EP2236828A1 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

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Publication number
EP2236828A1
EP2236828A1 EP09705346A EP09705346A EP2236828A1 EP 2236828 A1 EP2236828 A1 EP 2236828A1 EP 09705346 A EP09705346 A EP 09705346A EP 09705346 A EP09705346 A EP 09705346A EP 2236828 A1 EP2236828 A1 EP 2236828A1
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EP
European Patent Office
Prior art keywords
oil
discharge
partition member
scroll compressor
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP09705346A
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English (en)
French (fr)
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EP2236828A4 (de
EP2236828B1 (de
Inventor
Hajime Sato
Yoshiyuki Kimata
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Publication date
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Publication of EP2236828A1 publication Critical patent/EP2236828A1/de
Publication of EP2236828A4 publication Critical patent/EP2236828A4/de
Application granted granted Critical
Publication of EP2236828B1 publication Critical patent/EP2236828B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps
    • F04C15/066—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type
    • F04C15/068—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type of the elastic type, e.g. reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft

Definitions

  • the present invention relates to scroll compressors provided with an oil separation mechanism on a rear surface of a fixed-scroll member that discharges compressed gas.
  • a portion of lubricating oil supplied for lubricating a sliding section of a compressor merges with refrigerant gas compressed in the compressor and is carried away towards a refrigerant circuit. It is known from the past that this lubricating oil inhibits heat exchange in heat exchangers at the refrigerant-circuit side and is a factor that reduces system efficiency, and that too much of this oil carried away towards the refrigerant circuit can cause a shortage of lubricating oil in the compressor.
  • OCR oil circulation ratio
  • Patent Document 1 discloses a sealed-type scroll compressor in which an oil separation mechanism is provided within a high-pressure chamber.
  • This oil separation mechanism is configured by forming a discharge-valve surrounding chamber by providing a surrounding cover such that it covers a discharge port provided in a discharge cover joined to a fixed-scroll member, attaching an injection pipe to this discharge-valve surrounding chamber, opening one open end of the injection pipe at an acute angle relative to a tangential direction of an inner peripheral wall surface of a high-pressure chamber, and forming an annular oil-reservoir groove where oil separated at the outer peripheral side of the discharge-valve surrounding chamber accumulates.
  • Patent Document 1 Japanese Unexamined Patent Application, Publication No. 2001-248577
  • Patent Document 1 has a problem in that, since the annular oil-reservoir groove and the discharge-valve surrounding chamber are provided concentrically with each other on the same axis, if a discharge valve formed of a reed valve is made long, the annular oil-reservoir groove becomes small, making it impossible to ensure a sufficient capacity.
  • Another problem is that, since the oil accumulated in the annular oil-reservoir groove moves in an orbit with an orbiting flow of compressed gas, if the amount of oil is low, the compressed gas blows out toward the low-pressure side through an oil ejection port that returns the separated oil to an oil storage section in a low-pressure area, resulting in a compression loss.
  • the present invention has been made in view of these circumstances, and an object thereof is to provide a scroll compressor equipped with an oil separation mechanism that can ensure a sufficient capacity of an oil storage chamber even if a discharge reed valve is made long and that can prevent blow-by of compressed gas from an oil ejection port towards a low-pressure side.
  • a scroll compressor according to the present invention provides the following solutions. Specifically, in one aspect of a scroll compressor according to the present invention in which an oil separation chamber is formed by providing a discharge cover on a rear surface of a fixed-scroll member provided with a discharge port, and an oil separation mechanism is provided within the oil separation chamber, the oil separation mechanism includes a cylindrical partition member that partitions an interior of the oil separation chamber into an inner-peripheral-side gas discharge chamber and an outer-peripheral-side oil storage chamber, and a separator plate that closes an upper surface of the partition member, and the partition member is disposed eccentrically in a disposed direction of a discharge reed valve provided on the discharge port.
