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WO2020017020A1 - Compresseur - Google Patents

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Publication number
WO2020017020A1
WO2020017020A1 PCT/JP2018/027273 JP2018027273W WO2020017020A1 WO 2020017020 A1 WO2020017020 A1 WO 2020017020A1 JP 2018027273 W JP2018027273 W JP 2018027273W WO 2020017020 A1 WO2020017020 A1 WO 2020017020A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
pump
flow path
oil return
oil supply
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/027273
Other languages
English (en)
Japanese (ja)
Inventor
鉄郎 平見
雷人 河村
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to CN201880094061.5A priority Critical patent/CN112424475B/zh
Priority to PCT/JP2018/027273 priority patent/WO2020017020A1/fr
Priority to JP2020530838A priority patent/JP6914445B2/ja
Publication of WO2020017020A1 publication Critical patent/WO2020017020A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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

Definitions

  • the present invention relates to a compressor for compressing a refrigerant, and more particularly to a refueling structure.
  • a compressor that pumps up oil stored in an oil reservoir at the bottom of a container by a pump element and supplies the oil to the compression mechanism through an oil supply passage formed in a rotating shaft.
  • a pump element is connected to a rotating shaft and is driven by rotation of the rotating shaft.
  • the present invention has been made to solve the above problems, and has as its object to provide a compressor capable of preventing excessive lubrication and reducing the amount of oil taken out.
  • a compressor accommodates a compression mechanism for compressing a refrigerant, a rotation shaft having an oil supply passage for supplying oil to a sliding portion including the compression mechanism, a compression mechanism and the rotation shaft, and a bottom portion.
  • a reservoir in which an oil reservoir is formed an oil pump driven by the rotation of the rotary shaft to supply oil accumulated in the oil reservoir to an oil supply passage of the rotary shaft, and an oil supply pump for supplying oil to the oil supply channel of the rotary shaft.
  • the oil supply relief valve that opens when the oil pressure in the oil supply relief passage becomes equal to or higher than the set pressure since the oil supply relief valve that opens when the oil pressure in the oil supply relief passage becomes equal to or higher than the set pressure is provided, it is possible to prevent excessive oil supply and reduce the amount of oil taken out. Is possible.
  • FIG. 1 is a schematic vertical sectional view of the overall configuration of a compressor according to Embodiment 1 of the present invention.
  • FIG. 2 is an enlarged schematic cross-sectional view of the periphery of a lower portion of a rotary shaft of the compressor according to Embodiment 1 of the present invention.
  • FIG. 2 is an enlarged schematic cross-sectional view of a portion around an upper portion of a rotary shaft of the compressor according to Embodiment 1 of the present invention.
  • FIG. 2 is a diagram illustrating in detail a flow of oil around a lower portion of a rotary shaft of the compressor according to Embodiment 1 of the present invention.
  • FIG. 3 is an explanatory diagram of the oil supply pump as viewed from the direction of the section AA in FIG. It is a figure which shows the comparison result of the oil carry-out amount in each structure of the compressor which concerns on Embodiment 1 of this invention.
  • FIG. 1 is a schematic vertical sectional view of the overall configuration of the compressor according to Embodiment 1 of the present invention.
  • a thick solid line arrow indicates a flow of refueling.
  • the thick dotted arrow indicates the flow of oil return.
  • the compressor has a compression mechanism 3, a rotating shaft 6, an electric mechanism 110, and other components.
  • the compressor has a configuration in which these components are housed inside a container 100 forming an outer shell. In the container 100, the compression mechanism 3 is arranged at the upper part, and the electric mechanism 110 is arranged at the lower part.
  • the compression mechanism 3 and the electric mechanism 110 are connected via the rotating shaft 6, and the rotational force generated by the electric mechanism 110 is transmitted to the compression mechanism 3 via the rotating shaft 6, and the compression mechanism 3
  • the refrigerant is compressed.
  • the compressor of the first embodiment is a so-called low-pressure shell-type compressor in which the inside of the container 100 is filled with the refrigerant before being compressed by the compression mechanism 3.
