WO2015104863A1 - 回転式圧縮機 - Google Patents

回転式圧縮機 Download PDF

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Publication number
WO2015104863A1
WO2015104863A1 PCT/JP2014/071307 JP2014071307W WO2015104863A1 WO 2015104863 A1 WO2015104863 A1 WO 2015104863A1 JP 2014071307 W JP2014071307 W JP 2014071307W WO 2015104863 A1 WO2015104863 A1 WO 2015104863A1
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WO
WIPO (PCT)
Prior art keywords
reed valve
main shaft
oil
seating surface
rotary compressor
Prior art date
Application number
PCT/JP2014/071307
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
下地　美保子
関屋　慎
英彰 永田
雷人 河村
昌晃 須川
石園　文彦
角田　昌之
祐司 高村
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2015556704A priority Critical patent/JP6300829B2/ja
Priority to CN201480072634.6A priority patent/CN105899808B/zh
Publication of WO2015104863A1 publication Critical patent/WO2015104863A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • 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 rotary compressor used in a refrigeration cycle for refrigeration or for air conditioning, and more particularly to an oil supply structure.
  • This scroll-type rotary compressor includes a compression mechanism part in which a compression chamber is formed by combining a fixed scroll and an orbiting scroll in an airtight container, a main shaft connected to the orbiting scroll, and a compression mechanism part.
  • An electric motor that is driven at a variable speed via a shaft, a bearing that supports the main shaft, and an oil pump provided at the lower end of the main shaft are housed, and the oil stored at the bottom of the sealed container is stored in the main shaft inside the bearing and compressed
  • An oil supply passage for supplying to the sliding portion of the mechanism portion and a bypass passage communicating with the oil supply passage and the outside of the main shaft in the middle of the oil supply passage are formed and operated by the centrifugal force generated by the rotation of the main shaft.
  • an oil supply bypass mechanism that opens and closes (see, for example, Patent Documents 1 and 2).
  • Patent Document 1 as the oil supply bypass mechanism, a ball valve that closes the bypass path and an elastic belt that presses the ball valve toward the axial center are formed, and the bypass path has a funnel shape with a cross-sectional area that increases toward the outside.
  • Patent Document 2 as a fuel supply bypass mechanism, a piston that closes the bypass path, a spring that presses the piston toward the axial center, a plate that prevents the piston and the spring from jumping out of the main shaft, and a C-ring that stops the plate
  • the bypass path is formed obliquely downward toward the outside.
  • JP 2000-213480 A see, for example, [0012], [0013], [0018], FIG. 2
  • JP 2001-271769 A see, for example, [0013], [0014], FIG. 1
  • the present invention has been made to solve the above-described problems, and an object of the present invention is to obtain a rotary compressor capable of reducing the cost by a simple oil supply bypass mechanism having a small number of parts.
  • a rotary compressor according to the present invention includes a sealed container in which oil is stored in a bottom portion, a fixed scroll having a swirl portion, a swirl portion, and a compression chamber that compresses a refrigerant in combination with the swirl portion of the fixed scroll.
  • a rocking scroll forming an oil pump, an oil pump for pumping up the oil stored in the bottom of the closed container, an oil supply passage through which the oil pumped up by the oil pump passes, a branch from the oil supply passage, and an outlet to the outside
  • a bypass passage for discharging oil a main shaft formed inside, an electric motor section that drives the swing scroll through the main shaft, and a reed valve that opens and closes an outlet of the bypass passage formed of a flexible material
  • At least one of the fastening surface and the seating surface has an inclined shape for deflecting the reed valve, and a preload due to deflection of the reed valve acts on the seating surface, and the outlet of the bypass passage Is to be closed.
  • the fastening surface and the seating surface has an inclined shape, and the preload due to the deflection of the reed valve acts on the seating surface. Therefore, the oil supply bypass mechanism can be configured, and the number of parts is small and the cost can be reduced.
