WO2010070790A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2010070790A1
WO2010070790A1 PCT/JP2009/004584 JP2009004584W WO2010070790A1 WO 2010070790 A1 WO2010070790 A1 WO 2010070790A1 JP 2009004584 W JP2009004584 W JP 2009004584W WO 2010070790 A1 WO2010070790 A1 WO 2010070790A1
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WO
WIPO (PCT)
Prior art keywords
compression chamber
scroll
oil supply
supply path
oil
Prior art date
Application number
PCT/JP2009/004584
Other languages
English (en)
Japanese (ja)
Inventor
作田淳
河野博之
中井啓晶
大野竜一
森本敬
二上義幸
山田定幸
Original Assignee
パナソニック株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニック株式会社 filed Critical パナソニック株式会社
Priority to CN200980150596.0A priority Critical patent/CN102245903B/zh
Priority to JP2010542813A priority patent/JP5345636B2/ja
Publication of WO2010070790A1 publication Critical patent/WO2010070790A1/fr
Priority to US13/420,147 priority patent/US8576142B2/en

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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow

Definitions

  • the present invention relates to a scroll compressor used for a cooling device such as an air conditioning air conditioner or a refrigerator, or a heat pump type hot water supply device.
  • scroll compressors used in refrigeration air conditioners and refrigerators generally engage a fixed scroll and a swirl scroll in which a spiral wrap rises from an end plate to form a compression chamber therebetween. Then, the orbiting scroll is orbited along a circular path under the rotation restraint by the rotation restraining mechanism. At this time, suction, compression, and discharge are performed by moving the compression chamber while changing the volume.
  • oil supply to the compression chamber is indispensable, and the supplied oil plays a role mainly in improving the sealing performance of the compression chamber.
  • FIG. 25 is a cross-sectional view of a compression mechanism portion of a conventional scroll compressor described in Patent Document 1.
  • the orbiting scroll 101, the fixed scroll 102, a plurality of compression chambers 103 formed between the two scrolls, and an oil storage part for accumulating oil are provided.
  • the suction volume of one compression chamber 104o is larger than the suction volume of the second compression chamber 104i formed on the inner line side, the oil storage section, the first compression chamber 104o, and the second compression chamber 104i.
  • the first compression chamber 104o having a large suction volume starts to compress first, so that the pressure is higher than the suction pressure when the second compression chamber 104i starts to compress.
  • the amount of oil supplied to the first compression chamber 104o is made larger than the amount of oil supplied to the second compression chamber 104i, or the oil is supplied only to the first compression chamber 104o, whereby the first compression chamber 104o is supplied.
  • the leakage from 104o to the second compression chamber 104i is suppressed, and the compression performance is improved.
  • leakage from the second compression chamber 104i to the second compression chamber 104i on the low pressure side is from the first compression chamber 104o. More than one leak into the first compression chamber 104o on the low pressure side. This is because in the asymmetric scroll compressor in which the suction volume of the first compression chamber 104o is larger than the suction volume of the second compression chamber 104i, the second compression chamber 104i having a smaller suction volume has a difference in suction volume. This is because the pressure increase speed with respect to the crank rotation angle is large.
  • the relationship between the first compression chamber 104o and the second compression chamber 104i will be described with reference to FIG. As shown in FIG.
  • the pressure change is larger in the second compression chamber 104i having a smaller suction volume. Accordingly, leakage is more likely to occur in the spiral wrap contact portion D2 than in the spiral wrap contact portion D1. Therefore, leakage through the spiral wrap side surface causes recompression of the refrigerant, resulting in a reduction in compression performance due to useless work.
  • the present invention solves the above-described conventional problems, and by increasing the amount of oil supplied to the second compression chamber, the scroll compressor that suppresses leakage through the lap contact portion and realizes improvement in compression performance.
  • the purpose is to provide.
  • it aims at providing a highly efficient scroll compressor by the oil supply path
  • the scroll compressor according to the first aspect of the present invention is the fixed scroll and the orbiting scroll in which the spiral wrap rises from the end plate, the shaft for driving the orbiting scroll, and the fixed scroll and the orbiting scroll are engaged with each other.
  • a suction chamber of the first compression chamber formed on the wrap outer wall side of the orbiting scroll is formed on the wrap inner wall side of the orbiting scroll.
  • the scroll compressor according to the first aspect wherein a fixed front end gap formed between a wrap front end of the fixed scroll and a lap side end plate surface of the orbiting scroll is provided with the swivel scroll. It is characterized by being made smaller than the turning tip clearance formed between the wrap tip and the wrap side end plate surface of the fixed scroll.
  • a pump is provided at one end of the shaft, and a suction port of the pump is provided in the oil storage section.
  • the closed position of the first compression chamber and the closed position of the second compression chamber are substantially the same. It is characterized by being shifted by 180 degrees.
  • a high pressure region and a back pressure chamber are formed on a back surface of the orbiting scroll, and a plurality of oil supply paths are provided. Part or all of the oil supply path passes through the back pressure chamber.
  • a sealing member is disposed on the back surface of the orbiting scroll, the inner side of the sealing member is a high pressure region, and the outer side of the sealing member is a back pressure chamber.
  • at least one of the oil supply paths includes a back pressure chamber oil supply path from the high pressure region to the back pressure chamber, and a compression chamber oil supply path from the back pressure chamber to the second compression chamber. It is characterized by that.
  • an open end of the back pressure chamber oil supply path is moved back and forth through the seal member.
  • the present invention according to claim 8 is the scroll compressor according to claim 6 or claim 7, wherein the second compression chamber communicated with the back pressure chamber via the compression chamber oil supply path is configured to supply a working fluid. It is a compression chamber after being confined.
  • the compression chamber oil supply path includes a passage formed inside the orbiting scroll, and the fixed scroll.
  • the back pressure chamber and the second compression chamber are intermittently formed by a recess formed in the lap side end plate surface, and the opening end of the passage periodically opens to the recess in accordance with a turning motion. It is characterized by communicating with.
  • the oil supply path leading from the oil storage section to the first compression chamber and the second compression chamber is provided.
  • the first oil supply path and the second oil supply path are provided, respectively, and the same number or more of the second oil supply paths are provided with respect to the first oil supply path.
  • the present invention according to claim 11 is the scroll compressor according to claim 1, wherein at least one of the oil supply paths is an intermittent oil supply path for intermittent communication.
  • at least one of the intermittent oil supply paths opens an opening end in the compression chamber before confining the working fluid. .
  • a high pressure region and a back pressure chamber are formed on the back surface of the orbiting scroll, and at least one of the intermittent oil supply paths is It communicates with the high pressure region.
  • a high pressure region and a back pressure chamber are formed on a back surface of the orbiting scroll, and at least one of the intermittent oil supply paths is It passes through the back pressure chamber.
  • a high pressure region and a back pressure chamber are formed on a back surface of the orbiting scroll, and at least one of the intermittent oil supply paths is It is comprised from the connection path which connects the said back pressure chamber from the said high voltage
  • an opening end of the connection path partitions the high pressure region provided on the back surface of the orbiting scroll and the back pressure chamber. It is characterized by coming and going through the seal member.
  • the supply path communicates with the compression chamber after the working fluid is confined.
  • the present invention according to claim 18 is the scroll compressor according to any one of claims 15 to 17, characterized in that the supply passage communicates with the second compression chamber.
  • the supply path includes a passage formed in the orbiting scroll and the wrap side end plate of the fixed scroll. It is comprised from the recessed part formed in the surface, The one opening end of the said channel
  • the invention according to claim 20 is the scroll compressor according to any one of claims 11 to 19, wherein the intermittent oil supply path includes a passage formed in the orbiting scroll and the wrap side of the fixed scroll. It is comprised from the recessed part formed in the end plate surface, and the one opening end of the said path
  • the oil supply passage is open to a lap tip oil supply route for supplying oil to the lap tip of the orbiting scroll, and the second compression chamber. And an oil supply amount control path.
  • the lap tip oil supply path includes a passage passing through the inside of the orbiting scroll and an oil groove provided at the lap tip of the orbiting scroll. It is characterized by being.
  • a high pressure region and a back pressure chamber are formed on a back surface of the orbiting scroll, and the wrap tip oil supply path is the high pressure region and It passes through the back pressure chamber.
  • a high-pressure region and a back pressure chamber are formed on a back surface of the orbiting scroll, and the wrap tip oil supply path is the back pressure chamber. It is characterized by passing only through the high pressure region without going through.
  • at least one of the wrap tip oil supply passages supplies oil to the compression chamber before confining the working fluid. It is characterized by comprising a route to be performed.
  • a high pressure region and a back pressure chamber are formed on the back surface of the orbiting scroll, At least one is constituted by a connection path for supplying oil from the high pressure region to the back pressure chamber and a supply path A for communicating the back pressure chamber and the second compression chamber.
  • the present invention according to claim 27 is the scroll compressor according to claim 26, wherein an opening end of the connection path partitions the high pressure region provided on the back surface of the orbiting scroll and the back pressure chamber. It is characterized by coming and going.
  • the supply path A communicates with the second compression chamber after confining the working fluid.
