JP2011157895A - Compressor - Google Patents

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Publication number
JP2011157895A
JP2011157895A JP2010021207A JP2010021207A JP2011157895A JP 2011157895 A JP2011157895 A JP 2011157895A JP 2010021207 A JP2010021207 A JP 2010021207A JP 2010021207 A JP2010021207 A JP 2010021207A JP 2011157895 A JP2011157895 A JP 2011157895A
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JP
Japan
Prior art keywords
oil supply
supply passage
cylindrical
oil
fixed
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Granted
Application number
JP2010021207A
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Japanese (ja)
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JP5445180B2 (en
Inventor
Shigeki Iwanami
Takahiro Oki
重樹 岩波
恭弘 沖
Original Assignee
Denso Corp
株式会社デンソー
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Priority to JP2010021207A priority Critical patent/JP5445180B2/en
Publication of JP2011157895A publication Critical patent/JP2011157895A/en
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Publication of JP5445180B2 publication Critical patent/JP5445180B2/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02Rotary-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
    • F04C18/0207Rotary-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
    • F04C18/0215Rotary-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00Combinations 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
    • F04C23/008Hermetic pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02Lubrication; Lubricant separation
    • F04C29/023Lubricant distribution through a hollow driving shaft
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02Lubrication; Lubricant separation
    • F04C29/028Means for improving or restricting lubricant flow

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor having less wear due to an oil supply passage member. <P>SOLUTION: In an oil supply passage 127 of one member 12 out of a fixed member 12 and a movable member 11, the oil supply passage member 50 is stored, which has an oil supply hole 501 where lubricating oil distributes and which is thrust against the other member 11 by the pressure of fluid compressed by the compressor 10. The oil supply passage member 50 has a columnar portion 502 whose outer shape extends along the oil supply hole 501 into a columnar shape. The oil supply passage 127 of one member 12 has a columnar storage portion 511 into which the columnar portion 502 is inserted movably in the axial direction. The oil supply passage member 50 has a non-concentrically circular portion 503a formed in a non-concentrically circular shape relative to the columnar portion 502. The rotation of the oil supply passage member 50 is prevented by the non-concentrically circular portion 503a. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a compressor that compresses fluid by displacement of a movable member with respect to a fixed member.

  Conventionally, Patent Document 1 discloses a scroll compressor that compresses a refrigerant (fluid) as this type of compressor. In this prior art, lubricating oil is mixed in the refrigerant sucked into the working chamber, the lubricating oil is separated from the compressed refrigerant discharged from the working chamber, and the separated lubricating oil is used as a sliding portion (the object to be lubricated). Supply).

  The lubricating oil supply path is formed so as to penetrate the fixed scroll (fixed member) and the movable scroll (movable member) in the axial direction. Supplied. Specifically, the lubricating oil is supplied when the oil supply passage on the fixed scroll side and the oil supply passage on the movable scroll side overlap and communicate with each other, and when both the oil supply passages are out of communication with each other, the lubricating oil is supplied. Is interrupted.

  Here, a slight gap for preventing burn-in is formed between the fixed scroll and the movable scroll. For this reason, if the lubricating oil from the oil supply passage on the fixed scroll side leaks into the gap, the supply of the lubricating oil becomes insufficient.

  In view of this point, in the prior art of Patent Document 1, a cylindrical oil supply passage member is inserted into the oil supply passage of the fixed scroll, and the end face of the oil supply passage member is utilized using the pressure of the high-pressure refrigerant compressed in the working chamber. Is pressed against the sliding surface of the movable scroll.

  Thereby, the lubricating oil from the oil supply passage on the fixed scroll side flows into the oil supply passage on the movable scroll side through the inside of the oil supply passage member without leaking into the gap between the fixed scroll and the movable scroll. Lubricant leakage into the gap can be prevented.

  The oil supply passage member has a cylindrical portion whose outer shape is a cylindrical shape (a regular cylindrical shape), and the oil supply passage member has a cylindrical hole shape (a normal shape) in which the cylinder portion of the oil supply passage member is fitted in a liquid-tight state. A cylindrical housing portion having a cylindrical hole shape is formed. Thus, the lubricating oil is prevented from leaking from the gap between the cylindrical portion of the oil supply passage member and the cylindrical housing portion of the oil supply passage.

JP 2009-174337 A

  However, according to the detailed examination of the present inventor, in the above prior art, since the outer shape of the cylindrical portion of the oil supply passage member is cylindrical, the oil supply passage member rotates as it slides with the movable scroll. Thus, it has been found that the sliding surface of the movable scroll with the oil supply passage member is worn. An estimation mechanism of wear due to rotation of the oil supply passage member will be described later (FIG. 6).

  Here, as a means for preventing the rotation of the oil supply passage member, it is conceivable that both the cylindrical portion of the oil supply passage member and the cylindrical housing portion of the oil supply passage are made non-cylindrical. There is a problem that it becomes difficult to ensure the machining accuracy required for fitting in the state.

  An object of this invention is to suppress the abrasion by an oil supply channel | path member in view of the said point.

In order to achieve the above object, according to the first aspect of the present invention, the fixed member (12) and the movable member (11) displaced with respect to the fixed member (12) are provided. (11) comprising a compression mechanism (10) for compressing the fluid;
Each of the fixed member (12) and the movable member (11) is formed with oil supply passages (127, 114) for guiding the lubricating oil to the lubrication target portion.
The oil supply passages (127, 114) of the fixed member (12) and the movable member (11) are configured to communicate with each other intermittently as the movable member (11) is displaced,
The oil supply passage (127) of one member (12) of the fixed member (12) and the movable member (11) has an oil supply hole (501) through which lubricating oil flows and is compressed by the compression mechanism (10). An oil supply passage member (50) pressed against the other member (11) side by the pressure of the fluid is accommodated,
The oil supply passage member (50) has a cylindrical portion (502) whose outer shape extends in a cylindrical shape along the oil supply hole (501).
The oil supply passageway (127) of one member (12) has a columnar accommodating portion (511) into which the columnar portion (502) is movably inserted in the axial direction thereof,
Furthermore, the oil supply passage member (50) has a non-concentric circular portion (503a) formed non-concentrically with respect to the cylindrical portion (502),
The non-concentric circular part (503a) prevents the oil supply passage member (50) from rotating.