  • the compression mechanism 3 is supported by the frame 7.
  • the frame 7 is fixed to the inner peripheral surface of the container 100 by shrink fitting or welding.
  • the frame 7 is arranged between the compression mechanism 3 and the electric mechanism 110 in the container 100.
  • a shaft hole 7a is formed in the center of the frame 7, and the rotating shaft 6 is passed through the shaft hole 7a.
  • a sub-frame 8 is provided below the electric mechanism 110 in the container 100.
  • the subframe 8 is fixed to the inner peripheral surface of the container 100 by shrink fitting or welding.
  • An oil reservoir 100a is formed at the bottom of the container 100.
  • oil for lubricating sliding parts including the compression mechanism 3 and the bearing is stored.
  • the oil in the oil reservoir 100a is pumped up by a pump element 120 provided at the lower end of the rotating shaft 6, and is supplied to a sliding portion.
  • the refueling structure including the pump element 120 is a feature of the first embodiment, and will be described below again.
  • the container 100 is provided with a suction pipe 101 for sucking the refrigerant and a discharge pipe 102 for discharging the refrigerant.
  • a low-pressure suction space 70 filled with the suction refrigerant flowing from the suction pipe 101 is formed below the frame 7 in the container 100.
  • a high-pressure discharge space 71 filled with the refrigerant discharged from the compression mechanism 3 is formed on the discharge pipe 102 side of the below-described fixed base plate 1a of the compression mechanism 3 in the container 100.
  • the compression mechanism 3 includes the fixed scroll 1 and the orbiting scroll 2 disposed below the fixed scroll 1.
  • the fixed scroll 1 is fixed to the frame 7.
  • the orbiting scroll 2 is disposed in a space between the fixed scroll 1 and the frame 7.
  • An Oldham ring 13 for preventing rotation of the orbiting scroll 2 is disposed between the orbiting scroll 2 and the frame 7.
  • the fixed scroll 1 has a fixed base plate 1a and a fixed scroll 1b provided upright on one surface of the fixed base plate 1a.
  • the orbiting scroll 2 has an orbiting base plate 2a and an orbiting scroll 2b provided upright on one surface of the orbiting base plate 2a.
  • the fixed scroll 1 and the orbiting scroll 2 are arranged in the container 100 in a symmetrical spiral shape in which the fixed scroll 1b and the rocking scroll 2b are meshed with the rotation center of the rotation shaft 6 in the opposite phase. I have.
  • a compression chamber 9 is formed between the fixed spiral body 1b and the swinging spiral body 2b. The compression chamber 9 decreases in volume from the outside to the inside in the radial direction as the rotating shaft 6 rotates.
  • a discharge port 10 communicating with the compression chamber 9 is formed through the fixed base plate 1 a of the fixed scroll 1.
  • a discharge valve 11 for opening and closing the discharge port 10 and a valve holder 12 for regulating the movable range of the discharge valve 11 are attached.
  • a cylindrical boss 2d is formed substantially at the center of a surface (hereinafter referred to as a back surface) of the swing base plate 2a of the swing scroll 2 opposite to the surface on which the swing scroll 2b is formed.
  • a swing bearing 5 is fixed inside the boss 2d.
  • the oscillating bearing 5 is made of a bearing material used for a sliding bearing such as a copper-lead alloy, and the bearing material is pressed into the boss portion 2d and fixed.
  • the balancer-equipped slider 4 is rotatably arranged inside the swing bearing 5.
  • the slider 4 with a balancer has a configuration in which a cylindrical slider portion 4a and a balancer portion 4b are joined by shrink fitting or the like.
  • the slider portion 4a is relatively movably fitted to an eccentric shaft portion 6a, which will be described later, provided at the upper end of the rotary shaft 6, and automatically adjusts the swing radius of the swing scroll 2.
  • the slider portion 4a is provided so that the fixed scroll 1b and the rocking scroll 2b are always in contact with each other when the rocking scroll 2 rocks.
  • the balancer section 4b is located on the side of the slider section 4a, and is provided to cancel the centrifugal force of the orbiting scroll 2 and suppress the vibration of the compression element.
