 20 .
- a suction port 22 of the refrigerant is provided on the outer peripheral side of the scroll unit 6 in the outer peripheral wall 2 b of the rear housing 2 , and the refrigerant introduced via the suction port 22 from the refrigerant circulation passage is quickly sucked into the scroll unit 6 .
- the rotary shaft 24 is disposed in the front housing 4 , and the rotary shaft 24 has a large-diameter shaft part 24 a and a small-diameter shaft part 24 b . Moreover, a large-diameter inner peripheral surface 4 b , an intermediate-diameter inner peripheral surface 4 c , and a small-diameter inner peripheral surface 4 d are formed in the order from an opening end 4 a located on the rear housing 2 side in the front housing 4 by stepwisely reducing the diameter of the inner periphery thereof.
- a large-diameter shaft part 24 a is rotatably supported on an intermediate-diameter inner peripheral surface 4 c of the front housing 4 via a bearing 26 which is a needle bearing
- the small-diameter shaft part 24 b is rotatably supported on the small-diameter inner peripheral surface 4 d of the front housing 4 via a bearing 28 which is a ball bearing
- a lip seal (sealing device) 30 is disposed between the small-diameter shaft part 24 b and the small-diameter inner peripheral surface 4 d of the front housing 4 .
- the outer periphery side of the lip seal 30 is mounted to the small-diameter inner peripheral surface 4 d , and functions as a sealing device by the lip part located on the inner periphery side coming into contact with the small-diameter shaft part 24 b during rotation, to partition the inside of the front housing 4 in an airtight manner.
- the small-diameter shaft part 24 b of the rotary shaft 24 protrudes from the front housing 4 , and this protruding end is interconnected with a drive pulley 32 having an electromagnetic clutch built-in.
- the drive pulley 32 is rotatably supported on the front housing 4 via a bearing 34 which is a ball bearing.
- the drive pulley 32 is connected to an output pulley on the side of the engine of the vehicle via a belt, and receives the power of the engine, thereby being rotated.
- a crankpin 24 c is protruded toward the movable scroll 10 from the large-diameter shaft part 24 a of the rotary shaft 24 .
- the crankpin 24 c which is provided at a position eccentric from the axial center of the rotary shaft 24 , is inserted and fitted into a crankpin hole 38 drilled in an eccentric bush 36 .
- the crankpin 24 c supports the eccentric bush 36 by its base end part 24 c 1 .
- the eccentric bush 36 supports a boss 41 of the movable scroll 10 via a bearing 40 which is a needle bearing.
- a counterweight 42 is attached to the crankpin 24 c so as to be interposed between the eccentric bush 36 and the large-diameter shaft part 24 a .
- the counterweight 42 which is made up by superposing a plurality of large and small arc-shaped plates 42 a in an axial direction of the rotary shaft 24 , cancels centrifugal force acting on the rotary shaft 24 as the movable scroll 10 orbits, thereby balancing the orbiting of the movable scroll 10 .
- crank mechanism 44 which converts rotary motion of the rotary shaft 24 into orbiting motion of the movable scroll 10 and transfers the orbiting motion, is made up of the above described crankpin 24 c , eccentric bush 36 , boss 41 , and counterweight 42 .
- a rotation prevention mechanism 46 of a ball coupling type is disposed between an end plate 10 a of the movable scroll 10 and an 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 orbiting motion of the movable scroll 10 with respect to the fixed scroll 8 .
- the movable scroll 10 undergoes orbiting motion with respect to the fixed scroll 8 , the refrigerant sucked from the refrigerant circulation passage via the suction port 22 is introduced into the scroll unit 6 , and the fixed scroll 8 and the movable scroll 10 cooperate.
- a compression chamber 18 of refrigerant including lubricating oil is partitioned and formed between the fixed spiral body 8 b and the movable spiral body 10 b .
- the volume thereof is reduced while the movable spiral body 10 b is moved toward the center of the fixed spiral body 8 b by the orbiting motion of the movable scroll 10 with respect to the fixed scroll 8 , and thus the refrigerant is compressed.
- the compressed refrigerant is ejected to the ejection chamber 12 via the ejection hole 14 , and fed to the refrigerant circulation passage from the ejection port 20 .
- a crank chamber 48 is partitioned inside a large-diameter inner peripheral surface 4 b in the front housing 4 .
- the crank chamber 48 is a space in the front housing 4 , in which the crank mechanism 44 is positioned, and smooth orbiting of the counterweight 42 is allowed as the rotary shaft 24 rotates.
- an annulus-shaped base surface 48 a which substantially intersects at right angles with the axis of the rotary shaft 24 is formed as a stepped surface between the large-diameter inner peripheral surface 4 b and the intermediate-diameter inner peripheral surface 4 c of the front housing 4 , and an arc-shaped plate 42 a of the counterweight 42 is positioned in proximity to the base surface 48 a.
- a seal chamber 50 is partitioned from inner side of the intermediate-diameter inner peripheral surface 4 c to the inner side of the small-diameter inner peripheral surface 4 d .
- the seal chamber 50 is a space in which a lip part of the lip seal 30 is positioned, and an annulus-shaped base surface 50 a which substantially intersects at right angles with the axis of the rotary shaft 24 is formed as a stepped surface between the intermediate-diameter inner peripheral surface 4 c and the small-diameter inner peripheral surface 4 d of the front housing 4 , and a bearing 26 mounted to the intermediate-diameter inner peripheral surface 4 c is positioned in proximity to the base surface 50 a.