  • FIG. 9 is an arrow view of the AA cross section of FIG. 8. It is a longitudinal cross-sectional view of the rotary compressor which concerns on Embodiment 5 of this invention. It is an arrow view of the BB cross section of FIG.
  • FIG. 1 is a longitudinal sectional view of a rotary compressor 100 according to Embodiment 1 of the present invention.
  • the rotary compressor 100 sucks the refrigerant circulating in the refrigeration cycle, compresses it, and discharges it as a high-temperature and high-pressure state.
  • the rotary compressor 100 includes a compression mechanism unit 28 and an electric motor unit 29 in the hermetic container 20.
  • the compression mechanism unit 28 is on the upper side
  • the electric motor unit 29 is on the lower side.
  • Each is arranged.
  • the airtight container 20 is sealed in a cylindrical airtight container 17, a lower airtight container 18 that is sealed to the lower surface opening of the airtight container 17 by welding or the like, and a top surface opening of the airtight container 17 that is sealed by welding or the like. It is a pressure-resistant container comprised from the airtight container top 19 made.
  • the airtight container 17 is connected to a refrigerant suction pipe 21 that forms a part of the refrigerant circuit and takes the refrigerant into the airtight container 20.
  • the frame 3 is fixed to the inner periphery of the upper end portion, and the electric motor is connected to the inner periphery of the intermediate portion.
  • the stator 7 is fixed.
  • the bottom portion of the lower sealed container 18 constitutes an oil sump 16 that stores oil (hereinafter also simply referred to as oil) that lubricates each bearing.
  • An oil drain pipe 27 is connected to the bottom surface of the frame 3 to return the oil staying in the frame 3 to the oil sump 16.
  • a refrigerant discharge pipe 22 for discharging the compressed refrigerant from the closed container 20 to the refrigerant circuit is connected to the upper closed container 19.
  • the compression mechanism portion 28 has a fixed scroll 1 having a spiral portion on one surface (lower side in FIG. 1), and a spiral portion having a winding direction opposite to that of the fixed scroll 1 on one surface (upper side in FIG. 1).
  • the fixed scroll 1 is fixed to the swing scroll 2, the swing bearing 2a provided on the anti-compression chamber side (the lower side in FIG. 1) of the swing scroll 2 and swingably supported by the eccentric slider shaft portion 8a.
  • the motor 3 is arranged to include at least the frame 3 that is arranged and has the main bearing 3a in the center, and the main shaft 8 that transmits the driving force to the orbiting scroll 2 by the motor rotor 6 fixed to the outer periphery.
  • the eccentric slider shaft portion 8 a is a slider mounting shaft installed on the upper portion of the main shaft 8 so that the slider 9 is eccentric with respect to the main shaft 8.
  • a seal 25 is provided on the end surface of the spiral portion of the fixed scroll 1 and the spiral portion of the orbiting scroll 2.
  • a seal 26 is provided on each of the front end surfaces.
  • a discharge port 34 for discharging the compressed and high-pressure refrigerant gas is formed in the central part of the fixed scroll 1.
  • the compressed refrigerant gas having a high pressure is discharged to a high-pressure portion (not shown) in the closed container 19.
  • the refrigerant gas discharged to the high pressure portion is discharged to the refrigeration cycle via the refrigerant discharge pipe 22.
  • the discharge port 34 is provided with a discharge valve 24 that prevents the refrigerant from flowing backward from the high-pressure portion to the discharge port 34 side.
  • the electric motor unit 29 includes an electric motor rotor 6 fixed to the main shaft 8 and an electric motor stator 7 fixed to the sealed container 17.
  • the electric motor unit 29 is driven by energization of the electric motor stator 7 to rotate the main shaft 8. Further, the swing scroll 2 is caused to swing through the main shaft 8.
  • the rotary compressor 100 also has a thrust plate 4 serving as a thrust bearing for supporting the orbiting scroll 2 in the axial direction, and prevents the orbiting scroll 2 from rotating and swings the frame 3 to provide an orbiting motion.