  • the orbiting scroll 2 is connected to the eccentric shaft portion 6a of the rotating shaft 6 via the slider 4 with a balancer, and the swinging radius of the rotating shaft 6 is automatically adjusted by the slider 4 with the balancer. Swings with the movement.
  • a cylindrical bearing operation space 72 is formed between the back surface of the swing base plate 2a of the swing scroll 2 and the frame 7, and the swing bearing 5 has a balancer during the swing movement of the swing scroll 2.
  • the bearing 4 rotates in the bearing operation space 72 together with the slider 4.
  • the main shaft portion 6b below the eccentric shaft portion 6a on the rotating shaft 6 is fitted into the main bearing 15 via the sleeve 14, and slides on the main bearing 15 via an oil film made of oil.
  • the main bearing 15 is fixed to the frame 7 by press-fitting a bearing material used for a sliding bearing such as a copper-lead alloy.
  • An eccentric shaft portion 6a eccentric to the main shaft portion 6b is provided at an upper end portion of the rotating shaft 6.
  • a central portion of the sub-frame 8 is provided with a sub-bearing 16 formed of a ball bearing, and supports the rotating shaft 6 in a radial direction below the electric mechanism 110.
  • the auxiliary bearing 16 may have another bearing configuration other than the ball bearing.
  • the sub shaft portion 6c below the electric mechanism 110 on the rotating shaft 6 is fitted with the sub bearing 16, and slides on the sub bearing 16 via an oil film made of oil.
  • the axes of the main shaft portion 6b and the sub shaft portion 6c coincide with the axis of the rotating shaft 6.
  • the electric mechanism 110 has an electric motor stator 110a and an electric motor rotor 110b.
  • the motor stator 110a is connected to a glass terminal (not shown) existing between the frame 7 and the motor stator 110a by a lead wire (not shown) in order to obtain electric power from the outside.
  • the motor rotor 110b is fixed to the rotating shaft 6 by shrink fitting or the like.
  • FIG. 2 is an enlarged schematic cross-sectional view around the lower part of the rotating shaft of the compressor according to Embodiment 1 of the present invention.
  • FIG. 3 is an enlarged schematic cross-sectional view around the upper part of the rotation shaft of the compressor according to Embodiment 1 of the present invention.
  • FIG. 4 is a diagram showing in detail the flow of oil around the lower portion of the rotary shaft of the compressor according to Embodiment 1 of the present invention. 2 to 4, the thick solid arrow indicates the flow of refueling.
  • the bold dotted arrow indicates the flow of the oil return main flow path.
  • the thin dotted arrow indicates the flow of the sub-flow path for oil return.
  • the rotary shaft 6 is provided with an oil supply passage 61 for supplying oil to a sliding portion including the compression mechanism 3.
  • the refueling flow channel 61 includes a vertical hole 61a penetrating the center of the rotating shaft 6 in the axial direction, and a plurality of lateral holes 61b communicating with the vertical hole 61a and extending in the radial direction.
  • the lateral hole 61b is formed at a position facing each of the swing bearing 5, the main bearing 15, and the sub-bearing 16.
  • an oil return passage 62 is formed on the rotating shaft 6 separately from the oil supply passage 61.
  • the oil return channel 62 is a channel for returning the oil supplied from the oil supply channel 61 to the sliding portion to the oil reservoir 100a.
  • the oil return passage 62 is formed of a vertical hole whose upper end is opened in the bearing operation space 72 and whose lower end is opened in the lower end surface of the rotating shaft 6, and which is smaller than the axis of the main shaft portion 6 b of the rotating shaft 6. It is formed on the outside.
  • the oil flowing out of the oil supply passage 61 and flowing into the bearing operation space 72 is drawn in from the upper end side of the oil return passage 62 by the oil return pump 122 ⁇ / b> A of the pump element 120 described later, and the lower end of the oil return passage 62. After flowing to the oil reservoir 100a.
  • the pump element 120 is provided on the rotating shaft 6 and attached to the sub-frame 8.