  • the present invention according to claim 29 is the scroll compressor according to any one of claims 26 to 28, wherein the supply path A includes a passage formed in the orbiting scroll and the wrap side of the fixed scroll. It is comprised from the recessed part formed in the end plate surface, and the one opening end of the said path
  • carbon dioxide is used as the working fluid.
  • more oil is supplied to the compression chamber having a smaller suction volume than to the compression chamber having a larger suction volume.
  • a small compression chamber has a larger rate of pressure change and more leakage of working fluid than a compression chamber with a large suction volume, so that a large amount of oil is supplied to a compression chamber with a small suction volume, so that the suction volume is small.
  • Leakage loss in the compression chamber can be reduced, and a highly efficient scroll compressor can be realized.
  • the leak which passed through the lap contact part is suppressed, and oil supply is made intermittent. Thereby, it is possible to provide a scroll compressor in which the oil supply amount is minimized and the performance is improved.
  • the longitudinal cross-sectional view of the scroll compressor in Example 1 of this invention The principal part expanded sectional view of the compression mechanism part of the scroll compressor in a present Example.
  • Sectional drawing in the state which meshed the fixed scroll and the turning scroll of the scroll compressor in a present Example The characteristic view which shows the pressure rise curve of the 1st compression chamber of the scroll compressor in a present Example, and a 2nd compression chamber
  • Sectional drawing in the state which meshed the fixed scroll and the turning scroll of the scroll compressor in a present Example Sectional drawing in the state which meshed the fixed scroll and the turning scroll of the scroll compressor in a present Example
  • Sectional drawing in the state which meshed the fixed scroll and the turning scroll of the scroll compressor in a present Example Sectional drawing in the state which meshed the fixed scroll and the turning scroll of the scroll compressor in a present Example
  • Sectional drawing in the state which meshed the fixed scroll and the turning scroll of the scroll compressor in a present Example The conceptual diagram of the oil supply path
  • the principal part expanded sectional view of the compression mechanism part of the scroll compressor in Example 5 of this invention Sectional drawing which shows the state which meshed the turning scroll and fixed scroll of the scroll compressor in Example 4 and Example 6 The principal part expanded sectional view of the compression mechanism part of the scroll compressor in Example 6 of this invention Sectional drawing which shows the state which meshed the turning scroll and fixed scroll of the scroll compressor in a present Example.
  • the principal part expanded sectional view of the compression mechanism part of the scroll compressor in Example 7 of this invention The top view which shows the turning scroll of the scroll compressor in a present Example.
  • Sectional drawing which shows the state which fixed the fixed scroll and the turning scroll of the scroll compressor in a present Example
  • the top view which shows the turning scroll of the scroll compressor in a present Example.
  • Sectional drawing which shows the state which fixed the fixed scroll and the turning scroll of the scroll compressor in a present Example
  • the principal part expanded sectional view of the compression mechanism part of the scroll compressor in Example 9 of this invention The partially expanded plan view which shows the turning scroll of the scroll compressor in a present Example.
  • Sectional drawing which shows the compression mechanism part of the conventional scroll compressor Sectional view of the conventional scroll compressor with the fixed scroll and the orbiting scroll engaged
  • the scroll compressor according to the first embodiment of the present invention includes a fixed scroll and an orbiting scroll in which a spiral wrap rises from an end plate, a shaft that drives the orbiting scroll, and a fixed scroll and an orbiting scroll that are engaged with each other.
  • a compression chamber formed, and an oil storage section for storing oil, wherein a suction volume of the first compression chamber formed on the outer wall side of the orbiting scroll is formed on the inner wall side of the orbiting scroll.
  • a fixed tip clearance formed between the wrap tip of the fixed scroll and the wrap side end plate surface of the orbiting scroll is provided with the orbiting scroll. This is smaller than the turning tip clearance formed between the wrap tip and the wrap side end plate surface of the fixed scroll.
  • the influence of leakage that is, leakage from the first compression chamber to the second compression chamber
  • the leakage loss greatly affects the leakage that occurs between the second compression chambers, and the effect of making the total oil supply amount to the second compression chamber larger than the total oil supply amount to the first compression chamber. Appears prominently.
  • a pump is provided at one end of a shaft, and a suction port of the pump is provided in an oil storage section. According to the present embodiment, refueling can be reliably performed regardless of pressure conditions and operation speed.
  • the closed position of the first compression chamber and the closed position of the second compression chamber are shifted by approximately 180 degrees. It is what. According to the present embodiment, the influence of suction heating can be reduced. Moreover, since the maximum suction volume can be ensured, the wrap height can be set low. As a result, it is possible to reduce the leakage gap of the lap contact portion, thereby further reducing leakage loss.
  • a high pressure region and a back pressure chamber are formed on the back surface of the orbiting scroll, and a plurality of oil supply paths are provided. Some or all of them pass through the back pressure chamber.
  • the orbiting scroll is stably pressed against the fixed scroll by applying pressure to the back of the orbiting scroll. As a result, leakage can be reduced and stable operation can be performed.
  • by providing a plurality of oil supply paths it is possible to supply oil to a required part as much as necessary.
  • a seal member is disposed on the back of the orbiting scroll, the inside of the seal member is a high pressure region, and the outside of the seal member is a back pressure chamber.
  • at least one of the oil supply paths includes a back pressure chamber oil supply path from the high pressure region to the back pressure chamber and a compression chamber oil supply path from the back pressure chamber to the second compression chamber.
  • the seventh embodiment of the present invention is such that, in the scroll compressor according to the sixth embodiment, the open end of the back pressure chamber oil supply path goes around the seal member.
  • the amount of oil supplied to the back pressure chamber can be controlled by the ratio of the open end of the back pressure chamber oil supply path coming and going from the seal member. For this reason, it is possible to control the minimum amount of fuel supply and prevent excessive supply. That is, since it is not necessary to reduce the diameter of the oil supply path, it is possible to prevent the oil supply path from being blocked by foreign matter and maintain a stable back pressure.
  • the second compression chamber in which the back pressure chamber communicates with the compression chamber oil supply path confines the working fluid. This is the compression chamber after According to the present embodiment, it is possible to prevent a so-called tilting phenomenon in which the orbiting scroll is separated from the fixed scroll and the ability is reduced. Even if tilting occurs, the pressure in the second compression chamber can be guided to the back pressure chamber. Therefore, early return to normal operation is possible.
  • the compression chamber oil supply path includes a passage formed inside the orbiting scroll and a lap side end plate surface of the fixed scroll.
  • the back pressure chamber and the second compression chamber are intermittently communicated by the opening end of the passage periodically opening to the recess in accordance with the turning motion.
  • the back pressure chamber and the second compression chamber are intermittently communicated, whereby the pressure fluctuation in the back pressure chamber can be suppressed and controlled to a predetermined pressure.
  • the oil supply paths that lead from the oil storage section to the first compression chamber and the second compression chamber are respectively The oil supply path and the second oil supply path are provided, and the same number or more of the second oil supply paths are provided with respect to the first oil supply path. According to the present embodiment, it is possible to reliably increase the amount of oil supplied to the second compression chamber.
  • At least one of the oil supply paths is an intermittent oil supply path for intermittent communication.
  • the amount of oil supplied into the second compression chamber can be minimized by making the oil supply intermittent. Therefore, viscosity loss due to excessive oil supply can be reduced.
  • at least one of the intermittent oil supply paths opens an opening end in the compression chamber before confining the working fluid. . According to the present embodiment, when the working fluid is confined, the sealing effect of the compression chamber is enhanced by the oil, and the decrease in volume efficiency due to the suction heating due to excessive oil supply can be prevented.
  • a thirteenth embodiment of the present invention forms a high pressure region and a back pressure chamber on the back surface of the orbiting scroll, and at least one of the intermittent oil supply paths is It communicates with the high pressure area. According to the present embodiment, it is possible to increase the amount of oil supplied to the compression chamber due to the pressure difference during high differential pressure conditions. Therefore, it becomes possible to further improve the reliability of the compressor.
  • a fourteenth embodiment of the present invention forms a high pressure region and a back pressure chamber on the back of the orbiting scroll, and at least one of the intermittent oil supply paths is It goes through the back pressure chamber.
  • a fifteenth embodiment of the present invention forms a high pressure region and a back pressure chamber on the back surface of the orbiting scroll, and at least one of the intermittent oil supply paths is The connecting path connects the back pressure chamber from the high pressure region and the supply path connects the back pressure chamber and the compression chamber.
  • excessive pressure increase in the back pressure chamber is achieved by supplying the high pressure oil from the high pressure region to the back pressure chamber and pressing the back surface of the orbiting scroll while allowing the back pressure chamber and the compression chamber to communicate with each other.
  • the open end of the connection path is used as a seal member that partitions the high pressure region and the back pressure chamber provided on the back surface of the orbiting scroll.
  • the amount of oil supply to the back pressure chamber can be finely adjusted by the ratio of the opening end of the connection path coming and going from the seal member, and excessive supply can be prevented.
  • it is not necessary to reduce the diameter of the oil supply path it is possible to prevent the oil supply path from being blocked by foreign matter and maintain a stable back pressure.