- FIG. 2 is an enlarged cross-sectional view of parts 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 4 a side thereof.
- two communication holes 52 which communicate the crank chamber 48 with the seal chamber 50 are penetrated through in the front housing 4 at symmetric positions on one diagonal line interposing the rotary shaft 24 .
- Each communication hole 52 is formed at a position to extend linearly inclined with respect to the axis of the rotary shaft 24 and along the radial direction of the rotary shaft 24 , to be opened in the base surface 48 a in the crank chamber 48 , and to be intermittently covered by the arc-shaped plate 42 a as the counterweight 42 circles.
- each communication hole 52 is opened in the vicinity of the base surface 50 a of the intermediate-diameter inner peripheral surface 4 c .
- the openings on the crank chamber 48 side and the seal chamber 50 side of each communication hole 52 are substantially positioned on a diameter line of the rotary shaft 24 .
- a guide groove (first guide groove) 54 is concaved from the communication hole 52 opened in the intermediate-diameter inner peripheral surface 4 c to the vicinity of the lip part of the lip seal 30 in the base surface 50 a which is an inner wall of the seal chamber 50 .
- the guide groove 54 which is formed so as to have a bottom which is inclined in an arc shape with respect to the axis of the rotary shaft 24 , extends linearly along the radial direction of the rotary shaft 24 from the communication hole 52 opened in the intermediate-diameter inner peripheral surface 4 c to the vicinity of the lip part of the lip seal 30 .
- refrigerant including lubricating oil will also flow to the back surface 10 c side of the end plate 10 a of the movable scroll 10 .
- the lubricating oil which has flown into the crank chamber 48 with the refrigerant lubricates the rotation prevention mechanism 46 , the bearing 40 , the bearing 26 , and the lip seal 30 .
- the refrigerant that has flown into the crank chamber 48 is temporarily compressed in a minute gap formed between the arc-shaped plate 42 a and the base surface 48 a proximal to the arc-shaped plate 42 a as a result of the counterweight 42 circling in the two-dot-chain line arrow direction.
- the refrigerant that has been compressed in the crank chamber 48 is pushed out by differential pressure from the communication hole 52 into the seal chamber 50 in which pressure will be lower.
- the refrigerant that has flown into seal chamber 50 from the crank chamber 48 through the communication hole 52 is guided to the lip seal 30 passing through the guide groove 54 , and in this occasion, the lip seal 30 is appropriately lubricated by the lubricating oil contained in the refrigerant.
- the refrigerant that has flown into the seal chamber 50 is returned to the crank chamber 48 through the bearing 26 , and in that occasion, the bearing 26 is appropriately lubricated by the lubricating oil contained in the refrigerant.
- a lubricating oil recirculation passage is formed between the crank chamber 48 and the seal chamber 50 .
- the numbers of the communication hole 52 and the guide grooves 54 are not particularly limited, and for example, as shown in FIG. 4 , two sets of the communication hole 52 and the guide groove 54 may be formed at symmetrical positions interposing the rotary shaft 24 on the two diagonal lines, or as shown in FIG. 5 , only one set of the communication hole 52 and the guide groove 54 may be formed.
- FIG. 6 is an enlarged cross-sectional view of parts of the crank chamber 48 and the seal chamber 50 according to a second embodiment of the present invention
- FIG. 7 is a plan view of the front housing 4 of FIG. 6 as viewed from its opening end 4 a side. Note that regarding the same components as those of the first embodiment, description thereof may be omitted by giving them the same names and the reference symbols in the specification or the drawings.
- two guide grooves (second guide grooves) 56 are concaved at positions interposing the rotary shaft 24 on the same diagonal line as that with the guide groove 54 of the base surface 50 a .
- 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 intermediate-diameter inner peripheral surface 4 c , and the communication hole 52 is formed in the bottom of the guide groove 56 .
- FIG. 8 is a plan view of a front housing 4 according to a third embodiment of the present invention as viewed from its opening end 4 a side. Note that the present embodiment will be described as a variant of FIG. 5 shown in the first embodiment, and regarding the same components as those of the first embodiment, description thereof may be omitted by giving them the same names and the reference symbols in the specification or the drawings.
- a communication hole 58 that communicates the crank chamber 48 with the seal chamber 50 is formed in the front housing 4 .
- This communication hole 58 extends linearly inclined with respect to both the axis and radial directions of the rotary shaft 24 as shown by broken lines. Inclination with respect to the radial direction of the rotary shaft 24 is the direction along the circling direction of the counterweight 42 . That is, the openings of the crank chamber 48 side and the seal chamber 50 side of the communication hole 58 are positioned included with respect to the diameter line of the rotary shaft 24 .
- FIG. 9 is a side view showing a counterweight 60 according to a fourth embodiment of the present invention in a state of being mounted to the rotary shaft 24 . Note that regarding the same components as those of any of the first to the third embodiments, description thereof may be omitted by giving them the same names and the reference symbols in the specification or the drawings.
- the counterweight 60 of the present embodiment is configured such that a radial end surface 60 a 1 of each arc-shaped plate 60 a is inclined with respect to the axis of the rotary shaft 24 and forms a flush inclined surface 62 .