  • the cylindrical partition member that partitions the interior of the oil separation chamber into the gas discharge chamber and the oil storage chamber is disposed eccentrically in the disposed direction of the discharge reed valve provided on the discharge port, the capacity of the oil storage chamber can be sufficiently increased even if the discharge reed valve is made sufficiently long.
  • a sufficient capacity of the oil storage chamber can be ensured, and the oil separation function of the oil separation mechanism can be enhanced.
  • the above aspect may employ a configuration in which the separator plate is provided with an outlet through which compressed gas blows out from the gas discharge chamber towards the oil separation chamber, and the outlet is provided at a position corresponding to an outer peripheral area of a maximum eccentric section of the eccentrically-disposed partition member.
  • the outlet for compressed gas provided in the separator plate is provided at a position corresponding to the outer peripheral area of the maximum eccentric section of the partition member, the compressed gas can be blown out from the gas discharge chamber towards the oil storage chamber, without using a gas outlet pipe, at a position closer to an inner peripheral wall surface of the discharge cover corresponding to the maximum diameter of the oil storage chamber. Therefore, the configuration of the oil separation mechanism can be simplified and the oil can be centrifugally separated efficiently by utilizing the centrifugal force to the utmost, thereby enhancing the oil separation efficiency.
  • the outlet may be open at a predetermined angle towards an inner peripheral wall surface of the discharge cover.
  • the above configuration may be such that, in any one of the above scroll compressors, when the position of the outlet is defined as 0 degrees and an angle relative to an orbiting direction of the compressed gas blown out from the outlet is denoted by ⁇ , an oil ejection port that ejects oil from the oil storage chamber to a low-pressure area may be disposed at a position corresponding to an angle ⁇ of 180 to 360 degrees.
  • the disposed position of the oil ejection port can be set at a position where the oil separated in the oil storage chamber tends to gather the most due to the effect of a pressure drop caused by the eccentric disposition of the partition member.
  • the oil ejection port can be constantly liquid-sealed by the separated oil, and a compression loss caused by the compressed gas blowing out from the oil ejection port towards the low-pressure side can be suppressed.
  • the oil ejection port may be in communication with the oil storage chamber and be provided on an outer side of an outer periphery thereof.
  • the oil ejection port is in communication with the oil storage chamber and is provided on the outer side of the outer periphery thereof, the oil can be reliably guided to the oil ejection port even as the oil moves in an orbit with the orbiting flow of the compressed gas within the oil storage chamber, whereby the oil ejection port can be liquid-sealed by the oil. In consequence, blow-by of the compressed gas from the oil ejection port can be reliably prevented.
  • the above configuration may be configured such that, in any one of the above scroll compressors, the separator plate is concentric with an inner peripheral wall surface of the discharge cover and is provided so as to cover an upper surface of the oil storage chamber.
  • the separator plate since the separator plate is concentric with the inner peripheral wall surface of the discharge cover and is provided so as to cover the upper surface of the oil storage chamber, the separator plate can uniformly cover the upper surface of the oil storage chamber while maintaining a uniform gap therearound, regardless of whether the partition member is eccentrically disposed. This can suppress lifting of the separated oil within the oil storage chamber caused by the compressed gas, thereby enhancing the oil separation efficiency.
  • a gap of 1 mm to 2 mm may be formed between the separator plate and the inner peripheral wall surface of the discharge cover.