  • the supply path communicates with the compression chamber after the working fluid is confined. According to the present embodiment, it is possible to prevent a so-called tilting phenomenon in which the orbiting scroll is separated from the fixed scroll and the ability is reduced. Further, even if tilting occurs, the pressure in the compression chamber can be guided to the back pressure chamber, so that an early return to normal operation is possible. According to an eighteenth embodiment of the present invention, in the scroll compressor according to the fifteenth to seventeenth embodiments, the supply path communicates with the second compression chamber.
  • the amount of oil supplied to the second compression chamber can be made larger than the amount of oil supplied to the first compression chamber, and the second compression chamber closed next to the first compression chamber is closed. It is possible to further enhance the effect of preventing leakage between the two compression chambers.
  • the supply path is formed on the passage formed in the orbiting scroll and the lap side end plate surface of the fixed scroll. It is comprised from a recessed part, and one opening end of a channel
  • the back pressure chamber and the compression chamber are intermittently communicated, whereby the pressure fluctuation in the back pressure chamber can be suppressed and controlled to a predetermined pressure.
  • the intermittent oil supply path is formed in a passage formed in the orbiting scroll and a lap side end plate surface of the fixed scroll. The one opening end of the passage is periodically opened to the recess in accordance with the turning motion.
  • the intermittent oil supply path can be communicated to an arbitrary point by the arrangement of the recess and the position adjustment of the passage, so that excessive oil supply is suppressed and performance deterioration due to viscosity loss is prevented. Can do.
  • the oil supply path is opened to a lap tip oil supply route for supplying oil to the lap tip of the orbiting scroll and the second compression chamber. And an oil supply amount control path.
  • the oil supply path for supplying effective oil against the leakage through the wrap tip of the orbiting scroll and the leakage through the spiral wrap side surface, the sealing performance between the compression chambers is secured.
  • useless work such as oil biting due to excessive refueling is not generated, so that a highly efficient scroll compressor can be provided.
  • the lap tip oil supply path is configured by a passage passing through the inside of the orbiting scroll and an oil groove provided at the lap tip of the orbiting scroll. Is. According to the present embodiment, since the oil supplied to the wrap tip is supplied to a wider range of wrap tips via the oil groove, the sealing property between the first compression chamber and the second compression chamber is A wider range can be secured.
  • the twenty-third embodiment of the present invention is the scroll compressor according to the twenty-first or twenty-second embodiment, wherein a high pressure region and a back pressure chamber are formed on the back surface of the orbiting scroll, and the wrap tip oil supply path is formed between the high pressure region and the back pressure chamber. It goes through the pressure chamber.
  • the present embodiment when oil is supplied to the compression chamber via the gap between the wrap tips, the differential pressure is reduced, and it is possible to suppress the expansion noise during oil supply. Therefore, it is possible to provide a scroll compressor capable of suppressing the generation of noise and supplying oil to the wrap tip and the compression chamber.
  • a scroll compressor capable of suppressing the generation of noise and supplying oil to the wrap tip and the compression chamber.
  • a high pressure region and a back pressure chamber are formed on the back surface of the orbiting scroll, and the lap tip oil supply path is provided with the back pressure chamber. It goes through only the high pressure region without going through. According to the present embodiment, it is possible to provide the lap tip oil supply path up to the lap tip facing the compression chamber on the higher pressure side.
  • the twenty-fifth embodiment of the present invention is a scroll compressor according to the twenty-first to twenty-fourth embodiments, wherein at least one of the wrap tip oil supply passages supplies oil to the compression chamber before confining the working fluid. It is composed. According to the present embodiment, oil is supplied from the oil supply amount control path to the first and second compression chambers before the oil is supplied, and leakage during the compression chamber formation or immediately after the compression chamber formation can be suppressed. Become.
  • the oil supply amount control path and the lap end oil supply path described in the twenty-first embodiment work in a complementary manner, and a scroll compressor that enables more effective oil supply can be provided.
  • a scroll compressor that enables more effective oil supply can be provided in the scroll compressor according to the twenty-first to twenty-fifth embodiments.
  • a high pressure region and a back pressure chamber are formed on the back surface of the orbiting scroll, and at least one of the oil supply amount control paths is , A connection path for supplying oil from the high pressure region to the back pressure chamber, and a supply path A for communicating the back pressure chamber and the second compression chamber.
  • the amount of oil supplied to the second compression chamber via the supply path A can be controlled in the connection path, and a stable back pressure is applied to the orbiting scroll back surface. It is possible to provide a scroll compressor in which leakage through the wrap tip gap is suppressed.
  • the open end of the connection path is used as a seal member that separates the high-pressure region and the back-pressure chamber provided on the back surface of the orbiting scroll. To do.
  • the supply path A communicates with the second compression chamber after the working fluid is confined.
  • the oil supplied through the supply path A is limited after the formation of the second compression chamber, so that the controlled oil amount can be reliably supplied to the second compression chamber.
  • the oil pressure supplied via the supply path A can be controlled by the pressure in the compression chamber.
  • the pressure in the back pressure chamber can be controlled by the pressure in the second compression chamber in which the supply path A opens, a scroll compressor to which an appropriate back pressure is applied can be provided.
  • the supply path A is formed on the passage formed in the orbiting scroll and the lap side end plate surface of the fixed scroll. The one opening end of the passage is periodically opened to the recess in accordance with the turning motion.
  • the back pressure chamber and the second compression chamber can be communicated with each other only in a specific section in the compression stroke where the pressure in the second compression chamber increases.
  • the 30th embodiment of the present invention uses carbon dioxide as a working fluid in the scroll compressor according to the 1st to 29th embodiments. According to the present embodiment, even if the operating pressure is high and the pressure difference between the compression chambers becomes large, it is possible to effectively suppress the leakage of the second compression chamber accompanying the pressure increase. That is, the effect of the present invention is remarkably exhibited, and a scroll compressor that realizes high efficiency and high reliability can be provided.
  • FIG. 1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1 of the present invention
  • FIG. 2 is an enlarged sectional view of a main part of a compression mechanism portion of the scroll compressor according to this embodiment.
  • the scroll compressor according to this embodiment includes a sealed container 1 including a compression mechanism 2, a motor unit 3, and an oil storage unit 20 that stores oil 6.
  • the compression mechanism 2 is fixed in the sealed container 1 by welding, shrink fitting, or the like, and supports a main bearing member 11 that supports the shaft 4, a fixed scroll 12 that is bolted onto the main bearing member 11, a fixed scroll 12, And the orbiting scroll 13 engaged with each other.
  • a spiral wrap rises from the end plates of the fixed scroll 12 and the orbiting scroll 13 and meshes with the wraps of the fixed scroll 12 and the orbiting scroll 13 to form a compression chamber 15 therebetween.
  • a rotation restraining mechanism 14 made of an Oldham ring or the like that guides the orbiting scroll 13 to rotate in a circular orbit while preventing rotation.
  • the orbiting scroll 13 is moved in a circular orbit by driving the orbiting scroll 13 eccentrically at the eccentric shaft portion 4 a at the upper end of the shaft 4.
  • the compression chamber 15 moves while reducing the volume from the outer peripheral side toward the central portion.
  • the working fluid is sucked from the suction pipe 16 communicating with the outside of the hermetic container 1 and the suction port 17 on the outer periphery of the fixed scroll 12, confined in the compression chamber 15 and compressed.
  • the working fluid that has reached a predetermined pressure pushes open the reed valve 19 and is discharged into the sealed container 1 from the discharge port 18 at the center of the fixed scroll 12.
  • a pump 25 is provided at one end of the shaft 4 and is arranged so that a suction port of the pump 25 exists in the oil storage unit 20.
  • the pump 25 is driven simultaneously with the scroll compressor. Therefore, the pump 25 reliably sucks up the oil 6 in the oil storage unit 20 provided at the bottom of the hermetic container 1 regardless of the pressure condition and the operation speed. This eliminates the worry of running out of oil. Then, the oil 6 sucked up by the pump 25 is supplied to the compression mechanism 2 through an oil supply hole 26 running vertically through the shaft 4. If foreign matter is removed from the oil 6 with an oil filter or the like before or after the oil 25 is sucked up by the pump 25, foreign matter can be prevented from entering the compression mechanism 2 and further reliability can be improved.
  • the pressure of the oil 6 guided to the compression mechanism 2 is substantially equal to the discharge pressure of the scroll compressor, and becomes a back pressure source for the orbiting scroll 13.
  • the orbiting scroll 13 does not move away from the fixed scroll 12 and does not come into contact with each other, and the predetermined compression function is stably exhibited.
  • a part of the oil 6 enters the fitting portion between the eccentric shaft portion 4 a and the orbiting scroll 13 and the bearing portion 76 between the shaft 4 and the main bearing member 11 due to supply pressure and its own weight. And after lubricating each part, it falls, and returns to the oil storage part 20.
  • FIG. 3 is a cross-sectional view showing a state in which the turning scroll 13 is engaged with the fixed scroll 12.
  • the compression chamber 15 formed by the fixed scroll 12 and the orbiting scroll 13 includes a first compression chamber 15a formed on the wrap outer wall side 13o of the orbiting scroll 13 and a wrap inner wall side 13i. And a second compression chamber 15b.