- This inclined surface 62 which is inclined in a closing direction to the axis from the crankpin 24 c side toward the large-diameter shaft part 24 a , guides the lubricating oil adhered to the radial end surface 60 a 1 of each arc-shaped plate 60 a toward the communication hole 52 or the communication hole 58 as shown solid arrows, as the counterweight 60 circles.
- the counterweight 60 being provided with the inclined surface 62 in the present embodiment, it is possible to effectively guide the lubricating oil adhered to the radial end surface 60 a 1 of each arc-shaped plate 60 a into the communication hole 52 or the communication hole 58 , and more actively guide the lubricating oil to the lip seal 30 . Therefore, it is possible to realize significant reduction of wear of the lip seal 30 and ensure a residual fastening margin of the lip seal 30 while improving the compression efficiency of the compressor 1 , thereby maintaining the sealing performance of the compressor 1 over a long period of time.
- an inclined surface 64 in which only the radial end surface 60 a 1 of the arc-shaped plate 60 a closest to the large-diameter shaft part 24 a is inclined may be formed.
- a stepped surface 66 may be formed from the radial end surface 60 a 1 of each arc-shaped plate 60 a by causing one of the each arc-shaped plate 60 a to protrude in the radial direction of the rotary shaft 24 .
- solid arrows in FIGS. 10 and 11 it is possible to effectively guide the lubricating oil adhered to the counterweight 60 to flow or drip into the communication hole 52 or the communication hole 58 .
- an engine-driven scroll compressor 1 which is incorporated in an air conditioner for vehicles has been described.
- the present invention can be applied to integrated electric-motor-driven scroll compressors and general scroll compressors in various fields which use various working fluids.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
A scroll compressor 1 includes: a scroll unit 6; a crank mechanism 44; a housing 2, 4 in which the scroll unit 6 is accommodated and which has a suction port 22 of refrigerant provided in an outer peripheral wall 2 b located on the outer peripheral side of the scroll unit 6; and a sealing device 30 which seals between the housing 2, 4 and a rotary shaft 24, wherein the housing 2, 4 includes: a crank chamber 48 in which the crank mechanism 44 is positioned; a seal chamber 50 in which the sealing device 30 is positioned; a communication hole 52, 58 which communicates the crank chamber 48 with the seal chamber 50; and a first guide groove 54 which extends from an opening of the communication hole 52, 58 in the seal chamber 50 to the vicinity of the sealing device 30.
Description
- The present invention relates to a scroll compressor, and particularly to a scroll compressor for use in a refrigeration circuit of an air conditioner for vehicles.
- Patent Document 1 discloses a scroll compressor including: a fixed scroll and a movable scroll accommodated in a housing, the housing supporting a rotary shaft via a bearing; and a shaft seal mechanism fitted between the rotary shaft and the housing, in which a communication passage for communicating the seal chamber with the side of a suction chamber of refrigerant is formed as lubricating means of the shaft seal mechanism.
- Patent Document 1: Japanese Patent No. 2868998
- When a compressor has a structure in which a suction port is provided on an outer peripheral side of a scroll unit in an outer peripheral wall of a housing, since a refrigerant introduced from the suction port can be immediately sucked into the scroll unit, improvement of compression efficiency of the refrigerant can be expected. On the other hand, in the compressor having such a structure, the flow rate of the refrigerant flowing into a portion apart from the suction port in the housing is reduced and thus, particularly, deterioration of lubrication of a shaft seal mechanism or a lip seal which is a sealing device, has conventionally been a concern.
- In a case such as Patent Document 1, in which a communication passage for communicating the seal chamber with the side of the suction chamber of refrigerant is simply formed, the communication passage will become long when the lip seal is away from the suction port, making it difficult to sufficiently supply lubricating oil to the lip seal.
- The present invention has been made in view of the above-mentioned problems, and has its object to provide a scroll compressor which allows to significantly reduce wear of the sealing device while enhancing the compression efficiency of the compressor by actively guiding lubricating oil to the sealing device and, by extension, ensures a residual fastening margin of the sealing device with respect to the rotary shaft, thereby maintaining the sealing performance of the compressor over a long period of time.
- In order to achieve the above described object, a scroll compressor of the present invention includes: a scroll unit for compressing a refrigerant by orbiting of a movable scroll relative to a fixed scroll; a crank mechanism for converting rotary motion of a rotary shaft into orbiting motion of the movable scroll and transferring the orbiting motion; a housing for accommodating the scroll unit, the housing including a suction port of the refrigerant on an outer peripheral wall located on an outer peripheral side of the scroll unit; and a sealing device for sealing between the housing and the rotary shaft, wherein the housing includes: a crank chamber in which the crank mechanism is positioned, a seal chamber in which the sealing device is positioned, a communication hole for communicating the crank chamber with the seal chamber, and a first guide groove extending from an opening of the communication hole in the seal chamber to a vicinity of the sealing device.
- Preferably, the housing further includes a second guide groove in which an opening of the communication hole in the crank chamber is positioned.
- Preferably, the crank mechanism includes a counterweight attached to the rotary shaft, and the communication hole is formed at a position which is intermittently covered by the counterweight as the counterweight circles.
- Preferably, the communication hole is inclined along a circling direction of the counterweight with respect to a radial direction of the rotary shaft.
- Preferably, the counterweight has an inclined surface inclined with respect to an axis of the rotary shaft.
- Preferably, the counterweight has a stepped surface protruding in a radial direction of the rotary shaft.