  • the pump element 120 is driven by the rotation of the rotary shaft 6, and includes an oil supply pump 121A, an oil return pump 122A, and a pump cover 124 as shown in FIGS.
  • the oil supply pump 121A and the oil return pump 122A are provided at the lower end of the rotating shaft 6 vertically adjacent to each other via a partition plate 130.
  • the upper ends of the oil supply pipe 17 and the oil return pipe 18 are connected to the oil supply pump 121A and the oil return pump 122A.
  • the lower ends of the oil supply pipe 17 and the oil return pipe 18 are located in the oil reservoir 100a and are immersed in oil.
  • the oil supply pump 121 ⁇ / b> A supplies oil stored in the oil storage part 100 a to the oil supply passage 61 of the rotating shaft 6 via the oil supply pipe 17.
  • the oil return pump 122A draws oil in the bearing operation space 72 into the oil return flow path 62 of the rotating shaft 6.
  • the oil return pump 122A has a volume one to three times as large as that of the oil supply pump 121A. Since the slider 4 with the balancer rotates in the bearing operation space 72, it is difficult to draw oil into the oil return passage 62. Therefore, a pump having a larger capacity than the oil supply pump 121A is used for the oil return pump 122A.
  • the refueling pump 121A includes a refueling-side movable part 121 and a refueling pump body that houses the refueling-side movable part 121.
  • the oil return pump 122A includes an oil return side movable section 122 and an oil return pump body that houses the oil return side movable section 122.
  • the pump body 123 has a configuration in which the oil supply pump body that houses the oil supply-side movable section 121 and the oil return pump body that houses the oil return-side movable section 122 are shared. Pump body 123 is fixed to subframe 8. In addition, the pump body 123 is not limited to such a common configuration, and may be configured separately on the oil supply side and the oil return side.
  • An upper thrust plate 131 and a lower thrust plate 132 are arranged above the oil supply side movable portion 121 and below the oil return side movable portion 122.
  • the oil supply pump 121A and the oil return pump 122A are configured by trochoid pumps, which are a type of positive displacement pump, as shown in FIG.
  • the configurations of the oil supply pump 121A and the oil return pump 122A are the same, and the configuration of the oil supply pump 121A will be described below on behalf of the oil supply pump 121A.
  • FIG. 5 is an explanatory diagram of the oil supply pump viewed from the direction of the section AA in FIG.
  • the arrow in FIG. 5 indicates the direction of rotation of the rotating shaft 6.
  • the refueling pump 121A has an outer rotor 20 rotatably housed inside a pump body 123, and an inner rotor 21 housed inside the outer rotor 20.
  • a fluid chamber 23 is defined between the outer rotor 20 and the inner rotor 21.
  • the center axis of the inner rotor 21 is eccentric with respect to the center axis of the outer rotor 20.
  • the inner rotor 21 is attached to the rotating shaft 6 and is driven to rotate by the rotating shaft 6.
  • the outer rotor 20 has an oil supply port 24 for supplying oil into the fluid chamber 23 and an oil discharge port 25 for discharging oil from inside the fluid chamber 23.
  • the refueling port 24 communicates with the upper end of the refueling pipe 17 via a first passage hole 132a formed in the lower thrust plate 132.
  • the oil discharge port 25 communicates with an oil flow path 124 a described later formed on the upper surface of the pump cover 124 via a second flow path hole 132 b formed in the lower thrust plate 132.
  • the oil in the fluid chamber 23 is discharged from the oil discharge port 25 and flows into the oil flow path 124a through the second flow path hole 132b. Then, the oil that has flowed into the oil passage 124 a is supplied to the vertical hole 61 a of the oil supply passage 61.
  • the oil return pump 122A has the same configuration as the oil supply pump 121A as described above, and includes an outer rotor 20 rotatably housed inside a pump body 123, and an inner rotor 21 housed inside the outer rotor 20. Having.
  • the oil supply port 24 of the oil return pump 122 ⁇ / b> A communicates with the oil return flow path 62 of the rotating shaft 6 through a flow path hole 131 a formed in the upper thrust plate 131.