  • the gap of 1 mm to 2 mm is formed between the separator plate and the inner peripheral wall surface of the discharge cover, the gap can be reliably ensured and can compensate for an installation error, if any, in the separator plate and allow the separated oil to fall into the oil storage chamber. Consequently, while ensuring an oil drop gap, lifting of the oil within the oil storage chamber caused by the compressed gas can be minimized.
  • any one of the above scroll compressors may employ a configuration in which the partition member is formed as a separate component from the fixed-scroll member and a decompression mechanism that decompresses the oil ejected from the oil ejection port to the low-pressure area is provided between mating surfaces of the partition member and the fixed-scroll member.
  • the partition member is formed as a separate component from the fixed-scroll member and the decompression mechanism that decompresses the oil ejected from the oil ejection port to the low-pressure area is provided between the mating surfaces of the partition member and the fixed-scroll member, the decompression mechanism that decompresses high-pressure oil separated in the oil separation chamber to a low-pressure state before ejecting the oil can be disposed by utilizing the mating surfaces of the separately-formed partition member and fixed-scroll member.
  • the decompression mechanism may be constituted of a fine groove provided in a gasket that is interposed between the partition member and the fixed-scroll member and that forms a seal between the two members.
  • the decompression mechanism is constituted of the fine groove provided in the sealing gasket interposed between the partition member and the fixed-scroll member, the decompression mechanism can be formed using the sealing gasket. This eliminates the need to provide a dedicated component as the decompression mechanism, thereby achieving a simplified configuration and cost reduction.
  • the fine groove may be provided around substantially the entire circumference along a cylindrical segment of the partition member.
  • the fine groove provided in the gasket is provided around substantially the entire circumference along the cylindrical segment of the partition member, a sealing effect can be expected from the oil flowing through the fine groove in addition to the sealing effect by the gasket. In consequence, the sealability by the gasket between the partition member and the fixed-scroll member can be further enhanced.
  • the discharge reed valve since the capacity of the oil storage chamber can be sufficiently increased, even if the discharge reed valve is made sufficiently long, by disposing the cylindrical partition member, which partitions the interior of the oil separation chamber into the gas discharge chamber and the oil storage chamber, eccentrically in the disposed direction of the discharge reed valve, the discharge reed valve can be smoothly operated, as well as ensuring a sufficient capacity of the oil storage chamber and enhancing the oil separation function of the oil separation mechanism.
  • FIG. 1 is a longitudinal sectional view of a multistage compressor 1 for refrigerating/air-conditioning, to which a scroll compressor according to an embodiment of the present invention is applied.
  • a scroll compressor 3 according to an embodiment of the present invention is described as being used in a multistage compressor 1 configured by applying a rotary compressor 2 for the low-stage side and the scroll compressor 3 for the high-stage side as an example for the sake of convenience, the present invention can also be applied to a single-stage scroll compressor or to a multistage scroll compressor with scroll compressors for both the low-stage side and the high-stage side.
  • the multistage compressor 1 using the scroll compressor 3 includes a sealed housing 10.
  • the sealed housing 10 is constituted of a cylindrical center housing 10A, an annular bearing bracket 11 provided above the center housing 10A by welding around the entire circumference, a lower housing 10B that seals a lower section of the center housing 10A, and an upper housing 10C that is provided above the bearing bracket 11 by welding around the entire circumference and that seals an upper section of the center housing 10A.
  • An electric motor 4 formed of a stator 5 and a rotor 6 is fixedly disposed in a substantially central section inside the center housing 10A.
  • a rotary shaft (crankshaft) 7 is integrally joined to the rotor 6.
  • the low-stage rotary compressor 2 is disposed below the electric motor 4.