- According to the scroll compressor of the present invention, it is possible to significantly reduce wear of the sealing device while enhancing the compression efficiency of the compressor by actively guiding lubricating oil to the sealing device and, by extension, ensure a residual fastening margin of the sealing device with respect to the rotary shaft, thereby maintaining the sealing performance of the compressor over a long period of time.
-
FIG. 1 is a vertical cross-sectional view of a scroll compressor according to a first embodiment of the present invention. -
FIG. 2 is a vertical cross-sectional view of a scroll compressor with parts of the crank chamber and the seal chamber ofFIG. 1 being enlarged. -
FIG. 3 is a plan view of the front housing ofFIG. 1 as viewed from its opening end side. -
FIG. 4 is a plan view showing a variant ofFIG. 3 . -
FIG. 5 is a plan view showing a further variant ofFIG. 3 . -
FIG. 6 is a vertical cross-sectional view of a scroll compressor with parts of the crank chamber and the seal chamber according to the second embodiment of the present invention being enlarged. -
FIG. 7 is a plan view of the front housing ofFIG. 6 as viewed from its opening end side. -
FIG. 8 is a plan view of a front housing according to a third embodiment of the present invention as viewed from its opening end side. -
FIG. 9 is a side view showing a counterweight according to a fourth embodiment of the present invention, with the counterweight being mounted on a rotary shaft. -
FIG. 10 is a side view showing a variant ofFIG. 9 . -
FIG. 11 is a side view illustrating a further variant ofFIG. 9 . - Hereinafter, each embodiment of the present invention will be described based on the drawings.
-
FIG. 1 is a vertical cross-sectional view of a scroll compressor 1 according to a first embodiment of the present invention. This compressor 1 is incorporated, for example, in a refrigeration circuit of a vehicle air-conditioner mounted on a vehicle and is used for compressing refrigerant circulating in a 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 therear housing 2. Thescroll unit 6 is made up of afixed scroll 8 fixed to therear housing 2, and amovable scroll 10 assembled so as to engage with thefixed scroll 8. Thefixed scroll 8 includes anend plate 8 a, and a fixedspiral body 8 b integrally formed with theend plate 8 a, and themovable scroll 10 includes anend plate 10 a, and a movablespiral body 10 b integrally molded with theend plate 10 a, and the fixedspiral body 8 b and the movablespiral body 10 b are engaged with each other. - An
ejection chamber 12 is formed between anend wall 2 a of therear housing 2 and thefixed scroll 8 in therear housing 2. Thisejection chamber 12 can communicate anejection hole 14 formed in theend plate 8 a of thefixed scroll 8 with acompression chamber 18 formed between thefixed scroll 8 and themovable scroll 10 via anejection valve 16 of a reed valve type. In the outerperipheral wall 2 b of therear housing 2, anejection port 20 is formed at a position proximal to theend wall 2 a, and theejection chamber 12 is communicated with a refrigerant circulation passage of the refrigeration circuit via theejection port 20. - Moreover, a
suction port 22 of the refrigerant is provided on the outer peripheral side of thescroll unit 6 in the outerperipheral wall 2 b of therear housing 2, and the refrigerant introduced via thesuction port 22 from the refrigerant circulation passage is quickly sucked into thescroll unit 6. - On the other hand, the
rotary shaft 24 is disposed in thefront housing 4, and therotary shaft 24 has a large-diameter shaft part 24 a and a small-diameter shaft part 24 b. Moreover, a large-diameter innerperipheral surface 4 b, an intermediate-diameter innerperipheral surface 4 c, and a small-diameter innerperipheral surface 4 d are formed in the order from anopening end 4 a located on therear housing 2 side in thefront housing 4 by stepwisely reducing the diameter of the inner periphery thereof. - A large-
diameter shaft part 24 a is rotatably supported on an intermediate-diameter innerperipheral surface 4 c of thefront housing 4 via abearing 26 which is a needle bearing, and the small-diameter shaft part 24 b is rotatably supported on the small-diameter innerperipheral surface 4 d of thefront housing 4 via abearing 28 which is a ball bearing. Moreover, a lip seal (sealing device) 30 is disposed between the small-diameter shaft part 24 b and the small-diameter innerperipheral surface 4 d of thefront housing 4. The outer periphery side of thelip seal 30 is mounted to the small-diameter innerperipheral surface 4 d, and functions as a sealing device by the lip part located on the inner periphery side coming into contact with the small-diameter shaft part 24 b during rotation, to partition the inside of thefront housing 4 in an airtight manner. - The small-
diameter shaft part 24 b of therotary shaft 24 protrudes from thefront housing 4, and this protruding end is interconnected with adrive pulley 32 having an electromagnetic clutch built-in. Thedrive pulley 32 is rotatably supported on thefront housing 4 via abearing 34 which is a ball bearing. Thedrive pulley 32 is connected to an output pulley on the side of the engine of the vehicle via a belt, and receives the power of the engine, thereby being rotated. - On the other hand, a
crankpin 24 c is protruded toward themovable scroll 10 from the large-diameter shaft part 24 a of therotary shaft 24. Thecrankpin 24 c, which is provided at a position eccentric from the axial center of therotary shaft 24, is inserted and fitted into acrankpin hole 38 drilled in aneccentric bush 36. The crankpin 24 c supports theeccentric bush 36 by itsbase end part 24 c 1. Moreover, theeccentric bush 36 supports aboss 41 of themovable scroll 10 via abearing 40 which is a needle bearing. - Moreover, a
