WO2023148867A1 - Compresseur et dispositif à cycle de réfrigération - Google Patents

Compresseur et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2023148867A1
WO2023148867A1 PCT/JP2022/004176 JP2022004176W WO2023148867A1 WO 2023148867 A1 WO2023148867 A1 WO 2023148867A1 JP 2022004176 W JP2022004176 W JP 2022004176W WO 2023148867 A1 WO2023148867 A1 WO 2023148867A1
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WIPO (PCT)
Prior art keywords
drive shaft
annular member
oil
container
fixed
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Application number
PCT/JP2022/004176
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English (en)
Japanese (ja)
Inventor
秀明 北川
勝俊 辰己
Original Assignee
三菱電機株式会社
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Priority to PCT/JP2022/004176 priority Critical patent/WO2023148867A1/fr
Publication of WO2023148867A1 publication Critical patent/WO2023148867A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid

Definitions

  • the present disclosure relates to a compressor and a refrigeration cycle device that compress working gas.
  • a compressor that includes a compression mechanism and an electric motor in a sealed container, and drives the compression mechanism with the electric motor to compress a working gas such as a refrigerant.
  • the electric motor consists of a motor stator and a motor rotor.
  • oil is stored, for example, in an oil reservoir space formed at the bottom of a closed container. The oil lubricates the sliding portions of the components that make up the compression mechanism, and also seals the compression mechanism, thereby assisting the smooth compression of the refrigerant.
  • the low-pressure refrigerant sucked from the suction pipe is compressed in the compression mechanism to become a high-pressure refrigerant.
  • the high-pressure refrigerant containing oil is once discharged from the compression mechanism into the container, and then guided out of the container through a discharge pipe.
  • Patent Document 1 discloses a compressor in which an annular plate is provided above the oil reservoir space.
  • the annular plate since the annular plate is provided, the refrigerant in a gaseous state is prevented from scattering the oil stored in the oil reservoir space.
  • a plurality of baffle plates each having a large number of pores are fixed to the upper surface of the annular plate.
  • Patent Document 1 oil contained in high-pressure refrigerant collides with a baffle plate using a swirling flow, and the oil is separated from the refrigerant and drops into an oil reservoir space, thereby reducing the amount of oil discharged out of the container. We are trying to reduce the amount.
  • the compressor of Patent Document 1 has a large number of parts because a plurality of baffle plates are fixed to the annular plate.
  • the present disclosure has been made to solve the above-described problems, and provides a compressor and a refrigeration cycle device that reduce the amount of oil discharged out of the container while suppressing an increase in the number of parts. be.
  • the compressor according to the present disclosure includes a container that forms an outer shell and has an oil reservoir space that stores oil formed below the inside, an electric motor provided inside the container, and an electric motor attached to transmit the rotational force of the electric motor.
  • a drive shaft that rotates with the rotation of the drive shaft to compress the working gas; bearings that are provided in the container to rotatably support the drive shaft; a frame that supports the bearing; and an annular member provided on the upper part of the frame and arranged along the inner peripheral surface of the container around the drive shaft, wherein the annular member extends along the rotation direction of the drive shaft. and an upward slope portion that slopes upward from the lower end of the downward slope portion along the rotational direction of the drive shaft and forms an oil return gap between the frame and the frame for returning oil.
  • the working gas flows through the downward slope portion of the annular member due to the swirl flow generated by the rotation of the drive shaft and its own weight, and then passes through the oil return gap between the upward slope portion of the annular member and the frame. to the oil sump space. Since the working gas circulates in the oil reservoir space and stays below the ascending slope portion of the annular member, it is possible to suppress the oil from scattering. Thus, the amount of oil discharged out of the container can be reduced simply by providing the annular member. Therefore, the amount of oil discharged out of the container can be reduced while suppressing an increase in the number of parts.