  • the suction volume of the first compression chamber 15a is larger than the suction volume of the second compression chamber 15b. That is, since the timing for confining the working fluid is different, the pressures of the first compression chamber 15a and the second compression chamber 15b which are paired are also different.
  • FIG. 4 is a characteristic diagram showing the pressure rise curves of the first compression chamber 15a and the second compression chamber 15b.
  • the second compression chamber 15b having a smaller suction volume has a higher pressure change rate than the first compression chamber 15a. That is, the pressure difference ⁇ Pb between the second compression chamber 15b-1 formed immediately before and the second compression chamber 15b-2 formed next is the same as that between the first compression chamber 15a-1 and the first compression chamber 15b-1. It can be seen that the pressure difference ⁇ Pa of the compression chamber 15a-2 is larger. Therefore, with respect to the second compression chamber 15b, the working fluid is likely to leak through the radial contact portion of the wrap.
  • an oil supply path 50 is provided that leads from the oil storage section 20 to the first compression chamber 15a and / or the second compression chamber 15b, and the total oil supply amount to the second compression chamber 15b is provided. Is greater than the total amount of oil supplied to the first compression chamber 15a.
  • FIG. 5 is a conceptual diagram of an oil supply path.
  • an oil supply path 50 indicated by a solid line or a broken line corresponds to, for example, the back pressure chamber oil supply path 51 and the compression chamber oil supply path 52 shown in FIG. 2.
  • an oil supply path 50 indicated by a broken line means an oil supply path that may be additionally installed in addition to the oil supply path 50 indicated by a solid line.
  • the oil supply supplied from the oil supply paths 50 to the first compression chamber 15a and the second compression chamber 15b is set to satisfy the relationship of “Ga ⁇ Gb” where Ga is the amount of oil supplied to the first compression chamber 15a and Gb is the amount of oil supplied to the second compression chamber 15b.
  • Ga is the amount of oil supplied to the first compression chamber 15a
  • Gb is the amount of oil supplied to the second compression chamber 15b.
  • FIG. 6 is a cross-sectional view showing a state in which the turning scroll 13 is engaged with the fixed scroll 12.
  • leakage occurring through the fixed tip clearance 12d formed between the wrap tip 12c of the fixed scroll 12 and the wrap side end plate surface 13f of the orbiting scroll 13 can be understood from FIG.
  • leakage from the first compression chamber 15a-2 to the second compression chamber 15b-2, leakage from the first compression chamber 15a-1 to the second compression chamber 15b-2, and the first compression chamber This is a leak from 15a-1 to the second compression chamber 15b-1. That is, the only leakage that occurs through the fixed tip clearance 12d is leakage from the first compression chamber 15a to the second compression chamber 15b.
  • the leakage generated through the turning tip clearance 13d formed between the wrap tip 13c of the orbiting scroll 13 and the lap side end plate surface 12e of the fixed scroll 12 is the first compression chamber 15a-2.
  • the second compression chamber 15b-2 from the second compression chamber 15b-1 to the first compression chamber 15a-2, from the first compression chamber 15a-1 to the second compression chamber 15b- Leak to 1. That is, both leakage from the first compression chamber 15a to the second compression chamber 15b and leakage from the second compression chamber 15b to the first compression chamber 15a exist. Therefore, in this embodiment, the fixed tip clearance 12d is made smaller than the turning tip clearance 13d. With this configuration, it is possible to reduce the influence of leakage from the first compression chamber 15a to the second compression chamber 15b.
  • the leakage loss greatly affects leakage occurring between the second compression chambers 15b.
  • the second compression chamber 15b-1 to the second compression chamber 15b-2. Is a leak.
  • the effect of making the total oil supply amount to the second compression chamber 15b larger than the total oil supply amount to the first compression chamber 15a appears remarkably.
  • the fixed scroll 12 and the orbiting scroll 13 are made of different materials, and the thermal expansion coefficient of the orbiting scroll 13 is larger than the thermal expansion coefficient of the fixed scroll 12, the fixed tip clearance 12d and the orbiting tip clearance 13d are fixed. It is necessary to set in consideration of the thermal expansion difference between the scroll 12 and the orbiting scroll 13. That is, since the turning tip clearance 13d needs to be set larger than the fixed tip clearance 12d, the effect of increasing the total amount of oil supplied to the second compression chamber 15b appears more remarkably.
  • the spiral wrap is configured such that the position where the working fluid in the first compression chamber 15a is confined and the position where the working fluid in the second compression chamber 15b is confined are shifted by approximately 180 degrees.
  • the spiral wrap of the fixed scroll 12 is extended to the same extent as the spiral wrap of the orbiting scroll 13.
  • the position where the first compression chamber 15a confines the working fluid is point S in FIG. That is, after confining the first compression chamber 15a, the second compression chamber 15b confines the working fluid after the rotation of the shaft 4 has advanced by about 180 degrees.
  • a high pressure region 30 and a back pressure chamber 29 set to a high pressure and a low pressure are formed on the back surface 13 e of the orbiting scroll 13. And the pressure of the high pressure area
  • a compression chamber oil supply path 52 (which constitutes a part of the oil supply path 50) that connects the back pressure chamber 29 and the compression chamber 15 is provided, and a part or all of the oil supply path passes through the back pressure chamber 29.
  • the required minimum Minimal refueling is possible. That is, excessive oil supply can be prevented, and a decrease in performance due to suction heating and an increase in input due to viscosity loss can be suppressed.
  • a seal member 78 is disposed on the back surface 13 e of the orbiting scroll 13.
  • the inside of the seal member 78 is partitioned into the high pressure region 30 and the outside of the seal member 78 is partitioned into the back pressure chamber 29.
  • the oil supply path 50 is connected through a plurality of paths including a back pressure chamber oil supply path 51 from the high pressure region 30 to the back pressure chamber 29 and a compression chamber oil supply path 52 from the back pressure chamber 29 to the second compression chamber 15b. Is configured. With the configuration using the sealing member 78 described above, the pressure in the high pressure region 30 and the back pressure chamber 29 can be completely separated. Therefore, it is possible to stably control the pressure application to the back surface 13e of the orbiting scroll 13.
  • a compression chamber oil supply path 52 from the back pressure chamber 29 to the second compression chamber 15b is provided.
  • the compression chamber oil supply path 52 is formed inside the orbiting scroll 13 and has the other opening end 52a that opens to the back pressure chamber 29 and one opening end 52b that opens to the second compression chamber 15b.
  • the back pressure chamber 29 and the second compression chamber 15b are configured to communicate with each other. With this configuration, the amount of oil supplied to the second compression chamber 15b can be positively increased, and leakage loss in the second compression chamber 15b can be suppressed.
  • one open end 51 b of the back pressure chamber oil supply path 51 is formed on the back surface 13 e of the orbiting scroll 13, and the seal member 78 is moved back and forth, and the other open end 51 a is moved to the high pressure region 30.
  • FIG. 7 is a cross-sectional view showing a state where the orbiting scroll 13 is engaged with the fixed scroll 12. That is, it is the state seen from the back of the orbiting scroll 13, and is a figure in which the phase is shifted by 90 degrees.
  • the rear region of the orbiting scroll 13 is partitioned by the seal member 78 into an inner high pressure region 30 and an outer back pressure chamber 29.
  • the opening end 51 b opens to the back pressure chamber 29 that is outside the seal member 78, the oil 6 is supplied to the back pressure chamber 29.
  • the opening end 51 b is opened inside the seal member 78, so that the oil 6 is supplied to the back pressure chamber 29. There is no. That is, only when the opening end 51b of the back pressure chamber oil supply passage 51 moves back and forth between the high pressure region 30 and the back pressure chamber 29, a pressure difference occurs between the two opening ends 51a and 51b of the back pressure chamber oil supply passage 51. Oil 6 is supplied to the back pressure chamber 29. With this configuration, the amount of oil supply can be adjusted at a rate at which the opening end 51b travels the seal member 78, so that the passage diameter of the back pressure chamber oil supply passage 51 is 10 times or more larger than that of the oil filter. It is possible to configure with dimensions.
  • the thrust sliding portion and the rotation restraint mechanism 14 can be kept in good condition simultaneously with the stable application of the back pressure. That is, a scroll compressor that realizes high efficiency and high reliability can be provided.
  • the configuration in which the opening end 51a is always in the high pressure region 30 and the opening end 51b travels between the high pressure region 30 and the back pressure chamber 29 has been described as an example. Even in a configuration in which the pressure chamber 29 is moved back and forth and the opening end 51b is always in the back pressure chamber 29, a pressure difference is generated between the opening ends 51a and 51b, so that intermittent oil supply can be realized and the same effect can be obtained.
  • the compression chamber oil supply path 52 is configured so that the second compression chamber 15b after the working fluid is confined and the back pressure chamber 29 communicate with each other. With this configuration, the pressure in the back pressure chamber 29 becomes a predetermined pressure higher than the suction pressure. Therefore, the tilting phenomenon can be prevented and high efficiency can be realized. Even if tilting occurs, the pressure in the second compression chamber 15b can be guided to the back pressure chamber 29, so that early return to normal operation is possible.