counterweight 42 is attached to thecrankpin 24 c so as to be interposed between theeccentric bush 36 and the large-diameter shaft part 24 a. Thecounterweight 42, which is made up by superposing a plurality of large and small arc-shaped plates 42 a in an axial direction of therotary shaft 24, cancels centrifugal force acting on therotary shaft 24 as the movable scroll 10 orbits, thereby balancing the orbiting of themovable scroll 10. - In this way, a
crank mechanism 44 which converts rotary motion of therotary shaft 24 into orbiting motion of themovable scroll 10 and transfers the orbiting motion, is made up of the above describedcrankpin 24 c,eccentric bush 36,boss 41, andcounterweight 42. - Moreover, a
rotation prevention mechanism 46 of a ball coupling type is disposed between anend plate 10 a of themovable scroll 10 and anopening end 4 a of thefront housing 4. Therotation prevention mechanism 46 prevents the rotation of themovable scroll 10 without hindering the orbiting motion of themovable scroll 10 with respect to thefixed scroll 8. - In the compressor 1 as thus configured, when an electromagnetic clutch in the
drive pulley 32 is ON-operated during driving of engine, and therotary shaft 24 is rotated together with thedrive pulley 32, theeccentric bush 36 into which thecrankpin 24 c is fitted rotates. As a result, orbiting motion is imparted to themovable scroll 10 via theboss 41 with rotation being prevented by therotation prevention mechanism 46. - When the
movable scroll 10 undergoes orbiting motion with respect to thefixed scroll 8, the refrigerant sucked from the refrigerant circulation passage via thesuction port 22 is introduced into thescroll unit 6, and thefixed scroll 8 and themovable scroll 10 cooperate. As a result, acompression chamber 18 of refrigerant including lubricating oil is partitioned and formed between the fixedspiral body 8 b and the movablespiral body 10 b. In thecompression chamber 18, the volume thereof is reduced while themovable spiral body 10 b is moved toward the center of the fixedspiral body 8 b by the orbiting motion of themovable scroll 10 with respect to the fixedscroll 8, and thus the refrigerant is compressed. The compressed refrigerant is ejected to theejection chamber 12 via theejection hole 14, and fed to the refrigerant circulation passage from theejection port 20. - Here, a
crank chamber 48 is partitioned inside a large-diameter innerperipheral surface 4 b in thefront housing 4. Thecrank chamber 48 is a space in thefront housing 4, in which thecrank mechanism 44 is positioned, and smooth orbiting of thecounterweight 42 is allowed as therotary shaft 24 rotates. Further, in thecrank chamber 48, an annulus-shapedbase surface 48 a which substantially intersects at right angles with the axis of therotary shaft 24 is formed as a stepped surface between the large-diameter innerperipheral surface 4 b and the intermediate-diameter innerperipheral surface 4 c of thefront housing 4, and an arc-shapedplate 42 a of thecounterweight 42 is positioned in proximity to thebase surface 48 a. - On the other hand, in the
front housing 4, aseal chamber 50 is partitioned from inner side of the intermediate-diameter innerperipheral surface 4 c to the inner side of the small-diameter innerperipheral surface 4 d. Theseal chamber 50 is a space in which a lip part of thelip seal 30 is positioned, and an annulus-shapedbase surface 50 a which substantially intersects at right angles with the axis of therotary shaft 24 is formed as a stepped surface between the intermediate-diameter innerperipheral surface 4 c and the small-diameter innerperipheral surface 4 d of thefront housing 4, and abearing 26 mounted to the intermediate-diameter innerperipheral surface 4 c is positioned in proximity to thebase surface 50 a. -
FIG. 2 is an enlarged cross-sectional view of parts of thecrank chamber 48 and theseal chamber 50, andFIG. 3 is a plan view of thefront housing 4 as viewed from the openingend 4 a side thereof. As shown inFIGS. 2 and 3 , in the present embodiment, twocommunication holes 52 which communicate thecrank chamber 48 with theseal chamber 50 are penetrated through in thefront housing 4 at symmetric positions on one diagonal line interposing therotary shaft 24. Eachcommunication hole 52 is formed at a position to extend linearly inclined with respect to the axis of therotary shaft 24 and along the radial direction of therotary shaft 24, to be opened in thebase surface 48 a in thecrank chamber 48, and to be intermittently covered by the arc-shapedplate 42 a as thecounterweight 42 circles. - On the other hand, in the
seal chamber 50, eachcommunication hole 52 is opened in the vicinity of thebase surface 50 a of the intermediate-diameter innerperipheral surface 4 c. The openings on thecrank chamber 48 side and theseal chamber 50 side of eachcommunication hole 52 are substantially positioned on a diameter line of therotary shaft 24. Further, a guide groove (first guide groove) 54 is concaved from thecommunication hole 52 opened in the intermediate-diameter innerperipheral surface 4 c to the vicinity of the lip part of thelip seal 30 in thebase surface 50 a which is an inner wall of theseal chamber 50. Theguide groove 54, which is formed so as to have a bottom which is inclined in an arc shape with respect to the axis of therotary shaft 24, extends linearly along the radial direction of therotary shaft 24 from thecommunication hole 52 opened in the intermediate-diameter innerperipheral surface 4 c to the vicinity of the lip part of thelip seal 30. - Here, when the refrigerant flows from the