  According to this, since the non-concentric circular part (503a) for preventing rotation of the oil supply passage member (50) is formed in the oil supply passage member (50), rotation of the oil supply passage member (50) can be prevented. For this reason, wear (see FIG. 6 described later) due to the oil supply passage member (50) can be suppressed.

  Further, since the oil supply passage member (50) can be prevented from rotating without making the cylindrical part (502) and the cylindrical accommodating part (511) non-cylindrical, the cylindrical part (502) and the cylindrical accommodating part (511). It is easy to ensure the processing accuracy required to fit the two in a liquid-tight state.

According to a second aspect of the present invention, in the compressor according to the first aspect, the oil supply passage member (50) is positioned closer to the other member (11) than the cylindrical portion (502) and the outer shape is a cylindrical portion ( 502) having a radially enlarged head (503) with respect to
The oil supply passageway (127) of one member (12) has an enlarged storage part (512) in which the head part (503) is stored,
The non-concentric circular part (503a) is formed in the head part (503).

  According to this, since the non-concentric circular part (503a) of the oil supply passage member (50) is formed not on the cylindrical part (502) but on the head part (503), it affects the machining accuracy of the cylindrical part (502). The rotation stop of the oil supply passage member (50) can be performed without this.

  Specifically, as in the invention described in claim 3, in the compressor described in claim 2, the non-concentric circular portion (503a) may have a linear shape.

  More specifically, as in the invention described in claim 4, in the compressor described in claim 3, the non-concentric circular portion (503a) may have a two-sided width shape.

  Specifically, as in the invention described in claim 5, in the compressor described in claim 2, the non-concentric circular part (503a) has an eccentric shape eccentric with respect to the cylindrical part (502). You may make it do.

  According to a sixth aspect of the present invention, in the compressor according to any one of the second to fifth aspects, the oil supply passage member (50) projects from the head (503) to the other member (11) side, and It has the convex part (504) which slides with the other member (11), It is characterized by the above-mentioned.

  According to this, the sliding area between the oil supply passage member (50) and the other member (11) can be appropriately set by appropriately setting the shape of the convex portion (504) regardless of the shape of the head portion (503). . For this reason, compared with the case where the head (503) directly slides with the other member (11), the contact surface pressure between the oil supply passage member (50) and the other member (11) is set appropriately. be able to.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a typical sectional view of the compressor in a 1st embodiment of the present invention. It is a partial expanded sectional view of FIG. FIG. 3 is a partially enlarged sectional view of FIG. 2. It is the top view and sectional drawing of an oil supply channel | path member. It is sectional drawing which shows the circulation path | route of the lubricating oil in the compressor of FIG. It is explanatory drawing explaining the estimation mechanism of the abnormal wear by rotation of an oil supply passage member. It is a top view which shows the oil supply passage member in 2nd Embodiment of this invention. It is a top view which shows the oil supply passage member in 3rd Embodiment of this invention.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described. In this embodiment, the compressor of the present invention is applied to a heat pump cycle (not shown) for a hot water heater.

  The heat pump cycle is a vapor compression refrigeration cycle in which a compressor, a water-refrigerant heat exchanger, a decompressor, an evaporator, a gas-liquid separator, and the like are sequentially connected by piping. The water-refrigerant heat exchanger heats the hot water by exchanging heat between the refrigerant discharged from the refrigerant outlet of the compressor and the hot water. The decompressor decompresses the refrigerant flowing out of the water refrigerant heat exchanger. The evaporator absorbs heat from the outside air and evaporates the refrigerant decompressed by the decompressor. The gas-liquid separator separates the refrigerant flowing out of the evaporator into a liquid phase refrigerant and a gas phase refrigerant and stores excess refrigerant as the liquid phase refrigerant, and supplies the gas phase refrigerant to the refrigerant suction port of the compressor. The gas-liquid separator is not essential.

  The heat pump cycle of this embodiment constitutes a supercritical refrigeration cycle. Specifically, carbon dioxide is used as the refrigerant of the heat pump cycle, and the pressure of the high-pressure refrigerant discharged from the compressor is made higher than the critical pressure of the refrigerant.

  FIG. 1 is a schematic sectional view of the compressor, and FIG. 2 is a partially enlarged sectional view of FIG. The up and down arrows in FIGS. 1 and 2 indicate the up and down direction in the installed state of the compressor.

  The compressor is a scroll-type electric compressor, and is a vertical installation type in which a compression mechanism unit 10 that compresses a refrigerant (fluid) and an electric motor unit 20 that drives the compression mechanism unit 10 are arranged in the vertical direction (vertical direction). It has become. Specifically, the compression mechanism unit 10 is disposed below the electric motor unit 20.

  The compression mechanism unit 10 and the electric motor unit 20 are accommodated in a housing 30. An oil separator 40 that separates the lubricating oil from the refrigerant compressed by the compression mechanism unit 10 is disposed outside the housing 30. Both the housing 30 and the oil separator 40 have a vertically long shape extending in the vertical direction, and the oil separator 40 is disposed on the side of the housing 30.

  The housing 30 is a hermetically sealed structure in which a cylindrical member 31 extending in the vertical direction, an upper lid member 32 that closes the upper end portion of the cylindrical member 31, and a lower lid member 33 that closes the lower end portion of the cylindrical member 31 are joined. It is a container.

  Specifically, the cylindrical member 31 is formed in a cylindrical shape with iron, and the upper lid member 32 and the lower lid member 33 are both formed in a bowl shape with iron. The upper lid member 32 and the lower lid member 33 are hermetically joined to the cylindrical member 31 by welding after being press-fitted into the cylindrical member 31.