  • An Oldham ring 5 that is movably supported, a slider 9 that supports the orbiting scroll 2 to revolve the orbiting scroll 2, and a main bearing 3a and a main shaft of the frame 3 that are in the vicinity of the eccentric slider shaft portion 8a.
  • the main shaft 8 rotates with the rotation of the electric motor rotor 6 to revolve the orbiting scroll 2.
  • the upper portion of the main shaft 8 is supported by a main bearing 3 a formed on the frame 3.
  • the lower portion of the main shaft 8 is rotatably supported by a sub bearing 14 formed at the center of a sub frame 13 provided at the lower portion of the sealed container 20.
  • the auxiliary bearing 14 is press-fitted and fixed in a bearing housing portion whose outer ring is formed in the central portion of the sub-frame 13.
  • the subframe 13 is provided with a positive displacement oil pump 15 for pumping oil from the oil sump 16 at the bottom of the sealed container 20 and supplying the oil to each sliding portion, and transmits the rotational force to the oil pump 15.
  • a pump shaft portion 8 b is integrally formed with the main shaft 8.
  • the main shaft 8 has an oil supply penetrating in the vertical direction (axial direction) from the lower end of the pump shaft portion 8b to the upper end of the eccentric slider shaft portion 8a and supplied to the sliding portion of the bearing and the compression mechanism portion 28.
  • a passage 8c is formed, and a bearing oil supply passage (not shown) for supplying oil to the auxiliary bearing 14 and the main bearing 3a is formed orthogonal to the oil supply passage 8c, and between the main bearing 3a and the auxiliary bearing 14 is formed.
  • a bypass path 8 d is formed which branches from the oil supply path 8 c and communicates with the outside of the main shaft 8 and discharges oil from the outlet to the outside of the main shaft 8.
  • the oil stored in the bottom of the sealed container 20 passes through the oil supply passage 8c and is supplied to the bearing and the sliding portion of the compression mechanism unit 28.
  • the portion passes through a bearing oil supply passage (not shown) and is supplied to the auxiliary bearing 14 and the main bearing 3a.
  • a part of the oil stored in the bottom of the sealed container 20 passes through the bypass path 8d according to the rotational speed of the electric motor unit 29 and is discharged from the outlet to the outside of the main shaft 8.
  • An oil pump 15 communicates with the lower end side of the oil supply passage 8c, the reed valve 30 for opening and closing the outlet of the bypass passage 8d on the outer peripheral portion of the main shaft 8, and the lift amount of the reed valve 30 superimposed on the reed valve 30.
  • An oil supply bypass mechanism 33 including a reed valve stopper 31 for regulating (opening height) and a screw 32 as a fastening means is provided.
  • the reed valve 30 is formed in a flat plate shape with, for example, stainless steel having spring properties.
  • FIG. 2 is an enlarged cross-sectional view of the oil supply bypass mechanism 33 of the rotary compressor 100 according to Embodiment 1 of the present invention.
  • a reed valve 30 is fastened with a screw 32 to a fastening surface 8 e formed on the outer peripheral surface of the main shaft 8 in parallel with the axial direction.
  • a seating surface 8 f for opening and closing the outlet of the bypass passage 8 d by the reed valve 30 is formed on the outer periphery of the main shaft 8 on the outer periphery of the outlet of the bypass passage 8 d. That is, the outlet of the bypass path 8d is formed in the surface of the seating surface 8f.
  • the seating surface 8f has an inclined shape, and the inclination is defined as the fastening surface 8e so that the reed valve 30 has a predetermined deflection amount ⁇ with respect to the axial direction of the main shaft 8 (relative to the fastening surface 8e).
  • the shape is such that the amount of protrusion of the main shaft 8 outward in the radial direction increases in the opposite direction. Since the reed valve 30 bends due to the inclination of the seating surface 8f, the reed valve 30 is in contact with the seating surface 8f in a state in which a preload due to the deflection is applied, and the outlet of the bypass path 8d in the seating surface 8f is closed. ing.