suction port 22 toward thecompression chamber 18 side as themovable scroll 10 undergoes orbiting motion, refrigerant including lubricating oil will also flow to theback surface 10 c side of theend plate 10 a of themovable scroll 10. Moreover, the lubricating oil which has flown into thecrank chamber 48 with the refrigerant lubricates therotation prevention mechanism 46, thebearing 40, thebearing 26, and thelip seal 30. - Specifically, as shown by solid arrows in
FIGS. 2 and 3 , the refrigerant that has flown into thecrank chamber 48 is temporarily compressed in a minute gap formed between the arc-shapedplate 42 a and thebase surface 48 a proximal to the arc-shapedplate 42 a as a result of thecounterweight 42 circling in the two-dot-chain line arrow direction. The refrigerant that has been compressed in thecrank chamber 48 is pushed out by differential pressure from thecommunication hole 52 into theseal chamber 50 in which pressure will be lower. - The refrigerant that has flown into
seal chamber 50 from thecrank chamber 48 through thecommunication hole 52 is guided to thelip seal 30 passing through theguide groove 54, and in this occasion, thelip seal 30 is appropriately lubricated by the lubricating oil contained in the refrigerant. On the other hand, as shown by a broken line inFIGS. 2 and 3 , the refrigerant that has flown into theseal chamber 50 is returned to the crankchamber 48 through thebearing 26, and in that occasion, thebearing 26 is appropriately lubricated by the lubricating oil contained in the refrigerant. Thus, a lubricating oil recirculation passage is formed between thecrank chamber 48 and theseal chamber 50. - As so far described, according to the present embodiment, in the case of a structure in which a
suction port 22 is provided on the outer peripheral side of thescroll unit 6 as in the compressor 1, since the refrigerant introduced from thesuction port 22 will be able to be sucked into thescroll unit 6 immediately, improvement in compression efficiency of refrigerant can be expected. On the other hand, in the compressor 1 of such a structure, the flow rate of the refrigerant flowing into a portion apart from thesuction port 22 in thefront housing 4 is reduced, and in particular, deterioration of lubrication of thelip seal 30 has conventionally been a concern. - Even in such a case, as a result of forming the
communication hole 52 and theguide groove 54 in thefront housing 4, thereby forming a lubricating oil circulation passage between thecrank chamber 48 and theseal chamber 50, it is made possible to actively guide the lubricating oil to thelip seal 30. Therefore, it is possible to significantly reduce wear of thelip seal 30 while improving compression efficiency of the compressor 1, and by extension, to ensure a residual fastening margin of thelip seal 30 with respect to the small-diameter shaft part 24 b, thereby maintaining the sealing performance of the compressor 1 over a long period of time. Note that the numbers of thecommunication hole 52 and theguide grooves 54 are not particularly limited, and for example, as shown inFIG. 4 , two sets of thecommunication hole 52 and theguide groove 54 may be formed at symmetrical positions interposing therotary shaft 24 on the two diagonal lines, or as shown inFIG. 5 , only one set of thecommunication hole 52 and theguide groove 54 may be formed. -
FIG. 6 is an enlarged cross-sectional view of parts of thecrank chamber 48 and theseal chamber 50 according to a second embodiment of the present invention, andFIG. 7 is a plan view of thefront housing 4 ofFIG. 6 as viewed from its openingend 4 a side. Note that regarding the same components as those of the first embodiment, description thereof may be omitted by giving them the same names and the reference symbols in the specification or the drawings. - As shown in
FIGS. 6 and 7 , in thebase surface 48 a of thefront housing 4 of the present embodiment, two guide grooves (second guide grooves) 56 are concaved at positions interposing therotary shaft 24 on the same diagonal line as that with theguide groove 54 of thebase surface 50 a. Eachguide groove 56 extends linearly along the radial direction of therotary shaft 24 from the vicinity of the large-diameter innerperipheral surface 4 b to the vicinity of the intermediate-diameter innerperipheral surface 4 c, and thecommunication hole 52 is formed in the bottom of theguide groove 56. - Thus, in the present embodiment, as a result of forming the
guide groove 56 similar to theguide groove 54 of thebase surface 50 a at the opening position of thecommunication hole 52 in thebase surface 48 a, it is possible to effectively guide the lubricating oil adhered to thebase surface 48 a from theguide groove 56 to thecommunication hole 52, as shown by solid arrows inFIGS. 6 and 7 , thus further actively guiding the lubricating oil to thelip seal 30. Therefore, it is possible to realize significant reduction of wear of thelip seal 30 and ensure a residual fastening margin of thelip seal 30 while improving the compression efficiency of the compressor 1, thereby maintaining the sealing performance of the compressor 1 over a long period of time. -
FIG. 8 is a plan view of afront housing 4 according to a third embodiment of the present invention as viewed from its openingend 4 a side. Note that the present embodiment will be described as a variant ofFIG. 5 shown in the first embodiment, and regarding the same components as those of the first embodiment, description thereof may be omitted by giving them the same names and the reference symbols in the specification or the drawings. - As shown in
FIG. 8 , acommunication hole 58 that communicates thecrank chamber 48 with theseal chamber 50 is formed in thefront housing 4. Thiscommunication hole 58 extends linearly inclined with respect to both the axis and radial directions of therotary shaft 24 as shown by broken lines. Inclination with respect to the radial direction of therotary shaft 24 is the direction along the circling direction of thecounterweight 42. That is, the openings of thecrank chamber 48 side and theseal chamber 50 side of thecommunication hole 58 are positioned included with respect to the diameter line of therotary shaft 24. - Thus, in the present embodiment, as a result of forming a