  • the oil discharge port 25 of the oil return pump 122A communicates with the upper end side of the oil return pipe 18 via a flow passage hole 130a formed in the partition plate 130.
  • an oil passage 124a is formed at a position facing the vertical hole 61a of the rotating shaft 6.
  • the oil flow path 124a is specifically formed of a concave portion, and serves as a flow path until oil flowing out from the oil discharge port 25 of the oil supply pump 121A flows into the oil supply path 61 of the rotating shaft 6.
  • the pump cover 124 is provided with an oil supply relief channel 124b that relieves part of the oil supplied from the oil supply pump 121A to the oil supply channel 61 of the rotating shaft 6.
  • the oil supply relief channel 124b is specifically formed of a through-hole penetrating in the axial direction from the bottom surface of the oil channel 124a, and the upper end of the through-hole opens in the oil channel 124a and the lower end of the pump cover 124 It is open on the lower surface.
  • An oil supply relief valve 125 that opens and closes the oil supply relief channel 124b is disposed at the outlet of the oil supply relief channel 124b.
  • the refueling relief valve 125 is constituted by a leaf spring-shaped reed valve.
  • the refueling relief valve 125 is designed to open when the oil pressure in the refueling relief passage 124b becomes equal to or higher than a set pressure. This set pressure may be arbitrarily designed.
  • the first embodiment is characterized by a structure that prevents excessive lubrication during high-speed operation in which the rotating shaft 6 rotates at high speed.
  • the first lubrication relief passage 124b and the lubrication relief valve 125 Excessive refueling is prevented.
  • the pumping amount of oil by the oil supply pump 121A increases, and the pressure in the oil supply relief channel 124b increases. Therefore, the oil pressure in the oil supply relief passage 124b becomes equal to or higher than the set pressure, and the oil supply relief valve 125 is opened.
  • the oil supply relief valve 125 is opened, part of the oil supplied from the oil supply pump 121A to the oil supply passage 61 is relieved, and returns to the oil reservoir 100a. As a result, excessive refueling can be prevented, and the amount of oil taken out can be reduced as compared with the related art.
  • the oil in the bearing operation space 72 is transferred to the oil return passage 62 of the rotary shaft 6 using the oil return pump 122A. It draws in and is configured to forcibly return oil to the oil reservoir 100a.
  • the oil return pump 122A is driven by the rotation of the rotating shaft 6, and returns oil in accordance with the number of rotations. Therefore, by performing oil return using the oil return pump 122A, the amount of oil taken out can be reduced as a result, and oil depletion can be prevented.
  • the first embodiment by providing the oil return passage 62 and the oil return pump 122A, it is possible to reduce the amount of oil taken out while appropriately discharging the oil in the bearing operation space 72.
  • the oil discharge may not catch up. Therefore, the first embodiment further includes a structure in which the amount of oil returned during high-speed operation is increased as compared with low-speed operation.
  • a flow path of the oil return there is a main flow path 80 for returning oil to the oil reservoir 100a through the oil return flow path 62 and the oil return pipe 18 as shown by a thick dotted arrow in FIG.
  • a sub flow path 126 that returns oil in a flow indicated by a thin dotted arrow in FIG.
  • the sub flow path 126 is specifically formed of a through hole formed in the pump body 123, and the upper end of the through hole is opened in a flow path hole 130a formed in the partition plate 130, and the lower end is formed in the pump body 123. It is open on the lower surface of. That is, the sub flow path 126 is provided to be branched from the main flow path 80.
  • an oil return valve 127 for opening and closing the sub flow path 126 is disposed.
  • the oil return valve 127 is constituted by a leaf spring-shaped reed valve.
  • the oil return valve 127 is designed to open when the oil pressure in the sub flow path 126 becomes equal to or higher than a set pressure. This set pressure may be arbitrarily designed. Although only one set of the sub flow path 126 and the oil return valve 127 is shown in FIG. 2 and the like, the configuration is not limited to one set, and a plurality of sets may be provided.
  • the refrigerant is sucked into the suction space 70 in the container 100 from the external refrigeration cycle via the suction pipe 101, and is further taken into the compression chamber 9.