  • the low-stage rotary compressor 2 is configured by including a cylinder body 21 having a cylinder chamber 20 and fixedly disposed inside the center housing 10A, an upper bearing 22 and a lower bearing 23 fixedly disposed above and below the cylinder body 21, respectively, so as to seal upper and lower sections of the cylinder chamber 20, a rotor 24 fitted to a crank portion 7A of the rotary shaft 7 and rotating within an inner peripheral surface of the cylinder chamber 20, and a blade retaining spring and a blade (not shown) that partition the interior of the cylinder chamber 20 into an intake side and a discharge side.
  • This low-stage rotary compressor 2 is configured to take low-pressure refrigerant gas (working gas) into the cylinder chamber 20 through an intake pipe 25, compress this refrigerant gas to intermediate pressure by rotating the rotor 24, then discharge the refrigerant gas into upper and lower discharge chambers 26 and 27 by using the upper bearing 22 and the lower bearing 23, and discharge the refrigerant gas into the center housing 10A after the refrigerant gas merges inside the discharge chamber 26.
  • This intermediate-pressure refrigerant gas is guided to a space above the electric motor 4 by flowing through a gas channel hole 6A or the like provided in the rotor 6 of the electric motor 4, and is then taken in by the high-stage scroll compressor 3 so as to be compressed in two stages.
  • the high-stage scroll compressor 3 is provided inside the upper housing 10C.
  • the scroll compressor 3 includes a bearing member 31 (also called a frame member or a supporting member) fixedly disposed on an upper surface of the bearing bracket 11 with a bolt 12 and provided with a bearing 30 that supports the rotary shaft (crankshaft) 7, and a fixed-scroll member 32 and an orbiting scroll member 33 that have spiral wraps 32B and 33B erected on end plates 32A and 33A, respectively, and that form a pair of compression chambers 34 by engaging the spiral wraps 32B and 33B with each other and mounting them on the bearing member 31.
  • a bearing member 31 also called a frame member or a supporting member
  • the scroll compressor 3 is configured by also including an orbiting boss 33C that joins the orbiting scroll member 33 to an eccentric pin 7B of the rotary shaft 7 via a drive bush 13 so as to cause the orbiting scroll member 33 to revolve in an orbit, a self-rotation preventing mechanism 35 that is provided between the orbiting scroll member 33 and the bearing member 31 and allows the orbiting scroll member 33 to revolve in an orbit while preventing it from self-rotating, a discharge reed valve 36 (see Fig.
  • the aforementioned scroll compressor 3 is configured to take the intermediate-pressure refrigerant gas discharged to the sealed housing 10 after being compressed by the low-stage rotary compressor 2 into the compression chambers 34, perform a compressing operation by revolving the orbiting scroll member 33 in an orbit so as to compress this intermediate-pressure refrigerant gas to an even higher pressure state, and then discharge the refrigerant gas into the oil separation chamber 37 in the discharge cover 38 through the discharge reed valve 36. After oil in this high-temperature high-pressure refrigerant gas is removed by the oil separation mechanism 40 in the oil separation chamber 37, the gas is delivered outside the multistage compressor 1, i.e., a refrigeration-cycle side, through the discharge pipe 39.
  • a known positive-displacement oil pump 14 is fitted between the lowermost end of the rotary shaft (crankshaft) 7 and the lower bearing 23 of the low-stage rotary compressor 2.
  • This positive-displacement oil pump 14 is configured to pump up lubricating oil 15 that fills the bottom of the sealed housing 10 so as to forcedly supply the lubricating oil 15 to desired sections to be lubricated, such as the bearings in the rotary compressor 2 and the scroll compressor 3, through an oil hole 16 provided in the rotary shaft 7.
  • the oil separation mechanism 40 includes the oil separation chamber 37 with a cylindrical shape formed by the inner peripheral surface of the discharge cover 38, and a cylindrical partition member 42 fixedly disposed, within the oil separation chamber 37, on the rear surface of the fixed-scroll member 32 together with the discharge cover 38 via a gasket 41.
  • the partition member 42 is formed as a separate component from the fixed-scroll member 32 and has a flange 42A at a lower section thereof, and is tightly fixed to the rear surface of the fixed-scroll member 32 together with the discharge cover 38 via the flange 42A.
  • the partition member 42 is disposed eccentrically to the cylindrical oil separation chamber 37, formed by the inner peripheral surface of the discharge cover 38, in the disposed direction of the discharge reed valve 36, and partitions the interior of the oil separation chamber 37 into an inner-peripheral-side gas discharge chamber 43 surrounding the discharge reed valve 36 and an outer-peripheral-side oil storage chamber 44.