  • FIG. 1 is a circuit diagram showing a refrigeration cycle device according to Embodiment 1 of the present disclosure
  • FIG. 1 is an axial sectional view showing a compressor according to Embodiment 1 of the present disclosure
  • FIG. 1 is an enlarged view showing part of a compressor according to Embodiment 1 of the present disclosure
  • FIG. 1 is a circumferential cross-sectional view showing a compressor according to Embodiment 1 of the present disclosure
  • FIG. 1 is a perspective view showing an annular member according to Embodiment 1 of the present disclosure
  • FIG. 1 is a perspective view showing an annular member according to Embodiment 1 of the present disclosure
  • FIG. 1 is a perspective view showing an annular member according to Embodiment 1 of the present disclosure
  • FIG. FIG. 4 is a side view showing the annular member according to Embodiment 1 of the present disclosure
  • FIG. 4 is a perspective view showing the action of the annular member according to Embodiment 1 of the present disclosure
  • FIG. 11 is a perspective view showing an annular member according to Embodiment 2 of the present disclosure
  • FIG. 11 is a side view showing an annular member according to Embodiment 2 of the present disclosure
  • FIG. 10 is a perspective view showing the action of the annular member according to the second embodiment of the present disclosure
  • FIG. 1 is a circuit diagram showing a refrigeration cycle apparatus 200 according to Embodiment 1.
  • the refrigeration cycle device 200 is a device that adjusts air in an indoor space, and includes an outdoor unit 201 and an indoor unit 202 as shown in FIG.
  • the outdoor unit 201 is provided with, for example, a compressor 100, a channel switching device 103, an outdoor heat exchanger 104, an outdoor fan 104a, a gas-liquid separator 107, and an expansion section 105.
  • the indoor unit 202 is provided with, for example, an indoor heat exchanger 106 and an indoor fan 106a.
  • the refrigeration cycle device 200 is illustrated as an air conditioner, but it may be various industrial machines such as a refrigerator, a freezer, a refrigerating device, or a water heater.
  • a refrigerating circuit 203 is configured by connecting the compressor 100, the flow path switching device 103, the outdoor heat exchanger 104, the gas-liquid separator 107, the expansion section 105, and the indoor heat exchanger 106 by a pipe 204.
  • the compressor 100 sucks a low-temperature, low-pressure working gas, compresses the sucked working gas, and discharges the high-temperature, high-pressure working gas.
  • the compressor 100 is, for example, a capacity-controllable inverter compressor and a scroll compressor.
  • the channel switching device 103 switches the direction in which the working gas flows in the refrigerating circuit 203, and is, for example, a four-way valve.
  • the outdoor heat exchanger 104 exchanges heat, for example, between outdoor air and working gas.
  • the outdoor heat exchanger 104 acts as a condenser during cooling operation and acts as an evaporator during heating operation.
  • the gas-liquid separator 107 separates the gas-liquid two-phase working gas into a saturated gas working gas and a saturated liquid working gas. Gas-liquid separator 107 and compressor 100 are connected by gas return pipe 110 .
  • the expansion part 105 is a pressure reducing valve or an expansion valve that reduces the pressure of the working gas and expands it.
  • the expansion part 105 is, for example, an electronic expansion valve whose opening is adjusted.
  • the indoor heat exchanger 106 exchanges heat, for example, between the indoor air and the working gas.
  • the indoor heat exchanger 106 acts as an evaporator during cooling operation, and acts as a condenser during heating operation.
  • the indoor air blower 106 a is a device that sends indoor air to the indoor heat exchanger 106 .
  • heating operation Next, operation modes of the refrigeration cycle device 200 will be described.
  • the channel switching device 103 is connected to the solid line side in FIG. 1, and the refrigerant flows along the solid line arrows.
  • the working gas sucked into the compressor 100 is compressed by the compressor 100 and discharged as a high-temperature and high-pressure gas.
  • the high-temperature and high-pressure gaseous working gas discharged from the compressor 100 passes through the flow path switching device 103 and flows into the indoor-side heat exchanger 106 acting as a condenser.
  • the refrigerant is heat-exchanged with the indoor air sent by the indoor blower 106a, condensed and liquefied. At this time, the indoor air is warmed, and heating is performed in the room.
  • the condensed liquid working gas flows into the gas-liquid separator 107 and is separated into gaseous working gas and liquid working gas.
  • the gaseous working gas returns to the compressor 100 and the liquid working gas flows to the expansion section 105 side.
  • the liquid working gas flows into the expansion section 105, where it is expanded and decompressed to become a low-temperature, low-pressure gas-liquid two-phase working gas.
  • the gas-liquid two-phase working gas flows into the outdoor heat exchanger 104 acting as an evaporator, and in the outdoor heat exchanger 104, heat is exchanged with the outdoor air sent by the outdoor blower 104a to evaporate. to gasify.