  • the refrigerant taken into the compression chamber 9 gradually moves toward the center of the orbiting scroll 2 by the orbiting motion of the orbiting scroll 2, and is compressed by reducing the volume.
  • the compressed refrigerant gas is discharged from the discharge port 10 provided in the fixed scroll 1 to the discharge space 71 against the discharge valve 11.
  • the high-pressure refrigerant discharged into the discharge space 71 is discharged from the discharge pipe 102 to the outside of the container 100.
  • the oil pressure in the oil supply relief passage 124b increases with the oil pressure in the oil passage 124a increasing, and the oil supply relief valve 125 is opened.
  • the oil supply relief valve 125 is opened, a part of the oil supplied from the oil supply pump 121 ⁇ / b> A to the oil supply passage 61 is relieved from the oil supply passage 61.
  • excessive oil supply during high-speed operation can be prevented, and the amount of oil taken out can be reduced as compared with the conventional case.
  • the oil pressure in the sub flow path 126 increases, and the oil return valve 127 opens. Thereby, a part of the oil in the main flow passage 80 is relieved from the sub flow passage 126. The oil relieved from the sub flow path 126 falls and is returned to the oil reservoir 100a. In this way, the amount of oil returned during high-speed operation can be increased by returning the oil from the sub flow path 126 in addition to the main flow path 80.
  • the oil return valve 127 is opened by a pressure difference between the pressure in the sub flow path 126 and the upper space of the oil reservoir 100 a, and this pressure difference changes according to the rotation speed of the rotating shaft 6. That is, it is possible to adjust the oil return amount according to the rotation speed.
  • FIG. 6 is a diagram illustrating a comparison result of the amount of oil taken out in each configuration of the compressor according to Embodiment 1 of the present invention.
  • the horizontal axis represents the compressor rotation speed [rpm]
  • the vertical axis represents the amount of oil taken out.
  • (1) has a configuration provided with an oil supply relief channel 124b and an oil supply relief valve 125
  • (2) has a configuration provided with an oil return channel 62 and an oil return pump 122A in addition to the above (1)
  • (3) shows a case of a configuration having both the above (1) and the above (2).
  • FIG. 6, (4) is a diagram showing the amount of oil taken out in the conventional configuration not having any of the above (1) to (3). As shown in FIG.
  • the amount of oil taken out can be reduced as compared with the conventional case. Further, as is clear from FIG. 6, the amount of oil taken out does not continue to increase with the increase in the number of rotations of the compressor, but peaks at a certain number of rotations of the compressor, which differs for each of (1) to (3). Become.
  • the oil supply relief channel 124b and the oil supply relief valve 125 that opens when the oil pressure in the oil supply relief channel 124b becomes equal to or higher than the set pressure are provided.
  • the refueling relief valve 125 is opened at the time of high-speed operation, and a part of the oil flowing from the refueling pump 121A to the refueling channel 61 of the rotating shaft 6 can be relieved from the refueling channel 61. Therefore, the compressor of the first embodiment can prevent excessive refueling during high-speed operation, and can reduce the amount of oil taken out.
  • An oil return passage 62 is provided on the rotating shaft 6 separately from the oil supply passage 61, and the oil in the bearing operation space 72 is stored in the oil reservoir via the oil return passage 62 by using an oil return pump 122 ⁇ / b> A. The oil was forcibly returned to the part 100a. For this reason, mechanical loss when the swing bearing 5 and the slider with balancer 4 rotate in the bearing operation space 72 can be reduced.
  • the sub flow path 126 is provided separately from the main flow path 80 for returning the oil in the bearing operation space 72 to the oil reservoir 100 a via the oil return pipe 18.
  • An oil return valve 127 that opens when the oil pressure in the inside becomes equal to or higher than a set pressure is provided.
  • the oil return valve 127 is opened during high-speed operation, and oil can be returned not only from the main flow path 80 but also from the sub flow path 126. That is, since the number of oil return paths can be increased during high-speed operation, the amount of oil returned can be increased, and oil depletion can be prevented.