  • the deflection amount ⁇ of the seating surface 8f (relative to the fastening surface 8e) is less than or equal to a predetermined number of revolutions of the motor unit 29 (preload acting on the seating surface 8f due to deflection of the reed valve 30)> (pump of the oil pump 15 (Load due to pressure + centrifugal force acting on the reed valve 30 due to rotation of the electric motor unit 29).
  • the predetermined rotational speed is, for example, the rotational speed at which the amount of oil supplied from the oil pump 15 is larger than the amount of oil supplied to the bearing.
  • the outlet of the bypass path 8d in the seating surface 8f is closed by the preload (preload) due to the deflection of the reed valve 30 acting on the seating surface 8f.
  • the outermost diameter of the main shaft 8 at a position where the seating surface 8f is formed is formed to be smaller than the inner diameter of the electric motor rotor 6 so that the electric motor rotor 6 can be mounted from the lower end of the main shaft 8.
  • FIG. 3 is a longitudinal sectional view showing the flow of oil in rotary compressor 100 according to Embodiment 1 of the present invention.
  • white arrows indicate the flow of refrigerant gas
  • black arrows indicate the flow of oil.
  • a general commercial power source of 50 Hz or 60 Hz is used as the power source, but an inverter power source is also used so that the rotational speed can be driven in the range of 600 to 10000 rpm in order to make the refrigerant circulation amount variable.
  • the eccentric slider shaft portion 8 a rotates in the rocking bearing 2 a via the slider 9 and transmits a driving force to the rocking scroll 2.
  • an Oldham groove (not shown) of the orbiting scroll 2 that accommodates a key portion (not shown) formed on one surface of the Oldham ring 5 and a key formed on the other surface of the Oldham ring 5.
  • the oscillating scroll 2 is restrained from rotating by the Oldham's groove (not shown) of the frame 3 that accommodates the portion (not shown) and the Oldham ring 5 that reciprocates inside thereof, and performs the oscillating motion.
  • the frame 3 and the subframe 13 are fixed in the sealed container 20, but due to variations in accuracy at the time of fixation and variations in accuracy of individual components, the shaft misalignment between the main bearing 3 a and the sub-bearing 14 occurs. Further, the deflection of the main shaft 8 is also added, and the main bearing 3a and the main shaft 8, and the auxiliary bearing 14 and the main shaft 8 are not necessarily parallel.
  • a sleeve 10 is accommodated between the main shaft 8 and the main bearing 3a.
  • the main shaft 8 is inclined with respect to the main bearing 3a, but the second pipette portion (not shown) contacts the inner peripheral surface of the sleeve 10.
  • the second pipette part absorbs the inclination of the main shaft 8. Thereby, the outer periphery of the sleeve 10 can always slide in parallel with the main bearing 3a.
  • the slider 9 is accommodated between the eccentric slider shaft portion 8a of the main shaft 8 and the rocking bearing 2a. Therefore, when the eccentric slider shaft portion 8a is bent, the eccentric slider shaft portion 8a of the main shaft 8 is inclined with respect to the rocking bearing 2a, but the first pipette portion (not shown) contacts the slider surface of the slider 9. The first pipette part absorbs the inclination of the main shaft 8. As a result, the outer periphery of the slider 9 can always slide in parallel with the rocking bearing 2a.
  • the refrigerant in the refrigerant circuit is sucked into the sealed container 20 from the refrigerant suction pipe 21, and is formed by a spiral portion of the orbiting scroll 2 and a spiral portion of the fixed scroll 1 from the suction port (not shown) of the frame 3. Enter chamber 23.
  • the compression chamber 23 moves to the center of the orbiting scroll 2 by the orbiting motion of the orbiting scroll 2, and the refrigerant is compressed by further reducing the volume.
  • the fixed refrigerant 1 and the orbiting scroll 2 are subjected to a load for separating them in the axial direction by the compressed refrigerant.
  • the orbiting scroll 2 is constituted by the orbiting bearing 2 a and the thrust plate 4. The load is supported by the bearing.