  • the vaporized low-temperature, low-pressure gaseous working gas passes through the flow path switching device 103 and is sucked into the compressor 100 .
  • the passage switching device 103 is connected to the dashed line side in FIG. 1, and the refrigerant flows along the dashed arrow.
  • the working gas sucked into the compressor 100 is compressed by the compressor 100 and discharged as a high-temperature and high-pressure gas.
  • the high-temperature and high-pressure gaseous working gas discharged from the compressor 100 passes through the flow path switching device 103 and flows into the outdoor heat exchanger 104 acting as a condenser.
  • the outdoor heat exchanger 104 the refrigerant is heat-exchanged with the outdoor air sent by the outdoor blower 104a to be condensed and liquefied.
  • the condensed liquid working gas flows into the expansion section 105, where it is expanded and decompressed to become a low-temperature, low-pressure gas-liquid two-phase working gas.
  • the gas-liquid two-phase working gas is separated by the gas-liquid separator 107 into a gas-state working gas and a liquid-state working gas.
  • the gaseous working gas returns to the compressor 100 and the liquid working gas flows to the indoor heat exchanger 106 side.
  • the liquid state working gas flows into the indoor heat exchanger 106 acting as an evaporator, where it is heat-exchanged with the indoor air sent by the indoor blower 106a to evaporate into gas. become At this time, the indoor air is cooled, and cooling is performed in the room.
  • the vaporized low-temperature, low-pressure gaseous working gas passes through the flow path switching device 103 and is sucked into the compressor 100 .
  • the refrigeration cycle device 200 may not have the channel switching device 103 . In this case, the refrigeration cycle device 200 becomes a dedicated heating machine or a dedicated cooling machine. Also, the working gas is, for example, a refrigerant such as R407, R410A or R32.
  • FIG. 2 is an axial cross-sectional view showing compressor 100 according to Embodiment 1 of the present disclosure.
  • the compressor 100 sucks and compresses the working gas circulating in the refrigerating circuit 203, for example, and discharges it in a high-temperature and high-pressure state, and is, for example, a closed vertical scroll compressor.
  • Compressor 100 includes container 1, electric motor 16, drive shaft 19, compression mechanism 2, main bearing 25, guide frame 30, bearing 27, frame 37, and annular A member 50 is provided.
  • the container 1 is a closed container that constitutes the outer shell of the compressor 100 and has a cylindrical shape.
  • the container 1 accommodates the compression mechanism 2, the electric motor 16 and the drive shaft 19, and has pressure resistance.
  • the compression mechanism section 2 compresses the working gas sucked into the container 1 from the suction pipe 7 and includes a fixed scroll 4 and an orbiting scroll 3 .
  • the fixed scroll 4 is fixed by bolts (not shown) or the like to a guide frame 30 supported by the container 1 above the orbiting scroll 3, and has a fixed base plate 4b and a fixed spiral body 4a.
  • the fixed base plate 4 b is a plate-like member and constitutes the upper surface of the compression mechanism section 2 .
  • the fixed spiral body 4a is a spiral projection extending downward from the lower surface of the fixed base plate 4b.
  • the orbiting scroll 3 has an orbiting base plate 3b and an orbiting spiral body 3a.
  • the rocking plate 3 b is a plate-like member arranged above the drive shaft 19 .
  • the rocking spiral body 3a is a spiral projection extending upward from the upper surface of the rocking base plate 3b.
  • the fixed scroll 4 and the orbiting scroll 3 are arranged so that the fixed spiral body 4a and the orbiting scroll body 3a face each other.
  • a fixed spiral body 4a and an oscillating spiral body 3a are combined, and a compression chamber 2b is formed between the fixed spiral body 4a of the fixed scroll 4 and the oscillating spiral body 3a of the oscillating scroll 3.
  • a central portion of the compression chamber 2b serves as a discharge chamber 2a, and the discharge chamber 2a is connected to a discharge port 12 formed in the fixed base plate 4b.
  • the fixed spiral body 4a and the fixed base plate 4b form suction volumes on the inward and outward surface sides of the orbiting scroll 3, respectively.
  • the compliant frame 31 in which the gas introduction passage 14 is formed and the fixed base plate 4b having the air bleed holes 3e constitute an air bleed mechanism.