  • FIG. 8 is an enlarged cross-sectional view of a main part of the compression mechanism portion of the scroll compressor according to the second embodiment of the present invention.
  • the oil supply path 50 includes a back pressure chamber oil supply path 51 and a compression chamber oil supply path 55.
  • the compression chamber oil supply path 55 includes a passage 55c formed inside the orbiting scroll 13 and having an opening end 55a and an opening end 55b, and a recess 12b formed on the lap side end plate surface 12e of the fixed scroll 12. Has been. Then, one opening end 55b of the passage 55c is formed in the wrap tip 13c, and is periodically opened in the recess 12b in accordance with the turning motion. Further, the other open end 55a of the passage 55c is always opened in the back pressure chamber 29. Thereby, the back pressure chamber 29 and the second compression chamber 15b are intermittently communicated.
  • 8A shows a state in which the opening end 55b opens to the recess 12b
  • FIG. 8B shows a state in which the opening end 55b does not open to the recess 12b. Yes.
  • FIG. 9 is a cross-sectional view showing a state in which the orbiting scroll 13 is engaged with the fixed scroll 12, and the phase is shifted by 90 degrees.
  • intermittent communication is achieved by periodically opening the opening end 55 b of the passage 55 c formed inside the orbiting scroll 13 into the recess 12 b formed on the lap side end plate surface of the fixed scroll 12. It is realized.
  • the opening end 55b opens into the recess 12b.
  • the oil 6 in the back pressure chamber 29 is intermittently guided to the second compression chamber 15b through the passage 55c, so that pressure fluctuations in the back pressure chamber 29 can be suppressed. That is, the pressure in the back pressure chamber 29 can be controlled to a predetermined pressure.
  • the oil 6 supplied to the second compression chamber 15b can play a role of improving the sealing performance and lubricity during compression.
  • FIG. 10 is a conceptual diagram of an oil supply path of the scroll compressor according to the third embodiment of the present invention.
  • the oil supply path 50 that leads from the oil storage section 20 to the first compression chamber 15a and the second compression chamber 15b is connected to the plurality of first oil supply paths 53.
  • a plurality of second oil supply paths 54 a plurality of second oil supply paths 54.
  • the number of second oil supply paths 54 is equal to or more than the number of first oil supply paths 53. That is, when the number of the first oil supply paths 53 is m and the number of the second oil supply paths 54 is n, the relationship of “m ⁇ n” is established.
  • the number of first oil supply paths 53 and the number of second oil supply paths 54 are the same, and each of the second oil supply paths 54 having the same amount of oil supply with respect to the oil supply amount of each of the first oil supply paths 53. Therefore, if the oil supply path 50 is formed, the amount of oil supplied to the first compression chamber 15a is equal to the amount of oil supplied to the second compression chamber 15b. Therefore, if the second oil supply path 54 is further added and formed, the amount of oil supplied to the second compression chamber 15b can be surely increased. Further, when the number of the first oil supply paths 53 and the number of the second oil supply paths 54 is the same, the second compression in which the oil supply path 54 opens than the average pressure of the first compression chamber 15a in which the oil supply path 53 opens.
  • the amount of oil supplied to the second compression chamber 15b can be increased.
  • the passage 55c formed in the orbiting scroll 13 and the recess formed in the fixed scroll 12 are used.
  • route 55 which consists of a combination with 12b in several places.
  • the broken line oil supply path 50 described in the first embodiment can also be formed by a combination of such a passage and a recess.
  • the second oil supply paths 53 and 54 may be configured to pass through the back pressure chamber 29.
  • FIG. 11 is an enlarged cross-sectional view of a main part of the compression mechanism portion of the scroll compressor according to the fourth embodiment of the present invention.
  • an invention part different from the first embodiment will be described. That is, in the scroll compressor of the present embodiment, the same reference numerals are used for the same components as in the first embodiment, and the description of the configurations and operations is omitted.
  • FIG. 11 in the scroll compressor of the present embodiment, one or a plurality of oil supply paths for guiding the oil 6 from the oil storage section 20 to the first compression chamber 15a and the second compression chamber 15b are provided. .
  • At least one of the oil supply paths is an intermittent oil supply path 56 that intermittently connects the oil storage unit 20 and the compression chamber 15, and the total oil supply amount to the second compression chamber 15 b is transferred to the first compression chamber 15 a. More than the total amount of refueling.
  • Ga is the amount of oil supplied to the first compression chamber 15a
  • Gb is the amount of oil supplied to the second compression chamber 15b
  • the relationship of “Ga ⁇ Gb” is set.
  • the intermittent oil supply path 56 of the present embodiment is formed in the passage 56 c having the opening end 56 a and the opening end 56 b formed in the orbiting scroll 13 and the lap side end plate surface of the fixed scroll 12. It is comprised from the recessed part 12b. Then, one open end 56b of the intermittent oil supply path 56 (the passage 56c thereof) is formed at the lap tip 13c of the orbiting scroll 13, and is periodically opened in the recess 12b in accordance with the orbiting motion. The other open end 56 a of the intermittent oil supply path 56 is always open to the high pressure region 30. Thereby, the high pressure area
  • one open end 56b of the intermittent oil supply path 56 is configured such that the second compression chamber 15b before confining the working fluid is opened.
  • FIG. 12 is a cross-sectional view illustrating a state in which the orbiting scroll 13 is engaged with the fixed scroll 12, and is a cross-sectional view illustrating the state before the second compression chamber 15b is confined and the state before the first compression chamber 15a is confined. .
  • the open end 56b of the intermittent oil supply path 56 (the passage 56c thereof) is opened through the recess 12b in the second compression chamber 15f-2 before the working fluid is confined. Yes.
  • FIG. 12 the open end 56b of the intermittent oil supply path 56 (the passage 56c thereof) is opened through the recess 12b in the second compression chamber 15f-2 before the working fluid is confined. Yes.
  • FIG. 12 the open end 56b of the intermittent oil supply path 56 (the passage 56c thereof) is opened through the recess 12b in the second compression chamber 15f-2 before the working fluid is confined. Yes.
  • the open end 56b of the intermittent oil supply path 56 is opened through the recess 12b in the first compression chamber 15f-1 before confining the working fluid.
  • the arrows in FIG. 12 each represent the flow of the oil 6.
  • a certain amount of seal oil is necessary.
  • suction heating of the working fluid occurs, resulting in a decrease in volumetric efficiency. Therefore, it is ideal to supply only the amount necessary for sealing. Therefore, by intermittently supplying oil, excessive oil supply can be prevented and performance degradation due to suction heating of the working fluid can be suppressed.
  • the opening end 56b of the intermittent oil supply path 56 is opened to the first compression chamber 15a and the second compression chamber 15b before the working fluid is confined.
  • the sealing effect of the compression chambers 15a and 15b can be enhanced by the oil 6, and a decrease in volumetric efficiency due to suction heating of the working fluid due to excessive oil supply can be prevented.
  • the chamber 29 is formed, and at least one of the intermittent oil supply paths 56 is configured to communicate with the high pressure region 30. According to this configuration, for example, during a high differential pressure operation, the pressure difference between the compression chamber 15 communicating with the high pressure region 30 is large, so that it is possible to increase the amount of oil supplied to the compression chamber 15 and prevent oil shortage. Thus, reliability can be improved.
  • FIG. 13 is a principal part expanded sectional view of the compression mechanism part of the scroll compressor in Example 5 of this invention, and has shown the intermittent oil supply path
  • a high pressure region 30 and a back pressure chamber 29 set to an intermediate pressure between high pressure and low pressure are formed on the back surface 13 e of the orbiting scroll 13.
  • the intermittent oil supply path 57 includes a passage 57c formed in the orbiting scroll 13 and having an opening end 57a and an opening end 57b, and a recess 12b formed on the lap side end plate surface of the fixed scroll 12.
  • one open end 57b of the intermittent oil supply passage 57 (the passage 57c thereof) is formed at the lap tip 13c, and is periodically opened in the recess 12b in accordance with the turning motion.
  • the other open end 57 a of the intermittent oil supply path 57 is always opened in the back pressure chamber 29.
  • the back pressure chamber 29 and the second compression chamber 15b are intermittently communicated. That is, in the scroll compressor of the above-described embodiment, at least one of the intermittent oil supply paths is configured to pass through the back pressure chamber. According to this configuration, since the pressure difference between the back pressure chamber 29 and the second compression chamber 15b is small, it is possible to suppress an expansion sound during refueling and to reduce noise during operation.
  • FIG. 14 is a cross-sectional view showing a state in which the orbiting scroll 13 is engaged with the fixed scroll 12, and the phase is shifted by 90 degrees.
  • the opening end 57 b formed at the lap tip 13 c of the orbiting scroll 13 periodically opens into the recess 12 b formed on the lap side end plate surface of the fixed scroll 12. Therefore, intermittent communication is realized.
  • the opening end 57b opens into the recess 12b.
  • the oil 6 is supplied from the back pressure chamber 29 to the second compression chamber 15b through the intermittent oil supply path 57.