  The electric motor unit 20 includes a stator 21 that forms a stator and a rotor 22 that forms a rotor. The stator 21 has a cylindrical shape that extends in the vertical direction as a whole, and is fixed to a cylindrical member 31 of the housing 30. Specifically, the stator 21 includes a stator core 211 and a stator coil 212 wound around the stator core 211.

  Supply of electric power to the stator coil 212 is performed via the power supply terminal 23. The power supply terminal 23 is disposed at the upper end portion of the housing 30. Specifically, a power supply terminal fixing plate 24 that penetrates the power supply terminal 23 is fixed so as to close a through hole formed in the central portion of the upper cover member 32 of the housing 30.

  The rotor 22 is composed of a permanent magnet and is disposed inside the stator 21. The rotor 22 has a cylindrical shape extending in the vertical direction, and a drive shaft 25 extending in the vertical direction is fixed to the center hole of the rotor 22 by press-fitting. When electric power is supplied to the stator coil 212, a rotating magnetic field is applied to the rotor 22 to generate a rotational force in the rotor 22, and the drive shaft 25 rotates integrally with the rotor 22.

  The drive shaft 25 is formed in a cylindrical shape, and an internal space thereof constitutes an oil supply passage 251 that supplies lubricating oil to a sliding portion (lubrication target portion) of the drive shaft 25. The oil supply passage 251 is opened at the lower end surface of the drive shaft 25, and the upper end surface of the drive shaft 25 is closed by the closing member 26.

  A lower end side portion (a portion on the compression mechanism unit 10 side) of the drive shaft 25 protrudes below the rotor 22. A flange portion 252 that protrudes in the horizontal direction (a direction orthogonal to the axial direction) is formed in a portion of the drive shaft 25 that protrudes below the rotor 22. A balance weight 254 is provided on the flange portion 252. Balance weights 221 and 222 are also provided on both sides of the rotor 22 in the vertical direction.

  An upper end side portion of the drive shaft 25 (a portion opposite to the compression mechanism unit 10) protrudes upward from the rotor 22. A portion of the drive shaft 25 that protrudes above the rotor 22 is rotatably supported by a bearing member 27.

  The bearing member 27 is fixed to the cylindrical member 31 of the housing 30 via the interposed member 28. The interposition member 28 has a shape in which the outer peripheral portion of the annular plate that extends in the horizontal direction is bent downward, and the outermost peripheral surface thereof is fixed to the cylindrical member 31 of the housing 30.

  A flange portion 271 protruding in the horizontal direction is formed at the upper end portion of the bearing member 27, and the flange portion 271 is placed on the interposition member 28. The flange portion 271 of the bearing member 27 and the interposition member 28 are fastened and fixed by bolts (not shown). Thereby, the horizontal position of the bearing member 27 with respect to the interposition member 28 (position in the direction orthogonal to the axial direction) can be adjusted, and the drive shaft 25 can be centered.

  A portion of the drive shaft 25 between the rotor 22 and the flange portion 252 is rotatably supported by a bearing portion 291 formed in the middle housing 29. The middle housing 29 has a cylindrical shape whose outer diameter and inner diameter increase stepwise from the upper side toward the lower side, and is fixed with its outermost peripheral surface in contact with the cylindrical member 31 of the housing 30. Has been.

  A portion of the drive shaft 25 below the rotor 22 is located inside the middle housing 29, and an upper portion of the middle housing 29 having the smallest inner diameter constitutes a bearing portion 291.

  A flange portion 252 and a balance weight 254 of the drive shaft 25 are housed in a middle portion of the middle housing 29 in the vertical direction, that is, a portion whose inner diameter is larger than that of the bearing portion 291.

  As shown in FIG. 2, a movable scroll 11 that is a movable member of the compression mechanism unit 10 is accommodated in a lower portion of the middle housing 29 having the largest inner diameter. A fixed scroll 12 that is a fixed member of the compression mechanism unit 10 is disposed below the movable scroll 11.

  The movable scroll 11 and the fixed scroll 12 have disk-shaped substrate portions 111 and 121. Both board parts 111 and 121 are arranged so as to face each other in the vertical direction.

  A cylindrical boss portion 113 into which the lower end portion 253 of the drive shaft 25 is inserted is formed at the center portion of the movable scroll substrate portion 111. The lower end 253 of the drive shaft 25 is an eccentric portion that is eccentric with respect to the rotation center of the drive shaft 25. Therefore, the eccentric part 253 of the drive shaft 25 is inserted into the movable scroll 11.

  The movable scroll 11 and the middle housing 29 are provided with a rotation prevention mechanism (not shown) that prevents the movable scroll 11 from rotating about the eccentric portion 253. For this reason, when the drive shaft 25 rotates, the movable scroll 11 revolves (turns) around the rotation center of the drive shaft 25 without rotating around the eccentric portion 253.

  Two thrust plates 13 and 14 are stacked in the vertical direction between the movable scroll 11 and the middle housing 29. The upper side (middle housing 29 side) thrust plate 13 is fixed to the middle housing 29. Positioning of the upper thrust plate 13 with respect to the middle housing 29 is performed by positioning pins 131.

  The thrust plate 14 on the lower side (the movable scroll 11 side) is fixed to the movable scroll 11 and rotates integrally with the movable scroll 11. Positioning of the lower thrust plate 14 with respect to the middle housing 29 is performed by positioning pins 141.

  The movable scroll 11 is formed with a spiral tooth portion 112 protruding from the substrate portion 111 toward the fixed scroll 12 side. On the other hand, the substrate portion 121 of the fixed scroll 12 is fixed to the cylindrical member 31 of the housing 30, and the tooth portion 112 of the movable scroll 11 and the upper surface of the fixed scroll substrate portion 121 (surface on the movable scroll 11 side) Engaging spiral teeth 122 are formed. Specifically, a spiral groove portion is formed on the upper surface of the fixed scroll substrate portion 121, and a side wall of the spiral groove portion constitutes a spiral tooth portion 122.