  • the compressed refrigerant passes through the discharge port 34 of the fixed scroll 1, pushes open the discharge valve 24, passes through the high-pressure portion in the closed container 19, and is discharged from the closed container 20 to the refrigerant circuit through the refrigerant discharge pipe 22.
  • the oil pump 15 is driven by the pump shaft portion 8b of the rotating main shaft 8, and the oil is pumped up from the oil reservoir 16 at the bottom of the sealed container 20 through the oil supply passage 8c.
  • the pumped-up oil is first supplied to the sub-bearing 14, and the remainder is supplied to a plurality of sliding portions on the oil supply bypass mechanism 33 and the closed container top 19.
  • the sliding portion on the closed container 19 for example, the sliding portion between the rocking bearing 2 a of the rocking scroll 2 and the thrust plate 4, and the sliding of the spiral portion of the rocking scroll 2 and the spiral portion of the fixed scroll 1 are used.
  • FIG. 4 is an explanatory diagram for explaining a load acting on the oil supply bypass mechanism 33 of the rotary compressor 100 according to the first embodiment of the present invention
  • FIG. 5 is a rotary type according to the first embodiment of the present invention. It is a graph which shows the relationship between the rotation speed of the compressor 100, and upper oil supply amount.
  • the horizontal axis represents the number of revolutions of the electric motor unit 29, and the vertical axis represents the amount of oil pumped up to the upper closed container 19 positioned above the oil supply bypass mechanism 33 (hereinafter referred to as the upper oil supply amount).
  • the broken line represents the amount of oil supplied with respect to the rotational speed when the oil supply bypass mechanism 33 is not provided.
  • the operation of the oil supply bypass mechanism 33 when the electric motor unit 29 is equal to or less than the predetermined rotation speed N L will be described.
  • the motor unit 29 is driven at a rotation speed equal to or lower than a predetermined rotation speed N L, first, the auxiliary bearing 14 is supplied with oil as described above.
  • the shape of the seating surface 8f of the reed valve 30 is opposite to the fastening surface 8e so that the reed valve 30 has a predetermined deflection amount ⁇ with respect to the axial direction of the main shaft 8 (relative to the fastening surface 8e).
  • the inclination is such that the amount of protrusion outward in the radial direction increases toward the side, and the preload Fp due to the deflection of the reed valve 30 in the stationary state closes the outlet of the bypass passage 8d (the radial direction of the main shaft 8). Acting on the inside).
  • a preload Fp that satisfies (Fo + Fc) ⁇ Fp is applied at a predetermined rotational speed NL or less. For this reason, the preload Fp of the reed valve 30 acts on the seating surface 8f at the rotational speed N L or less, and the outlet of the bypass passage 8d in the seating surface 8f is closed by the reed valve 30.
  • the oil that has been gas-liquid separated in the hermetic container 20 without being discharged to the outside of the rotary compressor 100 passes through the clearance around the motor rotor 6 and the motor stator 7 and the oil drain pipe 27 connected to the frame 3. It is returned to the reservoir 16.
  • the load Fc caused by the centrifugal force that acts uniformly on the reed valve 30 by rotating together with it acts in the direction (in the radial direction outside) of opening the outlet of the bypass passage 8d.
  • the preload Fp is acting on the reed valve 30 as described above, at a rotational speed higher than the rotational speed NL , (Fo + Fc)> Fp is satisfied and the reed valve 30 is opened, and oil flows from the bypass 8d to the main shaft 8. It is discharged outside. Therefore, as shown in FIG. 5, the amount of oil supplied to the top 19 of the sealed container is limited as compared with the case where the bypass is not performed at a rotational speed greater than the rotational speed NL . Note that the operation of the oil pumped up on the airtight container 19 is the same as described above, and thus the description thereof is omitted.
  • the oil taken into the compression chamber 23 has an effect of reducing refrigerant leakage of the rotary compressor 100.