  • the opening end 57b does not open to the recess 12b. Therefore, the oil 6 is not supplied from the back pressure chamber 29 to the second compression chamber 15b.
  • the oil 6 in the back pressure chamber 29 is intermittently guided to the second compression chamber 15 b through the intermittent oil supply path 57. Therefore, the pressure fluctuation of the back pressure chamber 29 can be suppressed, and it can be controlled to a predetermined pressure.
  • the oil 6 supplied to the second compression chamber 15b can play a role of improving the sealing property and the lubricating property at the time of compression.
  • the compression chamber communicating with the back pressure chamber 29 is the first compression chamber 15a, the same effect as described above can be obtained.
  • FIG. 15 is an enlarged cross-sectional view of a main part of the compression mechanism portion of the scroll compressor according to the sixth embodiment of the present invention.
  • an invention part different from the fourth embodiment will be described. That is, in the scroll compressor of the present embodiment, the same reference numerals are used for the same components as those in the fourth embodiment, and description of the configurations and operations is omitted.
  • the intermittent oil supply path as the oil supply path connects the high pressure region 30 provided on the back surface 13 e of the orbiting scroll 13 and the back pressure chamber 29. And a supply path 59 that allows the back pressure chamber 29 and the compression chamber 15 to communicate with each other.
  • the orbiting scroll 13 can be pressed against the fixed scroll 12 by sending the oil 6 from the high pressure region 30 to the back pressure chamber 29 and applying the pressure of the oil 6 to the back surface 13 e of the orbiting scroll 13. .
  • the back pressure chamber 29 and the compression chamber 15 communicate with each other, an excessive increase in the pressing force of the back pressure chamber 29 can be suppressed. Therefore, it is possible to apply a stable back pressure and suppress an increase in thrust sliding loss.
  • one open end 58 b of the connection path 58 is formed on the back surface 13 e of the orbiting scroll 13. The other open end 58 a is always open to the high pressure region 30.
  • a seal member 78 that partitions the back pressure chamber 29 and the high pressure region 30 is disposed on the back surface 13 e side of the orbiting scroll 13 of the main bearing member 11. Then, the opening end 58 b of the connection path 58 is configured to open alternately to the high pressure region 30 and the back pressure chamber 29 by going back and forth through the seal member 78 by the orbiting motion of the orbiting scroll 13. With this configuration, intermittent communication between the back pressure chamber 29 and the high pressure region 30 is realized.
  • FIG. 16 is a cross-sectional view showing a state in which the turning scroll 13 is engaged with the fixed scroll 12. That is, it is the state seen from the back surface 13e of the orbiting scroll 13, and is the figure which shifted the phase by 90 degree
  • a seal member 78 divides the back surface 13 e region of the orbiting scroll 13 into an inner high pressure region 30 and an outer back pressure chamber 29.
  • the open end 58 b opens to the back pressure chamber 29 that is outside the seal member 78. Therefore, the oil 6 is supplied to the back pressure chamber 29.
  • the opening end 58b opens to the high-pressure region 30 that is inside the seal member 78. Therefore, the oil 6 is not supplied to the back pressure chamber 29. That is, only when the opening end 58b of the connection path 58 moves back and forth between the high pressure region 30 and the back pressure chamber 29 and a pressure difference occurs between the opening ends 58a and 58b of the connection path 58, the oil is supplied to the back pressure chamber 29. 6 is supplied. With this configuration, the amount of oil supply to the back pressure chamber 29 can be finely adjusted by the ratio of the opening end 58b of the connection path 58 to and from the seal member 78, and excessive supply to the back pressure chamber 29 is prevented. be able to.
  • the oil supply can be adjusted at a rate at which the opening end 58b moves back and forth through the seal member 78. Therefore, the passage diameter of the connection path 58 can be configured with a large dimension that is 10 times or more that of the oil filter. With this configuration in which the passage diameter is increased, there is no possibility that foreign matter is caught in the passage and is blocked. Therefore, it is possible to provide a scroll compressor that can maintain a good state of lubrication of the thrust sliding portion and the rotation restraint mechanism 14 at the same time as the application of a stable back pressure and realize high efficiency and high reliability.
  • the configuration in which the opening end 58 a is always in the high-pressure region 30 and the opening end 58 b moves between the high-pressure region 30 and the back pressure chamber 29 has been described.
  • the opening end 58a goes back and forth between the high pressure region 30 and the back pressure chamber 29 and the opening end 58b is always in the back pressure chamber 29
  • a pressure difference is generated at both the opening ends 58a and 58b, so intermittent communication is realized. And the same effect can be obtained.
  • the supply path 59 is configured so that the compression chamber 15 and the back pressure chamber 29 after the working fluid is confined communicate with each other.
  • a configuration in which a supply path 59 is provided so that the second compression chamber 15b, which is one of the compression chambers 15 after confining the working fluid, and the back pressure chamber 29 communicate with each other will be described with reference to FIG.
  • the supply path 59 includes a passage 59c and a recess 12b.
  • the passage 59c has an opening end 59a and an opening end 59b, and is formed in the orbiting scroll 13.
  • the recess 12 b is formed on the lap side end plate surface of the fixed scroll 12.
  • one opening end 59b of the supply path 59 (the passage 59c thereof) is formed in the wrap tip 13c, and is periodically opened in the recess 12b in accordance with the turning motion. Further, the other open end 59 a of the supply path 59 is always opened in the back pressure chamber 29. With this configuration, the back pressure chamber 29 and the second compression chamber 15b are intermittently communicated.
  • the pressure in the back pressure chamber 29 becomes a predetermined pressure higher than the suction pressure. Therefore, the tilting phenomenon can be prevented and high efficiency can be realized. Even if tilting occurs, the pressure in the second compression chamber 15 b can be guided to the back pressure chamber 29. Therefore, early return to normal operation is possible. Further, the back pressure chamber 29 and the second compression chamber 15b are intermittently communicated with each other, whereby the pressure fluctuation in the back pressure chamber 29 can be suppressed and controlled to a predetermined pressure. Furthermore, in the scroll compressor of the present embodiment, the supply path 59 communicates with the second compression chamber 15b.
  • the amount of oil supplied to the second compression chamber 15b can be made larger than the amount of oil supplied to the first compression chamber 15a, and the second compression chamber 15b-1 closed immediately before the next compression chamber 15b-1 It is possible to further enhance the effect of preventing leakage to the second compression chamber 15b-2 that is closed.
  • the compression chamber 15 communicating with the back pressure chamber 29 is changed from the second compression chamber 15b to the first compression chamber by changing the position where the concave portion 12b is formed within the range of the lap side end plate surface of the fixed scroll 12 as appropriate. It can also be changed to 15a. Further, the same effect as that in the case of communicating with the second compression chamber 15b described above can be obtained.
  • the opening end 59b does not open to the recess 12b. Therefore, the oil 6 is not supplied from the back pressure chamber 29 to the second compression chamber 15b.
  • the oil 6 in the back pressure chamber 29 is intermittently guided to the second compression chamber 15b through the supply path 59. Therefore, the pressure fluctuation of the back pressure chamber 29 can be suppressed, and it can be controlled to a predetermined pressure.
  • the oil 6 supplied to the second compression chamber 15b can play a role of improving the sealing property and the lubricating property during compression.
  • the intermittent oil supply paths 56 and 57 and the intermittent oil supply path including the connection path 58 and the supply path 59 are formed in the passage formed in the orbiting scroll 13 and the fixed scroll. 12 and a concave portion formed in 12. And it is the structure which opens the opening end of a channel
  • an intermittent oil supply path can be formed at an arbitrary location by arranging the recesses and adjusting the position of the passage, so that excessive oil supply can be suppressed and performance degradation due to viscosity loss can be prevented. .
  • the intermittent oil supply path 56 described in FIG. 11 is formed.
  • the passage 56 c of the intermittent oil supply path 56 formed in the orbiting scroll 13 is configured to open to a recess 12 b formed on the lap side end plate surface of the fixed scroll 12.
  • One open end 56b of the intermittent oil supply path 56 (the passage 56c thereof) is formed at the lap tip 13c of the orbiting scroll 13, and is periodically opened in the recess 12b in accordance with the orbiting motion.
  • the other opening end 56 a of the intermittent oil supply path 56 is always opened to the high pressure region 30. Therefore, the intermittent oil supply path 56 shares a part of the path with the connection path 58 that allows the high pressure region 30 and the back pressure chamber 29 to communicate with each other. With the above configuration, the high pressure region 30 and the second compression chamber 15b are intermittently communicated.
  • a plurality of paths with the intermittent oil supply path 56 are formed.
  • the working fluid is a high-pressure refrigerant, for example, carbon dioxide
  • the operating pressure is particularly high, so that leakage increases.
  • the scroll compressor of the present invention leakage between the second compression chambers 15b due to pressure increase can be effectively suppressed. That is, the effect of the present invention is remarkably exhibited, and a scroll compressor that realizes high efficiency and high reliability can be provided.
  • FIG. 17 is an enlarged cross-sectional view of the main part of the compression mechanism of the scroll compressor according to the seventh embodiment of the present invention.