  A plurality of crescent-shaped working chambers 15 are formed by meshing the tooth portions 112 and 122 of the scrolls 11 and 12 and making contact with each other at a plurality of locations. In FIG. 1, for convenience of illustration, only one working chamber among the plurality of working chambers 15 is denoted by reference numerals, and the other working chambers are not denoted by reference numerals.

  The working chamber 15 moves while reducing the volume from the outer peripheral side to the center side by the revolving motion of the movable scroll 11. Refrigerant is supplied to the working chamber 15 through the refrigerant supply passages 36 and 128, and the refrigerant in the working chamber 15 is compressed as the volume of the working chamber 15 decreases.

  Specifically, the refrigerant supply passages 36 and 128 that supply the refrigerant to the working chamber 15 are the refrigerant inlet 36 formed in the cylindrical member 31 of the housing 30 and the refrigerant formed inside the fixed scroll substrate portion 121. And a suction passage 128. A pipe connection member 37 is fixed to the refrigerant suction port 36, and a refrigerant pipe 38 shown in FIG. 1 is connected to the pipe connection member 37. The refrigerant suction passage 128 of the fixed scroll substrate 121 communicates with the outermost peripheral portion of the spiral groove of the fixed scroll substrate 121.

  As shown in FIG. 2, tip seals 16 and 17 for securing the airtightness of the working chamber 15 are attached to the movable scroll tooth portion 112 and the fixed scroll tooth portion 122. The chip seals 16 and 17 are formed in a prismatic shape extending along the spiral direction of the tooth portions 112 and 122 with a resin material such as polyether ether ketone ketone (PEEK).

  The tip seal 16 on the movable scroll 11 side is fitted in a tip seal groove formed on the lower surface of the movable scroll tooth portion 112 (the surface on the fixed scroll substrate portion 121 side). The tip seal 17 on the fixed scroll 12 side is fitted in a tip seal groove formed on the upper surface of the fixed scroll tooth portion 122 (the surface on the movable scroll substrate portion 111 side).

  The movable scroll side chip seal 16 slides in close contact with the bottom surface (sliding surface) of the spiral groove portion of the fixed scroll substrate portion 121, and the fixed scroll side chip seal 17 contacts the lower surface (sliding surface) of the movable scroll substrate portion 111. Slides in close contact with the surface. Thereby, the airtightness of the working chamber 15 is ensured, and the refrigerant is prevented from leaking from the working chamber 15.

  A discharge hole 123 through which the refrigerant compressed in the working chamber 15 is discharged is formed in the center of the fixed scroll substrate 121. A discharge chamber 124 communicating with the discharge hole 123 is formed below the discharge hole 123 in the fixed scroll substrate part 121. The discharge chamber 124 is defined by a recess 125 formed on the lower surface of the fixed scroll 12 and a partition member 18 fixed on the lower surface of the fixed scroll 12.

  In the discharge chamber 124, a reed valve (not shown) that forms a check valve that prevents the refrigerant from flowing back to the working chamber 15 and a stopper 19 that restricts the maximum opening of the reed valve are disposed.

  The refrigerant in the discharge chamber 124 is discharged to the outside of the housing 30 through a refrigerant discharge passage 54 formed in the fixed scroll substrate portion 121 and a refrigerant discharge port (not shown) formed in the cylindrical member 31 of the housing 30. It has become so.

  A refrigerant discharge port (not shown) of the housing 30 is connected to a refrigerant inlet 47 of the oil separator 40 shown in FIG. The oil separator 40 serves to separate the lubricating oil from the compressed refrigerant discharged from the housing 30 and return the separated lubricating oil into the housing 30.

  The oil separator 40 includes a cylindrical member 41 extending in the vertical direction, an upper lid member 42 that closes the upper end portion of the cylindrical member 41, and a lower lid member 43 that closes the lower end portion of the cylindrical member 41. The cylindrical member 41 is formed in a cylindrical shape with iron, and the upper lid member 42 and the lower lid member 43 are both formed with iron. The upper lid member 42 and the lower lid member 43 are press-fitted into the tubular member 41 and then joined to the tubular member 41 in an airtight and liquidtight manner by welding.

  The cylindrical member 41 of the oil separator 40 is joined to the cylindrical member 31 of the housing 30 by welding via a bracket 44 formed of iron. As a result, the oil separator 40 is fixed to the housing 30.

  The upper lid member 42 has a double cylinder structure constituted by an outer cylinder member 421 and an inner cylinder member 422. The outer cylinder member 421 and the inner cylinder member 422 are cylindrical members extending in the vertical direction, and the inner cylinder member 422 is inserted into the upper portion of the outer cylinder member 421.

  A cylindrical space 43 extending in the vertical direction is formed between the outer cylinder member 421 and the inner cylinder member 422. The refrigerant flowing from the refrigerant inlet 47 of the oil separator 40 is introduced into the cylindrical space 43. The refrigerant inlet 47 of the oil separator 40 is formed at a side portion of the cylindrical space 43 in the outer cylinder member 421.

  The upper part of the cylindrical space 43 is closed by an inner cylinder member 422. Specifically, the upper end portion of the inner cylinder member 422 has a larger diameter than the remaining portion, and is fixed to the inner peripheral surface of the outer cylinder member 421 in an airtight state.

  The upper end opening 45 of the outer cylinder member 421 constitutes a refrigerant outlet that discharges the refrigerant from which the lubricating oil has been separated to the outside of the oil separator 40 (in other words, outside the compressor). A refrigerant pipe 49 is connected to the refrigerant discharge port 45.

  The lower part of the oil separator 40 serves as an oil storage tank that stores lubricating oil separated from the refrigerant. An oil outlet 431 for allowing the stored lubricating oil to flow out of the oil separator 40 is formed in the lower lid member 43 of the oil separator 40.

  An oil pipe 46 is connected to the oil outlet 431, and the oil pipe 46 is connected to a pipe connecting member 34 fixed to the tubular member 31 of the housing 30. The pipe connecting member 34 passes through an oil introduction port 39 formed in the tubular member 31 of the housing 30 and is inserted into an insertion hole 126 formed in the side surface of the fixed scroll substrate portion 121.