  • the oil storage chamber 44 is given a shape with a small radial width in the disposed direction of the discharge reed valve 36 and a large radial width at the opposite side; in consequence, the oil storage chamber 44 can have a larger capacity as compared with a case where the partition member 42 is provided concentrically with the discharge cover 38 so as to surround the discharge reed valve 36.
  • a separator plate 45 is fixedly disposed on an upper surface of the partition member 42 by using several screws.
  • the separator plate 45 is concentric with the inner peripheral surface of the discharge cover 38 and is attached so as to uniformly cover an upper surface of the oil storage chamber 44 while maintaining a uniform gap of about 1 mm to 2 mm therearound.
  • the separator plate 45 is provided with an outlet 46 for blowing out compressed gas from the gas discharge chamber 43 towards the oil storage chamber 44.
  • This outlet 46 is formed by press molding a section of the separator plate 45 into an upward-protruding arch shape and then opening one end thereof in a semicircular shape.
  • the outlet 46 is provided at a position corresponding to an outer peripheral area of a maximum eccentric section of the partition member 42 disposed eccentrically in the disposed direction of the discharge reed valve 36, that is, an upper-left area of the oil storage chamber 44 shown in Fig. 4 , and is open at a predetermined angle in a tangential direction towards the inner peripheral surface of the discharge cover 38.
  • an oil ejection port 47 for ejecting the oil separated by the oil separation mechanism 40 from the oil storage chamber 44 to a low-pressure area within the sealed housing 10 is disposed at a position at which an angle ⁇ relative to the orbiting direction of the compressed gas blown out from the outlet 46 is from 180 to 360 degrees.
  • This oil ejection port 47 is formed in an inner wall of the discharge cover 38 so as to face the inner peripheral surface thereof, and is in communication with the oil storage chamber 44 and is provided at a position on the outer side of the outer periphery thereof.
  • a strainer 48 is fitted in the oil ejection port 47.
  • the aforementioned oil ejection port 47 extends through the flange 42A of the partition member 42 and is in communication with a fine groove 49 (see Fig. 5 ) provided in the sealing gasket 41 interposed between mating surfaces of the rear surface of the fixed-scroll member 32 and the partition member 42.
  • the gasket 41 is formed by coating a surface of an iron plate with an elastic material, and the fine groove 49 formed by cutting this gasket 41 in the thickness direction thereof is provided around substantially the entire circumference along a cylindrical segment of the partition member 42 and then meanders therefrom several times in an area opposite to the direction of eccentricity of the partition member 42.
  • This fine groove 49 constitutes a decompression mechanism 50 that decompresses high-pressure oil to a low-pressure state before returning it to the low-pressure area within the sealed housing 10.
  • the other end of the fine groove 49 is in communication with an oil drop hole 51 provided in an outer peripheral area of the end plate 32A of the fixed-scroll member 32, and in an oil drop hole 52 provided in the bearing member 31, this oil drop hole 51 is configured to merge with an oil drainage hole 53, provided in the bearing member 31 for draining lubricating oil after being used for bearing lubrication, within the bearing member 31 and then allows the oil to flow down near the inner peripheral surface of the center housing 10A through an oil drainage pipe 54 fitted to the bearing bracket 11.
  • this embodiment provides the following advantages.
  • Low-temperature low-pressure refrigerant gas taken into the cylinder chamber 20 of the low-stage rotary compressor 2 through the intake pipe 25 is compressed to intermediate pressure by the rotation of the rotor 24 and is subsequently discharged into the discharge chambers 26 and 27.
  • this intermediate-pressure refrigerant gas is discharged into a space below the electric motor 4 and then flows therefrom to a space above the electric motor 4 by passing through the gas channel hole 6A or the like provided in the rotor 6 of the electric motor 4.