  • an invention part different from the first embodiment will be described. That is, in the scroll compressor of the present embodiment, the same reference numerals are used for the same components as those in the first embodiment and the description of the configurations and operations is omitted.
  • the compression chamber 15 includes a first compression chamber 15a formed on the wrap outer wall side 13o of the orbiting scroll 13 and a second compression chamber 15b formed on the wrap inner wall side 13i. And exist.
  • the suction volume of the first compression chamber 15a is larger than the suction volume of the second compression chamber 15b.
  • a spiral wrap contact point D2 that partitions the second compression chamber 15b-1 and the second compression chamber 15b-2 formed thereafter, and the first compression chamber 15a-1 and the first compression chamber 15b-1 formed thereafter.
  • the pressure increase rate of the second compression chamber 15b with respect to the crank rotation angle is faster than the pressure increase rate of the first compression chamber 15a, and as a result, the second pressure chamber partitioned by the spiral wrap side surface D2 shown in FIG.
  • the pressure difference between the compression chamber 15b-1 and the second compression chamber 15b-2 formed on the low pressure side becomes large. From this, compared with the 1st compression chamber 15a, a working fluid tends to leak through the spiral wrap side surface of the 2nd compression chamber 15b.
  • the wrap tip 13c of the orbiting scroll 13 has a wrap height that gradually increases from the winding start portion that is the central portion to the winding end portion that is the outer peripheral portion based on the result of measuring the temperature distribution during operation. As shown, a slope shape is provided.
  • a wrap tip oil supply path 83 that guides the oil 6 from the oil storage unit 20 to the lap tip 13 c is provided for leakage through one lap tip 13 c.
  • the lap tip oil supply path 83 includes the other opening end 83a that is formed inside the orbiting scroll 13 and opens to the high pressure region 30, and the one opening end 83b that is formed at the wrap tip 13c and opens to the compression chamber 15. And the high pressure region 30 and the compression chamber 15 are communicated with each other.
  • an oil supply amount control path for guiding the oil 6 from the oil storage section 20 to the second compression chamber 15b is provided from the high pressure region 30 to the back pressure chamber 29.
  • a connection path 65 for supplying oil and a supply path A66 for communicating the back pressure chamber 29 and the second compression chamber 15b are configured.
  • the total oil supply amount to the second compression chamber 15b is supplied to the first compression chamber 15a by the oil supply route having the oil supply amount control path including the connection path 65 and the supply path A66 and the lap tip oil supply path 83.
  • the leakage loss in the compression stroke can be effectively reduced by increasing the amount of oil supply. Therefore, it is possible to provide a scroll compressor that realizes high efficiency.
  • FIG. 18 is a plan view showing the orbiting scroll of the scroll compressor in the present embodiment.
  • the step 66d communicates with one opening end 66b of the supply path A66 and opens to the second compression chamber 15b side which is the inner wall side compression chamber.
  • the oil 6 that has passed through one opening end 66b from the other opening end 66a of the supply path A66 is preferentially supplied from the step 66d to the second compression chamber 15b. That is, out of the oil 6 necessary for ensuring the sealing performance of the spiral wrap side surface, the extra oil 6 necessary for the first compression chamber 15a is adjusted by the supply path A66 of the oil supply amount control path.
  • the second compression chamber 15b can be supplied.
  • a high pressure region 30 and a back pressure chamber 29 set to a high pressure and a low pressure are formed on the back surface 13e of the orbiting scroll 13 so that at least one of the oil supply paths passes through the back pressure chamber 29.
  • the orbiting scroll 13 is stably pressed against the fixed scroll 12 by applying pressure to the back surface 13e. Therefore, leakage from the back pressure chamber 29 to the compression chamber 15 can be reduced and stable operation can be performed.
  • a plurality of oil supply paths that is, the oil supply amount control path and the lap tip oil supply path 83, it is possible to supply oil to the necessary portions as much as necessary.
  • a plurality of open ends 83 b of the lap tip oil supply passage 83 are formed.
  • At least one of the lap tip oil supply paths is configured with a path for supplying oil to the compression chamber before the working fluid is confined.
  • the oil is supplied to the first compression chamber and the second compression chamber before the oil is supplied from the oil supply amount control path, and leakage at the time of forming the compression chamber or immediately after the formation of the compression chamber is prevented. Can be suppressed.
  • the oil supply amount control path and the lap tip oil supply path work in a complementary manner, and more effective oil supply can be performed. Furthermore, an increase in input due to a decrease in volumetric efficiency or a viscosity loss can be avoided.
  • a seal member 78 is arranged on the back surface 13 e of the orbiting scroll 13, and the inner peripheral side of the seal member 78 is partitioned into the high pressure region 30 and the outer peripheral side of the seal member 78 is partitioned into the back pressure chamber 29. And, at least one of the oil supply paths, for example, the oil supply amount control path, from the connection path 65 from the high pressure region 30 to the back pressure chamber 29 and the supply path A66 from the back pressure chamber 29 to the second compression chamber 15b. Make up. By using the seal member 78, the pressure in the high pressure region 30 and the back pressure chamber 29 can be completely separated.
  • the oil 6 can be supplied to the sliding portion of the rotation restraint mechanism 14 and the thrust sliding portion of the fixed scroll 12 and the orbiting scroll 13. it can.
  • the supply path A66 from the back pressure chamber 29 to the second compression chamber 15b the amount of oil supplied to the second compression chamber 15b can be positively increased, and leakage in the second compression chamber 15b can be achieved. Loss can be suppressed.
  • FIG. 19 is a cross-sectional view showing a state in which the turning scroll 13 is engaged with the fixed scroll 12. That is, it is the state seen from the back of the orbiting scroll 13, and is a figure in which the phase is shifted by 90 degrees. As shown in FIG. 19, the rear region of the orbiting scroll 13 is partitioned by a seal member 78 into an inner high pressure region 30 and an outer back pressure chamber 29. In the state of FIG.
  • the open end 65 b is open to the back pressure chamber 29 that is outside the seal member 78, so that the oil 6 is supplied to the back pressure chamber 29.
  • the opening end 65b is opened inside the seal member 78, so that the oil 6 is supplied to the back pressure chamber 29.
  • the opening end 65 b of the connection path 65 is configured to travel between the high pressure region 30 and the back pressure chamber 29. Therefore, the oil 6 is supplied to the back pressure chamber 29 only when a pressure difference is generated between the two open ends 65 a and 65 b of the connection path 65.
  • the passage diameter of the connection path 65 can be configured with a large dimension that is 10 times or more that of the oil filter.
  • the passage diameter is increased, there is no possibility that foreign matter is caught in the passage and is blocked. Therefore, it is possible to provide a scroll compressor that can maintain the thrust sliding portion and the lubrication of the rotation restraint mechanism 14 in a good state simultaneously with the application of a stable back pressure, and realize high efficiency and high reliability.
  • the opening end 65a is always in the high pressure region 30 and the opening end 65b travels between the high pressure region 30 and the back pressure chamber 29 has been described as an example.
  • the opening end 65a is in the high pressure region. 30 and the back pressure chamber 29, and even when the opening end 65b is always in the back pressure chamber 29, a pressure difference occurs between the opening ends 65a and 65b, so that intermittent lubrication can be realized and the same effect can be obtained. It is done.
  • FIG. 20 is an enlarged cross-sectional view of a main part of the compression mechanism portion of the scroll compressor according to the eighth embodiment of the present invention.
  • FIG. 21 is a plan view showing the scroll compressor in the present embodiment.
  • the oil supply to the compression chamber 15 is the same as that of the seventh embodiment except for the lap tip oil supply route and the oil supply amount control route, and therefore, the lap tip oil supply route and the oil supply amount control route will be described. That is, in the scroll compressor of the present embodiment, the same reference numerals are used for the same components as those in the seventh embodiment, and description of the configurations and operations is omitted. As shown in FIGS.
  • the wrap end oil supply path 84 is provided inside the wrapping scroll 13 and inside the wrap, and has an opening end 84 a that opens to the high-pressure region 30 and the compression.
  • the passage 84c has an opening end 84b that opens into the chamber 15, and an oil groove 84d provided in the wrap tip 13c. At this time, the passage 84c is formed in communication with the oil groove 84d.
  • the wrap tip oil supply path 84 does not pass through the back pressure chamber 29 but passes only through the high pressure region 30 so that the oil 6 is supplied directly from the high pressure region 30 to the lap tip 13c. Yes. Then, by opening the opening end 84a of the passage 84c into the high pressure region 30 formed on the back surface of the orbiting scroll 13, the lap tip oil supply path 84 is extended to the lap tip 13c facing the compression chamber 15 on the higher pressure side. It can be provided. Further, as shown in FIG. 21, by extending and expanding the oil groove 84d along the spiral wrap shape, it is possible to ensure the sealing performance of the wrap tip 13c to a wider range. In addition, when the difference between the suction pressure and the discharge pressure changes during the operation of the compressor, the oil supply amount can be automatically increased using the differential pressure to improve the reliability. .
  • the oil supply amount control path of the present embodiment includes a connection path 65 and a supply path A67.
  • the supply path A ⁇ b> 67 is configured by combining a passage 67 c formed inside the orbiting scroll 13 and a recess 12 b formed on the lap side end plate surface of the fixed scroll 12.