  A fixed-side oil supply passage 127 through which the lubricating oil from the oil separator 40 flows is formed inside the fixed scroll substrate portion 121, and intermittently connected to the fixed-side oil supply passage 127 inside the movable scroll substrate portion 111. A movable oil supply passage 114 that communicates is formed.

  One end of the fixed oil supply passage 127 communicates with the insertion hole 126. The other end portion of the fixed-side oil supply passage 127 is open to the upper surface of the fixed scroll substrate portion 121 (the surface on the movable scroll substrate portion 111 side).

  One end of the movable oil supply passage 114 is open to the lower surface of the movable scroll substrate 111 (the surface on the fixed scroll substrate 121 side) so as to face the other end of the fixed oil supply passage 127.

  As a result, one end of the movable oil supply passage 114 overlaps or shifts from the other end of the fixed oil supply passage 127 as the movable scroll 11 revolves, so that the movable oil supply passage 114 is fixed to the fixed oil supply. The passage 127 is intermittently communicated.

  A cylindrical oil supply passage member 50 is accommodated at an end of the fixed side oil supply passage 127 on the movable scroll 11 side. Specifically, as shown in FIG. 2, the oil supply passage member 50 is accommodated in an accommodating portion 51 formed in the fixed-side oil supply passage 127.

  The oil supply passage member 50 is pressed toward the movable scroll 11 by the pressure in the oil separator 40, in other words, the pressure of the high-pressure refrigerant compressed in the working chamber 15. As a result, the upper end surface of the oil supply passage member 50 is pressed against the lower surface (sliding surface) of the movable scroll 12.

  For this reason, the lubricating oil from the fixed oil supply passage 127 flows through the oil supply passage member 50 and flows into the movable oil supply passage 114 without leaking into the slight gap between the fixed scroll 12 and the movable scroll 11. can do.

  The other end of the movable side oil supply passage 114 (the end opposite to the fixed side oil supply passage 127) opens at the lowermost inner surface of the boss portion 113 of the movable scroll 11. Therefore, when the movable-side oil supply passage 114 communicates with the fixed-side oil supply passage 127, the lubricating oil from the oil separator 40 is introduced into the gap between the boss portion 113 and the eccentric portion 253 of the drive shaft 25, and then the drive shaft 25 flows into the oil supply passage 251 of the drive shaft 25 from the lower end side of the drive shaft 25.

  The drive shaft 25 is formed with a through hole 255 extending radially outward from the oil supply passage 251 toward the boss portion 113 of the movable scroll 11. Further, as shown in FIG. 1, the drive shaft 25 has a through hole 256 extending radially outward from the oil supply passage 251 toward the bearing portion 291 of the middle housing 29, and a diameter from the oil supply passage 251 toward the bearing member 27. A through hole 257 extending outward in the direction is formed.

  Therefore, the lubricating oil that has flowed into the oil supply passage 251 passes through the through holes 255, 256, and 257, between the drive shaft 25 and the boss portion 113, between the drive shaft 25 and the bearing portion 291, and between the drive shaft 25 and the bearing. It is supplied to each sliding part (lubrication target part) between the members 27.

  The lubricating oil supplied between the drive shaft 25 and the bearing portion 291 flows down through the center hole of the middle housing 29 by gravity and is supplied between the two thrust plates 13 and 14. The lubricating oil supplied between the two thrust plates 13 and 14 flows down through a gap formed on the outer peripheral side of the movable scroll substrate 111 (a gap with the inner peripheral surface of the middle housing 29), and then the fixed scroll. The oil flows down an oil flow passage (not shown) penetrating the substrate portion 121 in the vertical direction, and reaches an oil storage chamber 35 formed in the lowermost portion of the housing 30.

  The oil storage chamber 35 is formed below the fixed scroll 12 and the partition member 18. The partition member 18 is formed with a through hole 181 penetrating in the vertical direction. The through hole 181 communicates with the refrigerant suction passage 128 of the fixed scroll substrate portion 121. A pipe 182 that sucks up the lubricating oil stored in the oil storage chamber 35 is inserted into the through-hole 181 from the lower side (oil storage chamber 35 side).

  Lubricating oil in the oil storage chamber 35 is supplied to the working chamber 15 through the pipe 182, the through-hole 181 of the partition member 18, and the refrigerant suction passage 128 of the fixed scroll substrate 121.

  FIG. 3 is an enlarged cross-sectional view showing the portion near the oil supply passage member 50 in FIG. 2 further enlarged. The oil supply passage member 50 is formed with an oil supply hole 501 through which lubricating oil flows. The oil supply hole 501 is formed in an orifice shape so that the flow rate of the lubricating oil is appropriate.

  The oil supply passage member 50 has a cylindrical portion 502 whose outer shape extends in a cylindrical shape (a regular cylindrical shape) along the oil supply hole 501, and is positioned closer to the movable scroll 11 than the cylindrical portion 502, and the outer shape has a diameter with respect to the cylindrical portion 502. And a head 503 enlarged in the direction.

  The accommodating portion 51 of the fixed-side oil supply passage 127 is formed in a cylindrical hole shape (a regular cylindrical hole shape) corresponding to the cylindrical portion 502, and the cylindrical portion 502 is inserted so as to be movable in the axial direction thereof. And an enlarged accommodating portion 512 in which the head portion 503 is accommodated.

  The cylindrical portion 502 is fitted into the cylindrical accommodating portion 511 in a liquid-tight state so that the lubricating oil does not leak from the gap between the cylindrical portion 502 and the cylindrical accommodating portion 511. That is, high processing accuracy is required for the cylindrical portion 502 and the cylindrical housing portion 511. For reasons of such processing accuracy, the cross-sectional shapes of the cylindrical portion 502 and the cylindrical housing portion 511 are perfect circles.

  FIG. 4 is a plan view and a cross-sectional view of the oil supply passage member 50. In addition, in FIG. 4, the accommodation part 51 of the fixed side oil supply path 127 is shown with the dashed-two dotted line for convenience of illustration.