  • the ratio of the refrigerant leakage flow rate from the gap with respect to the refrigerant circulation amount is larger as the engine speed is lower, and the efficiency improvement due to the oil seal effect becomes remarkable.
  • the oil discharged to the outside of the rotary compressor 100 becomes a factor that deteriorates the performance of the heat exchanger provided in the refrigeration cycle apparatus.
  • the oil separation efficiency in the hermetic container 20 is higher as the engine speed is lower, and the amount of oil discharged to the outside of the rotary compressor 100 is smaller than the circulation amount of the refrigerant.
  • the oil separation efficiency in the hermetic container 20 decreases, and the amount of oil discharged to the outside of the rotary compressor 100 increases with respect to the refrigerant circulation amount. Therefore, from the viewpoint of increasing the efficiency of the refrigeration cycle apparatus, in the low rotation speed range where the effect of reducing the leakage of refrigerant due to oil is high, the oil supply amount of 100% is secured from the oil pump 15 without limiting the oil supply amount to the upper part. In a high rotational speed range where the effect of reducing refrigerant leakage is low and the amount of oil flowing out of the rotary compressor 100 increases, the amount of oil supplied from the oil pump 15 to the upper portion is limited so that excessive oil is not taken into the compression chamber 23. It is desirable to do.
  • the seating surface 8f is formed on the outer peripheral surface of the main shaft 8, and the seating surface 8f has the outlet of the bypass passage 8d in the surface, and is fastened with respect to the axial direction of the main shaft 8.
  • the reed valve 30 is formed in an inclined shape such that the amount of protrusion outward in the radial direction increases toward the direction opposite to the fastening surface 8e so that the reed valve 30 has a predetermined deflection amount ⁇ (relative to the surface 8e).
  • the oil supply bypass mechanism 33 having the above characteristics can be configured with only the simple reed valve 30, and the number of parts is reduced and the cost is reduced. Is effective.
  • the oil supply bypass mechanism 33 when the electric motor unit 29 has a predetermined number of revolutions or less, the oil supply amount from the oil pump 15 to the upper part is secured 100%, and when the motor part 29 is larger than the predetermined number of revolutions, the oil pump 15 The amount of oil supply from the top to the top can be limited, and there is an effect that a highly efficient refrigeration cycle apparatus can be obtained at a wide rotational speed.
  • FIG. FIG. 6 is an enlarged cross-sectional view of the oil supply bypass mechanism 63 of the rotary compressor 200 according to Embodiment 2 of the present invention.
  • the configuration other than the oil supply bypass mechanism 63 is the same as that of the first embodiment, and only the parts different from the first embodiment will be described.
  • the seating surface 68 f is formed on the outer peripheral surface of the main shaft 8 parallel to the axial direction, and the fastening surface 68 e is formed with respect to the axial direction of the main shaft 8.
  • the reed valve 30 has a predetermined deflection amount ⁇ (with respect to the seating surface 68f), it is formed in an inclined shape in which the amount of protrusion outward in the radial direction increases toward the direction opposite to the seating surface 68f. Yes.
  • the effective length of the screw 32 that is the fastening means that is, the number of pitches of the screw grooves is also increased as compared with the first embodiment. It becomes possible. Therefore, there is an effect that the fastening force by the screw 32 can be improved.
  • FIG. 7 is an enlarged cross-sectional view of the oil supply bypass mechanism 73 of the rotary compressor 300 according to Embodiment 3 of the present invention.
  • the configuration other than the oil supply bypass mechanism 73 is the same as that of the first embodiment, and only the parts different from the first embodiment will be described.
  • both the fastening surface 78e and the seating surface 78f are inclined with respect to the vertical direction of the main shaft 8.
  • the seating surface 78f has a radius toward the direction opposite to the fastening surface 78e so that the reed valve 30 has a predetermined deflection amount ⁇ / 2 with respect to the axial direction of the main shaft 8. It is formed in an inclined shape that increases the amount of protrusion outward in the direction.