  • a pair of fixed-side Oldham ring grooves 15a are formed in a straight line on the outer peripheral portion of the fixed scroll 4 .
  • a pair of fixed-side keys 42a are installed in the fixed-side Oldham ring groove 15a so as to be reciprocally slidable.
  • a cylindrical boss portion 3c is formed on the lower surface of the rocking base plate 3b of the rocking scroll 3.
  • a swing bearing 26 is provided on the inner surface of the boss portion 3c. The swing shaft 21 of the drive shaft 19 is inserted into the swing bearing 26 , and the rotation of the swing shaft 21 causes the swing scroll 3 to revolve.
  • a swinging thrust surface 3d slidable with the thrust surface 33 of the compliant frame 31 is formed on the surface of the swinging base plate 3b of the swinging scroll 3 on which the boss portion 3c is formed.
  • a pair of rocking-side Oldham ring grooves 15b are formed in a straight line on the outer peripheral portion of the rocking scroll 3. As shown in FIG.
  • the swing-side Oldham ring groove 15b has a phase difference of about 90 degrees with respect to the fixed-side Oldham ring groove 15a, and the two Oldham rings 40 allow a pair of swing-side keys 42b to freely reciprocate. is set up.
  • a reciprocating sliding surface 41 is formed on the outer peripheral portion of the thrust surface 33 of the compliant frame 31, on which the rocking side key 42b of the Oldham ring 40 reciprocates.
  • the suction side space 8 the space around the base plate outside the fixed spiral body 4a of the fixed scroll 4 and the orbiting spiral body 3a of the orbiting scroll 3 (hereinafter referred to as the suction side space 8) is filled with the suction gas atmosphere (suction pressure).
  • suction pressure suction pressure
  • Ps low-pressure space
  • the electric motor 16 rotates the drive shaft 19 and generates a rotational force with a variable rotational speed.
  • the electric motor 16 has an electric motor rotor 16a and an electric motor stator 16b.
  • the electric motor rotor 16a is fixed to the drive shaft 19 by shrink fitting or the like, and a plurality of first through-flow passages 17a passing through in the axial direction are formed line-symmetrically or point-symmetrically with respect to the axis. there is Further, the motor rotor 16a and the motor stator 16b are positioned so that a minute gap 17c is formed between the motor rotor 16a and the motor stator 16b.
  • a glass terminal (not shown) is connected to the motor stator 16b, and the glass terminal is connected to a lead wire (not shown) for obtaining electric power from the outside.
  • the electric motor stator 16b is fixed to the container 1 by shrink fitting or the like, and a second through-flow passage 17b formed by a notch is formed in the outer peripheral portion.
  • Balance weights 18a and 18b are fixed to the motor rotor 16a and the drive shaft 19 in order to balance the entire rotation system of the compressor 100.
  • the space below the electric motor 16 and above the frame 37 is called an annular member upper space 51a.
  • the drive shaft 19 is attached to the electric motor 16 , transmits the rotational force of the electric motor 16 to the compression mechanism section 2 , and has a main shaft 20 and a sub shaft 22 .
  • the main shaft 20 constitutes the upper portion of the drive shaft 19 and is supported by a main bearing 25 provided on the inner peripheral surface of the compliant frame 31 .
  • the secondary shaft 22 constitutes the lower portion of the drive shaft 19 and is supported by bearings 27 provided within a frame 37 fixed and supported by the container 1 .
  • a lower end surface of the drive shaft 19 is in contact with a thrust bearing 28, and the dead weight of the drive shaft 19 is supported by the thrust bearing 28.
  • the main bearing 25 is of cylindrical construction.
  • the main bearing 25 and the bearing 27 have a structure made of a slide bearing such as a copper-lead alloy, and support the drive shaft 19 rotatably.
  • an oil supply passage 23 extending axially from the end of the drive shaft 19 and a supply passage 24a communicating with the oil supply passage 23 and extending radially are formed. Oil is supplied to each sliding portion such as the main bearing 25 and the bearing 27 through the oil supply passage 23 and the supply passage 24a.
  • An oil supply passage 23 is opened at the axial upper end portion of the drive shaft 19 , and oil is supplied from the oil supply passage 23 .