  The head portion 503 has a non-concentric circle portion 503a formed in a non-concentric circle shape with respect to the cylindrical portion 502, and the non-concentric circle portion 503a prevents the oil supply passage member 50 from rotating. This will be specifically described below.

  The non-concentric circular part 503a has a linear shape. More specifically, two non-concentric circular portions 503a are formed, and the two non-concentric circular portions 503a constitute two surfaces parallel to each other. In other words, the non-concentric circular portion 503a has a two-sided width shape.

  Parts of the head 503 other than the two non-concentric circular parts 503 a have an arc shape concentric with the cylindrical part 502. Similarly to the head portion 503 of the oil supply passage member 50, the enlarged accommodating portion 512 of the accommodating portion 51 also has a non-concentric circular portion having a two-sided width shape.

  Here, let L1 be the radial distance between the portion of the peripheral edge of the head portion 503 farthest from the center of the cylindrical portion 502 and the center 502c of the cylindrical portion 502. In addition, a radial distance between a portion closest to the center of the columnar portion 502 and a center 502c of the columnar portion 502 in the peripheral portion of the enlarged accommodating portion 512 is L2.

  The head portion 503 and the enlarged accommodating portion 512 have shapes in which the distances L1 and L2 satisfy the relationship L1> L2. Therefore, when the oil supply passage member 50 tries to rotate with respect to the housing portion 51, the arc-shaped portion of the head portion 503 interferes with the double-sided width portion of the housing portion 51. As a result, the oil supply passage member 50 is prevented from rotating.

  Further, the oil supply passage member 50 has a convex portion 504 that protrudes from the head 503 toward the movable scroll 11 and slides relative to the movable scroll 11. The convex portion 504 has a perfect circular shape in plan view. The area (sliding area) of the convex portion 504 is set in consideration of the contact surface pressure with the movable scroll 11.

  Next, the operation in the above configuration will be described with reference to FIG. When electric power is supplied to the stator coil 212 of the electric motor unit 20 and the rotor 22 and the drive shaft 25 rotate, the movable scroll 11 revolves (turns) around the rotation center of the drive shaft 25. Thereby, the crescent-shaped working chamber 15 formed between the movable scroll tooth portion 112 and the fixed scroll tooth portion 122 shown in FIG. 2 moves while reducing the volume from the outer peripheral side to the center side.

  At this time, the refrigerant and the lubricating oil in the oil storage chamber 35 are supplied to the working chamber 15 located on the outer peripheral side. Specifically, the refrigerant outside the compressor is supplied to the working chamber 15 through the refrigerant suction port 36 of the housing 30 and the refrigerant suction passage 128 of the fixed scroll board 121, and at the same time, the arrows A1, A2, A3 in FIG. As described above, the lubricating oil in the oil storage chamber 35 is supplied to the working chamber 15 through the pipe 182, the through hole 181 of the partition member 18, and the refrigerant suction passage 128 of the fixed scroll substrate portion 121.

  The refrigerant supplied to the working chamber 15 is compressed as the volume of the working chamber 15 decreases. The refrigerant compressed in the working chamber 15 is discharged to the outside of the housing 30 through the discharge chamber 124 and the refrigerant discharge passage 54 of the fixed scroll 12 as indicated by arrows A4 and A5 in FIG. 5, and then as indicated by the arrow A6 in FIG. It flows into the refrigerant inlet 47 of the oil separator 40 through the pipe 48.

  The refrigerant flowing into the refrigerant inlet of the oil separator 40 is introduced into the cylindrical space 43 in the oil separator 40 as indicated by an arrow A7 in FIG. Then, a swirling flow is generated in the refrigerant in the cylindrical space 43, and the lubricating oil is separated from the refrigerant by the action of the centrifugal force generated by the swirling flow of the refrigerant.

  The refrigerant from which the lubricating oil has been separated is discharged from the refrigerant discharge port 45 of the oil separator 40 as the refrigerant discharged from the compressor. On the other hand, the lubricating oil separated from the refrigerant flows down in the oil separator 40 by gravity as shown by an arrow A8 in FIG. 5 and is stored in the lower part of the oil separator 40. The lubricating oil stored in the oil separator 40 is intermittently supplied to the oil supply passage 251 of the drive shaft 25 as indicated by arrows A9, A10, A11, A12, and A13 in FIG.

  Specifically, as described above, the movable-side oil supply passage 114 of the movable scroll 11 is intermittently communicated with the fixed-side oil supply passage 127 of the fixed scroll 12 in accordance with the revolving motion of the movable scroll 11. Is stored between the boss portion 113 of the movable scroll 11 and the eccentric portion 253 of the drive shaft 25 through the oil pipe 46, the pipe connecting member 34, the fixed side oil supply passage 127, and the movable side oil supply passage 114. It is introduced into the gap and then flows into the oil supply passage 251 inside the drive shaft 25 from the lower end side of the drive shaft 25.

  When the movable oil supply passage 114 is not in communication with the fixed oil supply passage 127, the supply of the lubricating oil to the oil supply passage 251 of the drive shaft 25 is interrupted.

  Here, the oil supply passage member 50 is pressed toward the movable scroll 11 by the pressure in the oil separator 40, in other words, the pressure of the high-pressure refrigerant compressed in the working chamber 15. As a result, the upper end surface of the oil supply passage member 50 is pressed against the lower surface (sliding surface) of the movable scroll 12.

  For this reason, the lubricating oil from the fixed oil supply passage 127 flows through the oil supply hole 501 in the oil supply passage member 50 without leaking into the slight gap between the fixed scroll 12 and the movable scroll 11, and the movable oil supply passage. 114 can flow into the oil supply passage 251 of the drive shaft 25, so that the lubricating oil can be reliably supplied.

  The lubricating oil supplied to the oil supply passage 251 of the drive shaft 25 passes through the through holes 255, 256, and 257 of the drive shaft 25 as indicated by arrows A14, A15, A16, and A17 in FIG. And between the drive shaft 25 and the bearing member 27. Thereby, it is possible to maintain good lubricity at the sliding portion (lubrication target portion) of the drive shaft 25.