  • the intermediate-pressure refrigerant gas flowing into the space above the electric motor 4 travels through a gas channel (not shown) formed on the outer periphery or the like of the bearing member 31 constituting the high-stage scroll compressor 3 and is guided to an intake (not shown) provided in the fixed-scroll member 32 so as to be taken into the compression chambers 34.
  • the intermediate-pressure refrigerant gas After being compressed in two stages to a high-temperature high-pressure state by a compressing operation performed by revolving the orbiting scroll member 33 in an orbit, the intermediate-pressure refrigerant gas is discharged from the discharge port 32C into the discharge cover 38 via the discharge reed valve 36.
  • a portion of the lubricating oil 15 supplied by the oil pump 14 for lubricating the low-stage rotary compressor 2 is merged with the refrigerant gas and is discharged into the sealed housing 10 together with the intermediate-pressure refrigerant gas. Furthermore, a portion of the lubricating oil 15, flowing down to the bottom of the sealed housing 10 after being supplied to the high-stage scroll compressor 3 through the oil hole 16 to lubricate the scroll compressor 3, merges with the intermediate-pressure refrigerant gas.
  • the intermediate-pressure refrigerant gas merged with the lubricating oil 15 is taken in and compressed by the scroll compressor 3 while still containing the oil, and becomes high-temperature high-pressure gas which is subsequently discharged from the discharge port 32C together with the oil.
  • the compressed high-temperature high-pressure gas containing the oil is first discharged into the gas discharge chamber 43 and is then blown out therefrom towards the oil storage chamber 44 through the outlet 46, provided in the separator plate 45, at a predetermined angle in the tangential direction from the outermost peripheral area of the oil storage chamber 44 towards the inner peripheral surface of the discharge cover 38. Therefore, the compressed gas is given an orbiting flow, and the oil contained in the compressed gas is separated therefrom by a centrifugal force produced by the orbiting flow so as to drop down to the bottom of the oil storage chamber 44.
  • the compressed gas separated from the oil is discharged towards the refrigeration-cycle side through the discharge pipe 39 connected to the central section of the discharge cover 38. Consequently, the oil circulation ratio (OCR) of the lubricating oil 15 circulating to the refrigeration-cycle side can be reduced, thereby improving the system efficiency, as well as preventing a shortage of lubricating oil in the compressor 1.
  • the oil separated in the oil storage chamber 44 drops further down from the periphery of the separator plate 45 so as to accumulate at the bottom of the oil storage chamber 44.
  • the effect of the orbiting flow of the compressed gas causes this oil to move in an orbit in the same direction; but because the partition member 42 is eccentrically disposed within the oil storage chamber 44, the oil tends to gather in the vicinity of the opening area of the oil ejection port 47 due to a pressure drop in the narrow area in the direction of eccentricity.
  • the oil ejection port 47 can be constantly maintained in a liquid-sealed state by the oil, and after decompressing the high-pressure oil to low pressure with the decompression mechanism 50 constituted of the fine groove 49 provided in the gasket 41, the oil can be ejected to the low-pressure area within the sealed housing 10 via the oil drop holes 51 and 52 and the oil drainage pipe 54 so as to flow down therefrom to the bottom of the sealed housing 10.
  • the cylindrical partition member 42 that partitions the interior of the oil separation chamber 37 into the gas discharge chamber 43 and the oil storage chamber 44 is disposed eccentrically in the disposed direction of the discharge reed valve 36, the capacity of the oil storage chamber 44 can be sufficiently increased even if the discharge reed valve 36 is made sufficiently long. In consequence, in addition to allowing for smooth operation of the discharge reed valve 36, a sufficient capacity of the oil storage chamber 44 can be ensured, and the oil separation function of the oil separation mechanism 40 can be enhanced.
  • the outlet 46 for blowing out compressed gas from the gas discharge chamber 43 to the oil storage chamber 44 is provided at a position in the separator plate 45 that corresponds to the outer peripheral area of the maximum eccentric section of the partition member 42, the compressed gas can be blown out at a predetermined angle in the tangential direction towards the inner peripheral surface of the discharge cover 38, without using a gas outlet pipe, at a position closer to the inner peripheral wall surface of the discharge cover 38 corresponding to the maximum diameter of the oil storage chamber 44. Therefore, the configuration of the oil separation mechanism 40 can be simplified and the oil can be centrifugally separated efficiently by utilizing the centrifugal force to the utmost, thereby enhancing the oil separation efficiency.