  • One opening end 67b of the passage 67c is formed in the wrap tip 13c, and is periodically opened in the recess 12b in accordance with the turning motion.
  • the other open end 67a of the passage 67c is always opened in the back pressure chamber 29. With this configuration, the back pressure chamber 29 and the second compression chamber 15b can be intermittently communicated.
  • FIG. 22 is a cross-sectional view showing a state in which the turning scroll 13 is engaged with the fixed scroll 12. That is, it is the state seen from the back of the orbiting scroll 13, and is a figure in which the phase is shifted by 90 degrees.
  • intermittent communication is realized by periodically opening the opening end 67 b of the passage 67 c formed in the wrap tip 13 c into the recess 12 b formed in the wrap surface end plate of the fixed scroll 12. Yes.
  • the opening end 67b opens into the recess 12b.
  • the oil 6 is supplied from the back pressure chamber 29 to the second compression chamber 15b through the supply path A67.
  • the opening end 67b does not open to the recess 12b. Therefore, the oil 6 is not supplied from the back pressure chamber 29 to the second compression chamber 15b. From the above, the oil 6 in the back pressure chamber 29 is intermittently guided to the second compression chamber 15b through the supply path A67. Therefore, the pressure fluctuation of the back pressure chamber 29 can be suppressed, and it can be controlled to a predetermined pressure. At the same time, the oil 6 supplied to the second compression chamber 15b can play a role of improving the sealing property and the lubricating property during compression.
  • the back pressure chamber 29 and the second compression chamber 15b can be communicated with each other only in a specific section in the compression stroke where the pressure in the second compression chamber 15b increases.
  • the back pressure can be controlled, but also the pressure from the compression chamber 15 to the back pressure chamber 29 via the supply path A67 in a state where the pressure in the compression chamber 15 is higher than the pressure in the back pressure chamber 29. Backflow can be prevented.
  • the supply path A67 (supply path A66) so that the second compression chamber 15b after the working fluid is confined and the back pressure chamber 29 communicate with each other.
  • the supply path A67 (supply path A66) communicates with the second compression chamber 15b after confining the working fluid.
  • the pressure in the back pressure chamber 29 becomes a predetermined pressure higher than the suction pressure. Therefore, the tilting phenomenon can be prevented and high efficiency can be realized. Further, even if tilting occurs, the pressure in the second compression chamber 15b can be guided to the back pressure chamber 29, so that early return to normal operation is possible.
  • the controlled oil amount is reliably supplied to the 2nd compression chamber 15b. be able to.
  • the oil pressure supplied via the supply path A67 can be controlled by the pressure in the compression chamber 15. That is, since the pressure in the back pressure chamber 29 can be controlled by the pressure in the second compression chamber 15b, it is possible to provide a scroll compressor in which an appropriate back pressure is applied.
  • FIG. 23 is an enlarged cross-sectional view of a main part of the compression mechanism portion of the scroll compressor according to the ninth embodiment of the present invention
  • FIG. 24 is a partially enlarged plan view of the orbiting scroll of the scroll compressor according to the present embodiment.
  • the lap tip oil supply path except for the lap tip oil supply path, it is the same as the seventh embodiment and the eighth embodiment, and therefore the lap tip oil supply path will be described. That is, in the scroll compressor of the present embodiment, the same reference numerals are used for the same components as those of the seventh embodiment, and the description of the configurations and operations is omitted. As shown in FIG.
  • a supply path 85 (passage 85c) of the lap tip oil supply path is provided inside the orbiting scroll 13, and the oil 6 is supplied from the back pressure chamber 29 to the lap tip 13c. Supply.
  • the lap tip oil supply path includes the connection path 65 and the supply path 85, and the oil 6 is supplied to the back pressure chamber 29 from the oil storage section 20 via the high pressure region 30 and the back pressure chamber 29. It is configured to supply to the wrap tip 13c with an intermediate pressure.
  • the opening end 85b of the supply passage 85 and the oil groove 85d are at the center in the thickness direction of the spiral wrap at the wrap tip 13c where the lap tip oil supply passage opens. It is provided with the line removed. Accordingly, for example, if the oil groove 85d is provided near the lap inner wall side, the oil 6 is positively supplied from the wrap tip oil supply path to the second compression chamber 15b.
  • the oil supply amount to each of the first compression chamber 15a and the second compression chamber 15b can be adjusted by changing the dimensions of the seal lengths C1 and C2. That is, in the case of the present embodiment, it is possible to adjust the amount of oil supplied to the first compression chamber 15a and the second compression chamber 15b in the lap tip oil supply path. Therefore, the lap tip oil supply path and the oil supply amount control path can be made common to form a single path.
  • the working fluid is a high-pressure refrigerant, such as carbon dioxide
  • the differential pressure during oil supply increases and the expansion noise tends to be noise.
  • the scroll compressor of the present invention the differential pressure is reduced and the expansion noise can be suppressed. That is, the effect of the present invention is remarkably exhibited, and a scroll compressor that realizes high efficiency and high reliability can be provided.
  • the scroll compressor according to the present invention has a larger pressure change rate in the small compression chamber than in the compression chamber with a large suction volume when the suction volume of the paired compression chambers is different, and the working fluid Therefore, by supplying more oil to the small compression chamber than to the compression chamber with a large suction volume, it is possible to reduce the leakage loss of the compression chamber with a large pressure change rate.
  • a scroll compressor can be realized. Therefore, the working fluid is not limited to the refrigerant, and can be applied to applications of scroll fluid machines such as an air scroll compressor, a vacuum pump, and a scroll type expander.

Abstract

La présente invention concerne un routeur (50) d'alimentation en huile conduisant d'une section contenant de l'huile (20) à une première chambre de compression (15a) et à une seconde chambre de compression (15b), et la quantité d'huile amenée à la seconde chambre de compression (15b) étant supérieure à la quantité d'huile amenée à la première chambre de compression (15a). La configuration minimise les fuites d'une seconde chambre de compression (15b-1) formées à une étape se déroulant juste avant et celles d'une seconde chambre de compression (15b-2) formées à une étape se déroulant juste après, réduisant par conséquent une perte par fuite lors des courses de compression.
PCT/JP2009/004584 2008-12-15 2009-09-15 Compresseur à spirale WO2010070790A1 (fr)

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CN200980150596.0A CN102245903B (zh) 2008-12-15 2009-09-15 涡旋压缩机
JP2010542813A JP5345636B2 (ja) 2008-12-15 2009-09-15 スクロール圧縮機
US13/420,147 US8576142B2 (en) 2009-09-15 2012-03-14 Display device and control method therefor

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JP2008-317952 2008-12-15
JP2008317952 2008-12-15
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JP2009000095 2009-01-05
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WO2013084486A1 (fr) * 2011-12-09 2013-06-13 パナソニック株式会社 Compresseur à volute
WO2013140458A1 (fr) * 2012-03-23 2013-09-26 日立アプライアンス株式会社 Compresseur à volute
JP2016056757A (ja) * 2014-09-11 2016-04-21 日立アプライアンス株式会社 スクロール圧縮機および空気調和機
WO2018096823A1 (fr) * 2016-11-24 2018-05-31 パナソニックＩｐマネジメント株式会社 Compresseur à spirale asymétrique
WO2018096824A1 (fr) * 2016-11-24 2018-05-31 パナソニックＩｐマネジメント株式会社 Compresseur à volute
EP3901462A1 (fr) * 2020-04-20 2021-10-27 LG Electronics Inc. Compresseur

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JP6737308B2 (ja) * 2018-07-05 2020-08-05 ダイキン工業株式会社 スクロール圧縮機
DE102020210452A1 (de) * 2020-05-14 2021-11-18 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Scrollverdichter eines elektrischen Kältemittelantriebs

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WO2013084486A1 (fr) * 2011-12-09 2013-06-13 パナソニック株式会社 Compresseur à volute
WO2013140458A1 (fr) * 2012-03-23 2013-09-26 日立アプライアンス株式会社 Compresseur à volute
JP2016056757A (ja) * 2014-09-11 2016-04-21 日立アプライアンス株式会社 スクロール圧縮機および空気調和機
WO2018096823A1 (fr) * 2016-11-24 2018-05-31 パナソニックＩｐマネジメント株式会社 Compresseur à spirale asymétrique
WO2018096824A1 (fr) * 2016-11-24 2018-05-31 パナソニックＩｐマネジメント株式会社 Compresseur à volute
CN109996962A (zh) * 2016-11-24 2019-07-09 松下知识产权经营株式会社 不对称涡旋式压缩机
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JPWO2018096824A1 (ja) * 2016-11-24 2019-10-17 パナソニックＩｐマネジメント株式会社 スクロール圧縮機
CN109996962B (zh) * 2016-11-24 2021-02-26 松下知识产权经营株式会社 不对称涡旋式压缩机
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EP3901462A1 (fr) * 2020-04-20 2021-10-27 LG Electronics Inc. Compresseur
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JPWO2010070790A1 (ja) 2012-05-24
JP5345636B2 (ja) 2013-11-20
CN102245903B (zh) 2015-02-25

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