  • the oil supply pump 121A and the oil return pump 122A can be provided at the lower end of the rotating shaft 6 adjacent to each other.
  • the oil return structure includes the oil return passage 62 provided in the rotary shaft 6 and the oil return pump 122A.
  • the following structure is also conceivable.
  • an oil return hole communicating the bearing operation space 72 and the space outside the frame is formed through the frame 7, and an oil return pipe extends from the outlet of the oil return hole to the suction space 70 above the electric mechanism 110.
  • a configuration in which oil is relieved from the outlet of the oil return pipe to the suction space 70 is conceivable. In the case of this configuration, the following problem occurs during high-speed operation.
  • the oil discharged from the oil return pipe into the suction space 70 is agitated by the refrigerant flowing from the suction pipe 101 into the suction space 70 to form a mist.
  • the oil becomes mist-like it is taken up by the refrigerant flowing from the suction pipe 101, flows into the compression chamber 9 together with the refrigerant, and is consequently taken out of the compressor together with the compressed refrigerant. That is, the amount of oil taken out increases.
  • the oil return pipe 18 has an upper end communicating with the oil return pump 122A and a lower end located in the oil sump 100a. It returns directly to the part 100a. Thereby, mist of the oil to be returned can be prevented beforehand, and reliable oil return can be performed.
  • the amount of oil returned can be increased as compared with the case where one set is used.
  • the oil in the bearing operation space 72 can be sufficiently drawn into the oil return passage 62, A stable oil return can be performed.
  • a colloid pump which is a kind of positive displacement pump, can be used as the oil supply pump 121A and the oil return pump 122A.
  • the slider 4 with the balancer is provided. Therefore, the spiral of the fixed scroll 1 and the spiral of the orbiting scroll 2 can always be in contact with each other when the orbiting scroll 2 swings, and the centrifugal force of the orbiting scroll 2 is canceled to vibrate the compression element. Can be suppressed.
  • a through-hole for discharging oil in the bearing operation space 72 to the outside of the frame 7 is not formed in the frame 7 other than the shaft hole 7a through which the rotating shaft 6 passes. That is, most of the oil in the bearing operation space 72 returns to the oil reservoir 100a through the oil return passage 62 of the rotary shaft 6 and the oil return pipe 18. Therefore, the oil in the bearing operation space 72 does not flow into the suction space 70 between the frame 7 and the electric mechanism 110, and therefore, the oil is mist-formed by the refrigerant sucked from the suction pipe 101, so that the oil is mist outside the compressor. Can be prevented from being taken out.
  • the compression mechanism 3 is a scroll-type compression mechanism.
  • the present invention can be applied to a rotary-type compression mechanism.
  • the present invention is also applicable to a high-pressure shell-type compressor in which the inside of the container is filled with the refrigerant after being compressed by the compression mechanism 3. It is.
  • Reference Signs List 1 fixed scroll, 1a fixed base plate, 1b fixed scroll, 2 swing rocker, 2a swing base, 2b swing scroll, 2d boss, 3 compression mechanism, 4 slider with balancer, 4a slider, 4b balancer Part, 5 swing bearing, 6 rotary shaft, 6a eccentric shaft, 6b main shaft, 6c ⁇ sub shaft, 7 frame, 7a shaft hole, 8 subframe, 9 compression chamber, 10 discharge port, 11 discharge valve, 12 valve Holder, 13 Oldham ring, 14 Sleeve, 15 Main bearing, 16 Secondary bearing, 17 Oil supply pipe, 18 Oil return pipe, 20 Outer rotor, 21 Inner rotor, 23 Fluid chamber, 24 Oil filler, 25 Oil drain, 61 Oil flow Road, 61a vertical hole, 61b horizontal hole, 62 oil return passage, 70 suction space, 71 discharge space, 72 operation of bearing Between, 80 main flow path, 100 container, 100a oil reservoir, 101 suction pipe, 102 discharge pipe, 110 electric mechanism, 110a motor stator, 110b motor rotor, 120 pump element, 121 oil supply side

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un compresseur, qui comporte : un mécanisme de compression (3) pour comprimer un agent réfrigérant ; un arbre rotatif (6) qui a, formée à l'intérieur de celui-ci, une trajectoire de délivrance d'huile (61) pour délivrer de l'huile à une partie de coulissement comprenant le mécanisme de compression ; et un récipient qui renferme le mécanisme de compression et l'arbre rotatif et qui a un réservoir d'huile (100a) formé à la partie inférieure. En outre, le compresseur comporte : une pompe de délivrance d'huile (121A) qui est entraînée par la rotation de l'arbre rotatif de façon à délivrer de l'huile stockée dans le réservoir d'huile par l'intermédiaire de la trajectoire de délivrance d'huile de l'arbre rotatif ; et une vanne de décharge de délivrance d'huile (125) qui ouvre/ferme une trajectoire de décharge de délivrance d'huile (124b) par l'intermédiaire de laquelle l'huile délivrée à partir de la pompe de délivrance d'huile par l'intermédiaire de la trajectoire de délivrance d'huile de l'arbre rotatif est partiellement relâchée, et qui s'ouvre quand la pression d'huile dans la trajectoire de décharge de délivrance d'huile atteint une pression établie, ou plus élevée que celle-ci.