communication hole 58 having a different shape from those of the communication holes 52 of the first and second embodiments, as shown solid arrows inFIG. 8 , it is possible to guide lubricating oil to thelip seal 30 further effectively and quickly by exploiting force in the circling direction of thecounterweight 42 which acts on the refrigerant and the lubricating oil which have flown into thecommunication hole 58. Therefore, it is possible to realize significant reduction of wear of thelip seal 30 and ensure a residual fastening margin of thelip seal 30 while improving the compression efficiency of the compressor 1, thereby maintaining the sealing performance of the compressor 1 over a long period of time. -
FIG. 9 is a side view showing acounterweight 60 according to a fourth embodiment of the present invention in a state of being mounted to therotary shaft 24. Note that regarding the same components as those of any of the first to the third embodiments, description thereof may be omitted by giving them the same names and the reference symbols in the specification or the drawings. - As shown in
FIG. 9 , thecounterweight 60 of the present embodiment is configured such that a radial end surface 60 a 1 of each arc-shapedplate 60 a is inclined with respect to the axis of therotary shaft 24 and forms a flush inclinedsurface 62. Thisinclined surface 62, which is inclined in a closing direction to the axis from thecrankpin 24 c side toward the large-diameter shaft part 24 a, guides the lubricating oil adhered to the radial end surface 60 a 1 of each arc-shapedplate 60 a toward thecommunication hole 52 or thecommunication hole 58 as shown solid arrows, as thecounterweight 60 circles. - As a result of the
counterweight 60 being provided with theinclined surface 62 in the present embodiment, it is possible to effectively guide the lubricating oil adhered to the radial end surface 60 a 1 of each arc-shapedplate 60 a into thecommunication hole 52 or thecommunication hole 58, and more actively guide the lubricating oil to thelip seal 30. Therefore, it is possible to realize significant reduction of wear of thelip seal 30 and ensure a residual fastening margin of thelip seal 30 while improving the compression efficiency of the compressor 1, thereby maintaining the sealing performance of the compressor 1 over a long period of time. - Note that, without being limited to the above described one, for example as shown in
FIG. 10 , aninclined surface 64 in which only the radial end surface 60 a 1 of the arc-shapedplate 60 a closest to the large-diameter shaft part 24 a is inclined may be formed. Moreover, as shown inFIG. 11 , a steppedsurface 66 may be formed from the radial end surface 60 a 1 of each arc-shapedplate 60 a by causing one of the each arc-shapedplate 60 a to protrude in the radial direction of therotary shaft 24. In such cases, as shown by solid arrows inFIGS. 10 and 11 , it is possible to effectively guide the lubricating oil adhered to thecounterweight 60 to flow or drip into thecommunication hole 52 or thecommunication hole 58. - The present invention will not be limited to each embodiment described above, and various modifications can be made thereto.
- For example, in each embodiment described above, an engine-driven scroll compressor 1 which is incorporated in an air conditioner for vehicles has been described. However, the present invention can be applied to integrated electric-motor-driven scroll compressors and general scroll compressors in various fields which use various working fluids.
-
-
- 1 Scroll compressor
- 2 Rear housing (housing)
- 2 b Outer peripheral wall
- 4 Front housing (housing)
- 6 Scroll unit
- 8 Fixed scroll
- 10 Movable scroll
- 22 Suction port
- 24 Rotary 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 Stepped surface
Claims (6)
1. A scroll compressor, comprising:
a scroll unit for compressing a refrigerant by orbiting of a movable scroll relative to a fixed scroll;
a crank mechanism for converting rotary motion of a rotary shaft into orbiting motion of the movable scroll and transferring the orbiting motion;
a housing for accommodating the scroll unit, the housing including a suction port of the refrigerant on an outer peripheral wall located on an outer peripheral side of the scroll unit; and
a sealing device for sealing between the housing and the rotary shaft, wherein
the housing includes:
a crank chamber in which the crank mechanism is positioned,
a seal chamber in which the sealing device is positioned,
a communication hole for communicating the crank chamber with the seal chamber, and
a first guide groove extending from an opening of the communication hole in the seal chamber to a vicinity of the sealing device, and wherein
the crank mechanism includes a counterweight attached to the rotary shaft, and
the communication hole is formed at a position which is intermittently covered with the counterweight as the counterweight circles.
2. The scroll compressor according to claim 1 , wherein
the housing further includes a second guide groove in which an opening of the communication hole in the crank chamber is positioned.
3. (canceled)
4. The scroll compressor according to claim 1 , wherein
the communication hole is inclined along a circling direction of the counterweight with respect to a radial direction of the rotary shaft.
5. The scroll compressor according to claim 1 , wherein
the counterweight has an inclined surface inclined with respect to an axis of the rotary shaft.