  • the separator plate 45 is concentric with the inner peripheral surface of the oil storage chamber 44 and is attached so as to uniformly cover the upper surface of the oil storage chamber 44 while maintaining a uniform gap of about 1 mm to 2 mm therearound, the surrounding narrow gap can be reliably ensured and can compensate for an installation error, if any, in the separator plate 45 and allow the separated oil to fall into the oil storage chamber 44, in addition to minimizing lifting of the separated oil within the oil storage chamber 44 caused by the compressed gas, thereby enhancing the oil separation efficiency. It is preferable that the gap surrounding the separator plate 45 be made as narrow as possible from the viewpoint of suppressing lifting of the oil caused by the compressed gas.
  • the oil ejection port 47 for ejecting the oil separated in the oil storage chamber 44 to the low-pressure area within the sealed housing 10 is disposed at a position at which an angle ⁇ relative to the orbiting direction of the compressed gas blown out from the outlet 46 is from 180 to 360 degrees. Therefore, the disposed position of the oil ejection port 47 can be set at a position where the oil separated in the oil storage chamber 44 tends to gather the most due to the effect of a pressure drop caused by the eccentric disposition of the partition member 42.
  • the oil ejection port 47 can be constantly liquid-sealed by the separated oil, and a compression loss caused by the compressed gas blowing out from the oil ejection port 47 towards the low-pressure side can be suppressed.
  • the oil ejection port 47 is in communication with the oil storage chamber 44 and is provided on the outer side of the outer periphery thereof, the oil can be guided to the oil ejection port 47 even as the oil moves in an orbit with the orbiting flow of the compressed gas within the oil storage chamber 44, whereby the oil ejection port 47 can be liquid-sealed by the oil. In consequence, blow-by of the compressed gas from the oil ejection port 47 can be reliably prevented.
  • the rear-surface configuration of the fixed-scroll member 32 can be simplified, machining of the fixed-scroll member 32, which requires high machining accuracy, can be facilitated.
  • the fine groove 49 is provided around substantially the entire circumference along the cylindrical segment of the partition member 42, a sealing effect can be expected from the oil flowing through the fine groove 49 in addition to the sealing effect by the gasket 41. In consequence, the sealability by the gasket 41 between the partition member 42 and the fixed-scroll member 32 can be further enhanced.
  • the scroll compressor 3 according to the above embodiment is also applicable to refrigeration-cycle compressors that use any kind of refrigerant (working gas), other than R410A refrigerant or CO2 refrigerant
  • the scroll compressor 3 is suitable for use with CO2 refrigerant, which is particularly a high-pressure refrigerant.
  • CO2 refrigerant has high pressure and high density and oil separation is thus difficult
  • the scroll compressor 3 according to the present invention with a high centrifugal separation effect for oil is effective since higher oil separation performance is required.
  • the scroll compressor 3 according to the present invention is effective for a high-pressure refrigerant in view of the fact that a sealing effect can be expected from the oil flowing through the fine groove 49 constituting the decompression mechanism 50, in addition to the gasket 41.
  • the partition member 42 is formed as a separate component from the fixed-scroll member 32 in the above embodiment, the present invention is not limited to this, and the partition member 42 may alternatively be integrally molded to the rear surface of the end plate 32A of the fixed-scroll member 32.
  • the decompression mechanism 50 for decompressing the separated oil and ejecting the oil to the low-pressure area within the sealed housing 10 a configuration in which, for example, a decompression mechanism 50 is provided by inserting a pin having a spiral groove on the outer periphery thereof into an oil ejection hole provided in the end plate 32A of the fixed-scroll member 32 may be employed.