PCT/JP2018/027273 2018-07-20 2018-07-20 Compresseur Ceased WO2020017020A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201880094061.5A CN112424475B (zh) 2018-07-20 2018-07-20 压缩机
PCT/JP2018/027273 WO2020017020A1 (fr) 2018-07-20 2018-07-20 Compresseur
JP2020530838A JP6914445B2 (ja) 2018-07-20 2018-07-20 圧縮機

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/027273 WO2020017020A1 (fr) 2018-07-20 2018-07-20 Compresseur

Publications (1)

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WO2020017020A1 true WO2020017020A1 (fr) 2020-01-23

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JP (1) JP6914445B2 (fr)
CN (1) CN112424475B (fr)
WO (1) WO2020017020A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0942181A (ja) * 1995-08-04 1997-02-10 Mitsubishi Heavy Ind Ltd スクロール型圧縮機
JPH1182350A (ja) * 1997-09-05 1999-03-26 Sanyo Electric Co Ltd 圧縮機のオイルポンプ
JPH11141472A (ja) * 1997-11-11 1999-05-25 Daikin Ind Ltd スクロール型流体機械
US20090035168A1 (en) * 2005-05-23 2009-02-05 Danfoss Commercial Compressors Scroll-type refrigerant compressor
US20100122550A1 (en) * 2008-11-14 2010-05-20 Nam-Kyu Cho Hermetic compressor and refrigeration cycle device having the same
JP2017106423A (ja) * 2015-12-11 2017-06-15 ダイキン工業株式会社 圧縮機
WO2017158809A1 (fr) * 2016-03-18 2017-09-21 三菱電機株式会社 Compresseur

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017210898A (ja) * 2016-05-24 2017-11-30 ダイキン工業株式会社 スクロール圧縮機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0942181A (ja) * 1995-08-04 1997-02-10 Mitsubishi Heavy Ind Ltd スクロール型圧縮機
JPH1182350A (ja) * 1997-09-05 1999-03-26 Sanyo Electric Co Ltd 圧縮機のオイルポンプ
JPH11141472A (ja) * 1997-11-11 1999-05-25 Daikin Ind Ltd スクロール型流体機械
US20090035168A1 (en) * 2005-05-23 2009-02-05 Danfoss Commercial Compressors Scroll-type refrigerant compressor
US20100122550A1 (en) * 2008-11-14 2010-05-20 Nam-Kyu Cho Hermetic compressor and refrigeration cycle device having the same
JP2017106423A (ja) * 2015-12-11 2017-06-15 ダイキン工業株式会社 圧縮機
WO2017158809A1 (fr) * 2016-03-18 2017-09-21 三菱電機株式会社 Compresseur

Also Published As

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JP6914445B2 (ja) 2021-08-04
JPWO2020017020A1 (ja) 2021-05-13
CN112424475B (zh) 2022-09-02
CN112424475A (zh) 2021-02-26

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