6. The scroll compressor according to claim 1 , wherein
the counterweight has a stepped surface protruding in a radial direction of the rotary shaft.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2015-132670 | 2015-07-01 | ||
JP2015132670A JP6633305B2 (en) | 2015-07-01 | 2015-07-01 | Scroll compressor |
PCT/JP2016/066651 WO2017002536A1 (en) | 2015-07-01 | 2016-06-03 | Scroll compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20180187679A1 true US20180187679A1 (en) | 2018-07-05 |
Family
ID=57608560
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/740,195 Abandoned US20180187679A1 (en) | 2015-07-01 | 2016-06-03 | Scroll compressor |
Country Status (4)
Country | Link |
---|---|
US (1) | US20180187679A1 (en) |
JP (1) | JP6633305B2 (en) |
CN (1) | CN107923395A (en) |
WO (1) | WO2017002536A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN114439747A (en) * | 2021-12-24 | 2022-05-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Scroll compressor shafting lubricating structure, scroll compressor and air conditioner |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6917845B2 (en) * | 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 | Scroll type fluid machine |
KR102684109B1 (en) | 2022-05-09 | 2024-07-12 | 엘지전자 주식회사 | Scroll Compressor |
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JPS58108289A (en) * | 1981-12-22 | 1983-06-28 | Sumitomo Metal Ind Ltd | Liquefaction of coal |
US4468178A (en) * | 1981-03-09 | 1984-08-28 | Sanden Corporation | Scroll type compressor with displacement adjusting mechanism |
US4673340A (en) * | 1984-11-09 | 1987-06-16 | Sanden Corporation | Variable capacity scroll type fluid compressor |
US5456584A (en) * | 1993-10-29 | 1995-10-10 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Scroll type compressor with refrigerant gas passage in balance weight |
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US5490769A (en) * | 1993-01-15 | 1996-02-13 | Sanden International (U.S.A.), Inc. | Variable capacity scroll type fluid displacement apparatus |
US6132179A (en) * | 1997-09-09 | 2000-10-17 | Sanden Corporation | Scroll type compressor enabling a soft start with a simple structure |
US20020057977A1 (en) * | 2000-11-16 | 2002-05-16 | Mitsubishi Heavy Industries, Ltd. | Compressor having a seal member for supporting a shaft during assembly |
US6439775B1 (en) * | 1999-05-12 | 2002-08-27 | Sanden Corporation | Compressor bearings |
US20070292293A1 (en) * | 2006-06-14 | 2007-12-20 | Mitsubishi Heavy Industries, Ltd. | Fluid machine and scroll compressor |
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JPS58108289U (en) * | 1982-12-10 | 1983-07-23 | サンデン株式会社 | positive displacement fluid compression device |
JPS59196745A (en) * | 1983-03-31 | 1984-11-08 | Res Assoc Residual Oil Process<Rarop> | Iron-contg. zeolite composition |
JP4246826B2 (en) * | 1998-12-14 | 2009-04-02 | サンデン株式会社 | Scroll compressor |
JP2001132671A (en) * | 1999-11-09 | 2001-05-18 | Sanden Corp | Scroll compressor |
JP2002161879A (en) * | 2000-11-30 | 2002-06-07 | Toyota Industries Corp | Scroll compressor |
CN2651470Y (en) * | 2003-09-11 | 2004-10-27 | 王迪生 | Dynamic vortx air compressor |
CN203230590U (en) * | 2013-05-14 | 2013-10-09 | 力达(中国)机电有限公司 | Lubricating cooling system of vortex-type air compressor |
-
2015
- 2015-07-01 JP JP2015132670A patent/JP6633305B2/en active Active
-
2016
- 2016-06-03 WO PCT/JP2016/066651 patent/WO2017002536A1/en active Application Filing
- 2016-06-03 CN CN201680038468.7A patent/CN107923395A/en active Pending
- 2016-06-03 US US15/740,195 patent/US20180187679A1/en not_active Abandoned
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4468178A (en) * | 1981-03-09 | 1984-08-28 | Sanden Corporation | Scroll type compressor with displacement adjusting mechanism |
JPS58108289A (en) * | 1981-12-22 | 1983-06-28 | Sumitomo Metal Ind Ltd | Liquefaction of coal |
US4673340A (en) * | 1984-11-09 | 1987-06-16 | Sanden Corporation | Variable capacity scroll type fluid compressor |
US5490769A (en) * | 1993-01-15 | 1996-02-13 | Sanden International (U.S.A.), Inc. | Variable capacity scroll type fluid displacement apparatus |
US5456584A (en) * | 1993-10-29 | 1995-10-10 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Scroll type compressor with refrigerant gas passage in balance weight |
CN2214546Y (en) * | 1994-11-19 | 1995-12-06 | 西安交通大学 | Whirl commpression engine |
US6132179A (en) * | 1997-09-09 | 2000-10-17 | Sanden Corporation | Scroll type compressor enabling a soft start with a simple structure |
US6439775B1 (en) * | 1999-05-12 | 2002-08-27 | Sanden Corporation | Compressor bearings |
US20020057977A1 (en) * | 2000-11-16 | 2002-05-16 | Mitsubishi Heavy Industries, Ltd. | Compressor having a seal member for supporting a shaft during assembly |
US20070292293A1 (en) * | 2006-06-14 | 2007-12-20 | Mitsubishi Heavy Industries, Ltd. | Fluid machine and scroll compressor |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN114439747A (en) * | 2021-12-24 | 2022-05-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Scroll compressor shafting lubricating structure, scroll compressor and air conditioner |
Also Published As
Publication number | Publication date |
---|---|
WO2017002536A1 (en) | 2017-01-05 |
JP2017014999A (en) | 2017-01-19 |
CN107923395A (en) | 2018-04-17 |
JP6633305B2 (en) | 2020-01-22 |
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