  The lubricating oil supplied between the drive shaft 25 and the bearing portion 291 flows down through the center hole of the middle housing 29 by gravity and is supplied between the two thrust plates 13 and 14. Thereby, lubricity can be favorably maintained at the sliding portion between the thrust plates 13 and 14.

  The lubricating oil supplied between the two thrust plates 13 and 14 flows down through a gap formed on the outer peripheral side of the movable scroll substrate 111 (a gap with the inner peripheral surface of the middle housing 29), and then the fixed scroll. It flows down an oil flow passage (not shown) penetrating the base plate part 121 in the vertical direction, and reaches an oil storage chamber 35 formed at the lowermost part in the housing 30 as indicated by an arrow A18 in FIG.

  According to the present embodiment, the oil supply passage member 50 is prevented from rotating by forming a two-sided width shape in the head portion 503 of the oil supply passage member 50 and the enlarged storage portion 512 of the storage portion 51. It is possible to prevent abnormal wear of the movable scroll 11 due to this rotation.

  Here, an estimation mechanism of abnormal wear of the movable scroll 11 due to the rotation of the oil supply passage member 50 will be described with reference to FIG.

  First, as shown in FIG. 6A, when the movable scroll 11 revolves (swings) and slides with the oil supply passage member 50, the sliding surface of the movable scroll 11 is gradually worn and recessed. When a certain level of level difference is formed on the sliding surface of the movable scroll 11 due to the progress of the wear, this level level applies a rotational force to the oil supply passage member 50.

  At this time, if the oil supply passage member 50 is not rotated, the oil supply passage member 50 rotates. By this rotation, as shown in FIG. 6B, it is estimated that the oil supply passage member 50 itself wears in a tapered shape, and the sliding surface of the movable scroll 11 abnormally wears in a mortar shape.

  In this respect, in the present embodiment, since the non-concentric circular portion 503a formed on the head portion 503 of the oil supply passage member 50 prevents the oil supply passage member 50 from rotating, it is possible to prevent the oil supply passage member 50 from rotating, and hence the movable scroll. 11 abnormal wear can be prevented.

  Further, since the non-concentric circular portion 503a of the oil supply passage member 50 is formed in the head portion 503, it is necessary to form a detent shape in the cylindrical portion 502 of the oil supply passage member 50 and the cylindrical housing portion 511 of the fixed-side oil supply passage 127. Absent.

  For this reason, since it is very easy to ensure the processing accuracy required for fitting the cylindrical portion 502 to the cylindrical accommodating portion 511 in a liquid-tight state, the clearance from the gap between the cylindrical portion 502 and the cylindrical accommodating portion 511 is very easy. Lubricant leakage can be reliably prevented.

  Incidentally, the oil supply passage member 50 is formed with a convex portion 504 that protrudes from the head 503 toward the movable scroll 11, and the convex portion 504 slides on the movable scroll 11. The contact surface pressure between the member 50 and the movable scroll 11 can be set appropriately.

  That is, if the contact surface pressure between the oil supply passage member 50 and the movable scroll 11 is to be set appropriately, it is necessary to set the sliding area between the oil supply passage member 50 and the movable scroll 11 according to the desired contact surface pressure. .

  However, when the head 503 slides directly with the movable scroll 11, the sliding area between the oil supply passage member 50 and the movable scroll 11 is uniquely determined by the shape of the head 503, and the oil supply passage member is formed. The contact surface pressure between 50 and the movable scroll 11 is also uniquely determined.

  In this respect, in this embodiment, the sliding area between the oil supply passage member 50 and the movable scroll 11 can be appropriately set by setting the shape of the convex portion 504 regardless of the shape of the head portion 503, and as a result, the oil supply The contact surface pressure between the passage member 50 and the movable scroll 11 can be set appropriately.

(Second Embodiment)
In the first embodiment, two straight non-concentric circular portions 503a are formed on the head portion 503 of the oil supply passage member 50. However, in the second embodiment, as shown in FIG. Only one concentric circle 503a is formed.

  Also in the present embodiment, the head portion 503 and the enlarged accommodating portion 512 have a shape that satisfies the relationship L1> L2. Therefore, similarly to the first embodiment, the oil supply passage member 50 is prevented from rotating, and thus the abnormal scroll 11 can be prevented from being worn.

(Third embodiment)
In the first and second embodiments, the non-concentric circular portion 503a of the oil supply passage member 50 has a linear shape. However, in the third embodiment, as shown in FIG. 8, the non-concentric circular portion 503b has a cylindrical shape. It has an eccentric shape eccentric with respect to the part 502. Accordingly, the enlarged accommodating portion 512 of the fixed-side oil supply passage 127 also has an eccentric shape that is eccentric with respect to the cylindrical portion 502. The convex portion 504 of the oil supply passage member 50 is concentrically formed with respect to the cylindrical portion 502.

  Also in the present embodiment, the head portion 503 and the enlarged accommodating portion 512 have a shape that satisfies the relationship L1> L2. Therefore, as in the first and second embodiments, the oil supply passage member 50 is prevented from rotating, and thus the abnormal wear of the movable scroll 11 can be prevented.

(Other embodiments)
(1) In each of the above-described embodiments, the oil supply passage member 50 is configured such that the head portion 503 of the oil supply passage member 50 is enlarged in the radial direction with respect to the cylindrical portion 502 and the head portion 503 is formed with the non-concentric circular portion 503a. However, it is not always necessary to form the head portion 503 expanded in the radial direction with respect to the cylindrical portion 502. For example, a non-concentric circle is formed by a protrusion formed on the side surface of the cylindrical portion 502. You may comprise a part.

  (2) In the above-described embodiments, the lubricating oil is guided from the fixed scroll 12 side toward the movable scroll 11 side. On the contrary, from the movable scroll 11 side toward the fixed scroll 12 side. Lubricating oil may be guided. In this case, the oil supply passage member 50 may be disposed in the movable scroll 11 and pressed toward the fixed scroll 12 by the pressure of the high-pressure refrigerant compressed in the working chamber 15.