  • the outermost diameter of the main shaft 8 at the position where the fastening surface 78e and the seating surface 78f are formed is smaller than the inner diameter of the motor rotor 6 so that the motor rotor 6 can be mounted from the lower end of the main shaft 8. It is necessary to keep.
  • the outer peripheral surface of the main shaft 8 is at least the deflection amount ⁇ . It was necessary to cut out by the minute.
  • the deflection amount of the reed valve 30 can be taken by both the fastening surface 78e and the seating surface 78f, the cutout amount of the outer peripheral surface of the main shaft 8 can be reduced by a maximum of ⁇ / 2.
  • the rigidity of the main shaft 8 can be improved as compared with the first and second embodiments.
  • FIG. 8 is a cross-sectional view of a rotary compressor 400 according to Embodiment 4 of the present invention
  • FIG. 9 is a cross-sectional view taken along the line AA in FIG.
  • the configuration other than the oil supply bypass mechanism 74 is the same as that of the first embodiment, and only the parts different from the first embodiment will be described.
  • a ring-shaped reed valve holder 50 is provided between the reed valve 30 and the main shaft 8, and the reed valve holder 50 has a lower end surface.
  • a fastening surface 50e and a seating surface 50f are formed, and the reed valve 30 is fastened to the fastening surface 50e with screws 32.
  • the shape of the reed valve holder 50 is axisymmetric so that a load due to unbalance does not act during rotation.
  • the reed valve holder 50 corresponds to a “holder” of the present invention.
  • the reed valve 30 that opens and closes the outlet of the bypass 8d of the main shaft 8 is fastened to a fastening surface 50e formed on the lower end surface of the reed valve holder 50. That is, the reed valve 30 is provided so as to open and close in the axial direction of the main shaft 8, and centrifugal force due to rotation does not act in the opening (deflection) direction of the reed valve 30, so that only the pump pressure acts.
  • the deflection amount ⁇ of the seating surface 50f (relative to the fastening surface 50e) is less than or equal to a predetermined number of revolutions of the motor unit 29 (preload acting on the seating surface 50f due to the deflection of the reed valve 30)> (pump of the oil pump 15 Pressure).
  • the outlet of the bypass passage 50d in the seating surface 50f is closed by the preload (preload) due to the deflection of the reed valve 30 acting on the seating surface 50f.
  • the rotational speed is larger than the predetermined rotational speed, (the preload acting on the seating surface 50f due to the deflection of the reed valve 30) ⁇ (the load due to the pump pressure of the oil pump 15), the reed valve 30 is opened and the bypass passage 50d Oil is discharged to the outside of the main shaft 8.
  • the main shaft 8 is provided with the main shaft 8 as in the first to third embodiments. There is no need to form a flat surface or a screw hole for providing the reed valve 30, and there is an effect that the rigidity of the main shaft 8 can be prevented from being lowered as compared with the first to third embodiments.
  • the fastening surface 50e and the seating surface 50f are formed on the lower end surface of the reed valve holder 50.
  • the present invention is not limited thereto, and the fastening surface 50e and the seating surface 50f are formed on the upper end surface of the reed valve holder 50. And may be formed.
  • FIG. 10 is a cross-sectional view of a rotary compressor 500 according to Embodiment 5 of the present invention
  • FIG. 11 is a cross-sectional view taken along the line BB of FIG.
  • the configuration other than the oil supply bypass mechanism 75 is the same as that of the fourth embodiment, and only the parts different from the fourth embodiment will be described.
  • the reed valve 30 is provided on the lower end surface of the reed valve holder 50, whereas in the fuel supply bypass mechanism 75 according to the fifth embodiment, the reed valve 30 is provided as shown in FIGS. Provided on the outer peripheral side surface of the reed valve holder 51.
  • the outer periphery of the ring-shaped reed valve holder 51 is cut to form a flat surface parallel to the axial direction of the main shaft 8, and a fastening surface 51e and a seating surface 51f are formed on the flat surface.