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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)
EP09705346.6A 2008-01-29 2009-01-07 Spiralverdichter Active EP2236828B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008018202A JP5112090B2 (ja) 2008-01-29 2008-01-29 スクロール圧縮機
PCT/JP2009/050101 WO2009096206A1 (ja) 2008-01-29 2009-01-07 スクロール圧縮機

Publications (3)

Publication Number Publication Date
EP2236828A1 true EP2236828A1 (de) 2010-10-06
EP2236828A4 EP2236828A4 (de) 2014-09-03
EP2236828B1 EP2236828B1 (de) 2017-08-02

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EP09705346.6A Active EP2236828B1 (de) 2008-01-29 2009-01-07 Spiralverdichter

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EP (1) EP2236828B1 (de)
JP (1) JP5112090B2 (de)
WO (1) WO2009096206A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3136020A1 (de) * 2015-08-27 2017-03-01 Mitsubishi Heavy Industries, Ltd. Zweistufige kompressionskälteanlage
EP3141753A1 (de) * 2015-09-09 2017-03-15 Lg Electronics Inc. Spiralverdichter

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5863263B2 (ja) * 2011-04-07 2016-02-16 三菱重工業株式会社 多段圧縮機
JP6440927B2 (ja) * 2013-02-07 2018-12-19 三菱重工サーマルシステムズ株式会社 密閉型スクロール圧縮機
FR3102793B1 (fr) 2019-11-04 2021-10-29 Danfoss Commercial Compressors Compresseur à spirales comportant des premier et deuxième agencements de stabilisation axiale
KR20210105565A (ko) * 2020-02-19 2021-08-27 한온시스템 주식회사 스크롤 압축기

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EP0864754A1 (de) * 1996-09-30 1998-09-16 Daikin Industries, Limited Ölabscheider für verdichter, spiralverdichter mit einem solchen ölabscheider sowie verfahren zur herstellung eines ölabscheider für spiralverdichtern

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JPS61226587A (ja) * 1985-03-30 1986-10-08 Toshiba Corp スクロ−ル型圧縮装置
JP3391072B2 (ja) * 1993-12-28 2003-03-31 松下電器産業株式会社 密閉型スクロール圧縮機
JPH08151990A (ja) * 1994-11-30 1996-06-11 Daikin Ind Ltd スクロール型流体装置
JPH09170581A (ja) * 1995-12-19 1997-06-30 Daikin Ind Ltd 圧縮機
JP4690516B2 (ja) 2000-03-06 2011-06-01 三菱重工業株式会社 スクロール型流体機械
JP4127108B2 (ja) * 2003-04-18 2008-07-30 松下電器産業株式会社 密閉型圧縮機
JP2005180297A (ja) * 2003-12-19 2005-07-07 Mitsubishi Heavy Ind Ltd スクロール圧縮機
JP2006336599A (ja) * 2005-06-06 2006-12-14 Matsushita Electric Ind Co Ltd 密閉型圧縮機
JP4117847B2 (ja) * 2005-11-14 2008-07-16 株式会社デンソー スクロール型圧縮機

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Publication number Priority date Publication date Assignee Title
EP0864754A1 (de) * 1996-09-30 1998-09-16 Daikin Industries, Limited Ölabscheider für verdichter, spiralverdichter mit einem solchen ölabscheider sowie verfahren zur herstellung eines ölabscheider für spiralverdichtern

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Title
See also references of WO2009096206A1 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3136020A1 (de) * 2015-08-27 2017-03-01 Mitsubishi Heavy Industries, Ltd. Zweistufige kompressionskälteanlage
EP3141753A1 (de) * 2015-09-09 2017-03-15 Lg Electronics Inc. Spiralverdichter
US10227983B2 (en) 2015-09-09 2019-03-12 Lg Electronics Inc. Scroll compressor having an oil separation space

Also Published As

Publication number Publication date
EP2236828A4 (de) 2014-09-03
WO2009096206A1 (ja) 2009-08-06
EP2236828B1 (de) 2017-08-02
JP2009180106A (ja) 2009-08-13
JP5112090B2 (ja) 2013-01-09

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