  (3) In each of the embodiments described above, the oil separator 40 is disposed outside the housing 30, but the oil separator 40 may be housed inside the housing 30.

  (4) In each of the embodiments described above, the present invention is applied to a vertical type compressor in which the compression mechanism unit 10 and the motor unit 20 are arranged in the vertical direction (vertical direction). The present invention can also be applied to a horizontal type compressor in which the electric motor unit 20 is disposed in the horizontal direction (lateral direction).

  (5) In each of the above-described embodiments, the heat pump cycle constitutes a supercritical refrigeration cycle, and carbon dioxide is used as a refrigerant. Or a refrigerant such as a chlorofluorocarbon refrigerant or a hydrocarbon refrigerant may be employed.

  (6) In each of the above embodiments, the compressor of the present invention is applied to a heat pump cycle, but the compressor of the present invention can be widely applied to various refrigeration cycles.

  (7) In each of the above-described embodiments, an example in which the present invention is applied to a scroll-type compressor has been shown. For example, the present invention can be widely applied to a reciprocating compressor, a rotary compressor, and the like.

10 compression mechanism 11 movable scroll (movable member, other member)
12 Fixed scroll (fixed member, one member)
50 Oil supply passage member 114 Movable oil supply passage (oil supply passage)
127 Fixed side oil supply passage (oil supply passage)
501 Oil supply hole 502 Cylindrical part 503 Head 503a Non-concentric circular part 511 Cylindrical accommodating part 512 Expansion accommodating part

Claims (6)

  1. A compression member (10) having a fixed member (12) and a movable member (11) displaced with respect to the fixed member (12), and compressing fluid by the fixed member (12) and the movable member (11). )
    Each of the fixed member (12) and the movable member (11) is formed with oil supply passages (127, 114) for guiding the lubricating oil to the lubrication target portion.
    The oil supply passages (127, 114) of the fixed member (12) and the movable member (11) are configured to intermittently communicate with each other as the movable member (11) is displaced,
    The oil supply passage (127) of one member (12) of the fixed member (12) and the movable member (11) has an oil supply hole (501) through which the lubricating oil flows, and the compression mechanism ( An oil supply passage member (50) that is pressed toward the other member (11) by the pressure of the fluid compressed in 10);
    The oil supply passage member (50) has a cylindrical portion (502) whose outer shape extends in a cylindrical shape along the oil supply hole (501),
    The oil supply passageway (127) of the one member (12) has a columnar accommodating portion (511) into which the columnar portion (502) is inserted so as to be movable in the axial direction thereof.
    Furthermore, the oil supply passage member (50) has a non-concentric circular part (503a) formed non-concentrically with respect to the cylindrical part (502),
    The compressor is characterized in that the oil supply passage member (50) is prevented from rotating by the non-concentric circular portion (503a).
  2. The oil supply passage member (50) is positioned closer to the other member (11) than the columnar part (502), and a head (503) whose outer shape is radially expanded with respect to the columnar part (502). )
    The oil supply passage (127) of the one member (12) has an enlarged accommodating portion (512) in which the head (503) is accommodated,
    The compressor according to claim 1, wherein the non-concentric circular part (503a) is formed in the head part (503).
  3.   The compressor according to claim 2, wherein the non-concentric circular part (503a) has a linear shape.
  4.   The compressor according to claim 3, wherein the non-concentric circular part (503a) has a two-sided width shape.
  5.   The compressor according to claim 2, wherein the non-concentric circular part (503a) has an eccentric shape eccentric with respect to the cylindrical part (502).
  6.   The oil supply passage member (50) has a protrusion (504) that protrudes from the head (503) toward the other member (11) and slides with the other member (11). The compressor according to any one of claims 2 to 5, characterized in that:
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Cited By (5)

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US8578603B2 (en) 2010-02-18 2013-11-12 Denso Corporation Compressor and manufacturing method thereof
CN103573623A (en) * 2013-11-01 2014-02-12 广东美芝制冷设备有限公司 Rotary compressor
WO2015194122A1 (en) * 2014-06-17 2015-12-23 株式会社デンソー Compressor
US9765780B2 (en) 2012-03-30 2017-09-19 Denso Corporation Compressor
WO2017208455A1 (en) * 2016-06-03 2017-12-07 三菱電機株式会社 Scroll compressor

Families Citing this family (1)

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Publication number Priority date Publication date Assignee Title
KR20190000035A (en) 2017-06-22 2019-01-02 엘지전자 주식회사 Scroll compressor and air conditioner having the same

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JPH02227582A (en) * 1989-02-28 1990-09-10 Toshiba Corp Scroll compressor
JP2009174337A (en) * 2008-01-22 2009-08-06 Denso Corp Compressor

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Publication number Priority date Publication date Assignee Title
DE102008008860B4 (en) 2007-02-14 2015-09-03 Denso Corporation Compressor

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Publication number Priority date Publication date Assignee Title
JPH02227582A (en) * 1989-02-28 1990-09-10 Toshiba Corp Scroll compressor
JP2009174337A (en) * 2008-01-22 2009-08-06 Denso Corp Compressor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8578603B2 (en) 2010-02-18 2013-11-12 Denso Corporation Compressor and manufacturing method thereof
US9765780B2 (en) 2012-03-30 2017-09-19 Denso Corporation Compressor
CN103573623A (en) * 2013-11-01 2014-02-12 广东美芝制冷设备有限公司 Rotary compressor
CN103573623B (en) * 2013-11-01 2016-03-16 广东美芝制冷设备有限公司 Rotary compressor
WO2015194122A1 (en) * 2014-06-17 2015-12-23 株式会社デンソー Compressor
JP2016020687A (en) * 2014-06-17 2016-02-04 株式会社デンソー Compressor
WO2017208455A1 (en) * 2016-06-03 2017-12-07 三菱電機株式会社 Scroll compressor

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