  • the outer shape of the reed valve holder 51 is axisymmetric so that a load due to unbalance does not act on the shaft during rotation.
  • a cylindrical holder cover 80 including the balancer 12 is attached to the outside of the reed valve holder 51.
  • the reed valve holder 51 corresponds to the “holder” of the present invention
  • the holder cover 80 corresponds to the “cover” of the present invention.
  • the axial thickness of the main shaft 8 of the oil supply bypass mechanism 75 can be made thinner than that of the fourth embodiment. That is, the oil supply bypass mechanism 75 is compactly accommodated upward, so that even when the oil level becomes higher than the subframe 13, the oil level is not agitated by the oil supply bypass mechanism 75 and oil can be prevented from being rolled up. Further, by covering the oil supply bypass mechanism 75 with the cylindrical holder cover 80, the oil floating and falling in the container can be prevented from being stirred and atomized by the oil supply bypass mechanism 75, and the effect of reducing oil rising can be reduced. There is.
  • the balancer 12 and the reed valve holder 51 are provided separately.
  • the balancer 12 may be configured as the reed valve holder 51, and there is an effect of further downsizing.
  • the present invention is not limited to this, and a fastening method other than the screw may be used.
  • the maximum rotational speed is set to 10,000 rpm.
  • the maximum rotational speed may be 10,000 rpm or higher, and a higher efficiency improvement effect is obtained as the upper limit of the rotational speed is increased.
  • the scroll-type rotary compressors 100, 200, 300, 400, and 500 have been described.
  • the present invention is not limited to this.
  • a rotary type compressor may be used as long as it has an oil pump at the end of the main shaft and has a mechanism for supplying oil to the sliding portion from an oil supply passage provided in the main shaft. Further, by providing the oil supply bypass mechanism, there is an effect that a highly efficient refrigeration cycle can be obtained.

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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)
PCT/JP2014/071307 2014-01-08 2014-08-12 回転式圧縮機 WO2015104863A1 (ja)

Priority Applications (2)

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JP2015556704A JP6300829B2 (ja) 2014-01-08 2014-08-12 回転式圧縮機
CN201480072634.6A CN105899808B (zh) 2014-01-08 2014-08-12 旋转式压缩机

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JP2014-002005 2014-01-08
JP2014002005 2014-01-08

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JP2017078360A (ja) * 2015-10-20 2017-04-27 三菱重工業株式会社 スクロール流体機械
JP2017078361A (ja) * 2015-10-20 2017-04-27 三菱重工業株式会社 スクロール流体機械
WO2021149180A1 (ja) * 2020-01-22 2021-07-29 三菱電機株式会社 圧縮機

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CN111684158B (zh) * 2018-02-06 2022-03-08 三菱电机株式会社 压缩机和制冷循环装置
CN111089058A (zh) * 2018-10-24 2020-05-01 艾默生环境优化技术(苏州)有限公司 旋转机械的供油机构以及旋转机械
CN111089056A (zh) * 2018-10-24 2020-05-01 艾默生环境优化技术(苏州)有限公司 旋转机械的供油机构和具有该供油机构的旋转机械
WO2020083310A1 (zh) * 2018-10-24 2020-04-30 艾默生环境优化技术(苏州)有限公司 旋转机械的供油机构以及旋转机械
WO2020083309A1 (zh) * 2018-10-24 2020-04-30 艾默生环境优化技术(苏州)有限公司 旋转机械的供油机构和具有该供油机构的旋转机械
JP7241915B2 (ja) * 2019-12-04 2023-03-17 三菱電機株式会社 圧縮機
WO2021124557A1 (ja) * 2019-12-20 2021-06-24 三菱電機株式会社 圧縮機システム、圧縮機および冷凍サイクル装置
CN113123970B (zh) * 2019-12-31 2023-11-14 比亚迪股份有限公司 压缩机及具有其的车辆

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JP2017078361A (ja) * 2015-10-20 2017-04-27 三菱重工業株式会社 スクロール流体機械
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