  • a swing shaft 21 is installed on the drive shaft 19 and engaged with a swing bearing 26 formed on the boss portion 3 c of the swing scroll 3 . The oil supplied to the oil supply passage 23 is supplied to each sliding portion such as the main bearing 25 and the bearing 27 .
  • the main shaft 20 has a cylindrical structure similar to that of the main bearing 25 and is fitted into the main bearing 25 and rotatably supported by the main bearing 25 .
  • the supply path 24 a of the main shaft 20 is installed at a position covered by the main bearing 25 .
  • One side of the container 1 is connected with a suction pipe 7 through which the working gas is taken into the container 1, and the other side of the container 1 is connected with a discharge pipe 11 through which the compressed working gas is discharged to the outside of the container 1. It is connected.
  • a suction check valve 9 and a spring 10 are provided inside the suction pipe 7 .
  • the suction check valve 9 is urged by a spring 10 in a direction to close the suction pipe 7 . This prevents the working gas from flowing back from the suction pipe 7 to the outside of the container 1 .
  • a portion of the container 1 connected to the discharge pipe 11 is a high-pressure gas atmosphere 6 in which high-pressure working gas is retained.
  • An oil reservoir space 5 is formed in the bottom of the container 1 filled with the working gas compressed by the compression mechanism 2 .
  • the oil reservoir space 5 is a portion that reserves oil.
  • the oil is refrigerating machine oil that lubricates the sliding portions of the components that make up the compression mechanism 2 and that seals the compression mechanism 2 to assist in smooth refrigerant compression.
  • the oil reservoir space 5 is formed in the high-pressure gas atmosphere 6 below the frame 37 and the bearing 27 that support the lower end of the drive shaft 19 .
  • the drive shaft 19 is supported by a thrust bearing 28 at its lowermost end surface. Thrust bearing 28 is fixed to holder 29 , and holder 29 is fixed to frame 37 . Note that the frame 37 is also called a subframe.
  • the frame 37 has at least two fixing legs 37a fixed to the container 1 at its radial end, and extends toward the container 1 side.
  • the fixed leg portions 37a are arranged at equal intervals in the circumferential direction with the axis of the main shaft 20, which is the upper portion of the drive shaft 19, as a reference.
  • the fixed leg portion 37a is fixed inside the container 1 by welding or the like.
  • An annular member 50 is provided on the upper portion of the frame 37 , and the annular member 50 is arranged along the inner peripheral surface of the container 1 with the drive shaft 19 as the center.
  • a guide frame 30 is fixed to the container 1 above the electric motor 16 , and a frame 37 holding the drive shaft 19 is fixed to the container 1 below the electric motor 16 .
  • a compliant frame 31 is housed inside the guide frame 30 .
  • the compliant frame 31 is also called an abutment member.
  • a guide upper fitting cylindrical surface 30a is formed on the inner peripheral surface of the guide frame 30 on the fixed scroll 4 side of the compression mechanism portion 2 .
  • the guide upper mating cylindrical surface 30 a is engaged with a compliant upper mating cylindrical surface 35 a formed on the outer peripheral surface of the compliant frame 31 .
  • a guide lower fitting cylindrical surface 30b is formed on the inner peripheral surface of the guide frame 30 on the electric motor 16 side, and the guide lower fitting cylindrical surface 30b is formed on the outer peripheral surface of the compliant frame 31. It is engaged with the compliant lower mating cylindrical surface 35b.
  • An upper annular seal member 36 a and a lower annular seal member 36 b are arranged at two locations on the outer peripheral surface of the compliant frame 31 .
  • the inner surface of the guide frame 30 and the outer surface of the compliant frame 31 are partitioned by an upper annular seal member 36a and a lower annular seal member 36b.
  • a compliant frame lower space 32b is formed between the upper annular seal member 36a and the lower annular seal member 36b.
  • FIG. 3 is an enlarged view showing part of the compressor 100 according to Embodiment 1 of the present disclosure
  • FIG. 4 is a circumferential cross-sectional view showing the compressor 100 according to Embodiment 1 of the present disclosure.
  • a gas introduction passage 14 is formed along the vertical direction to communicate between the thrust surface 33 and the compliant frame lower space 32b.
  • the gas introduction passage 14 is connected to an air bleed hole 3e formed in the rocking bed plate 3b of the rocking scroll 3 of the compression mechanism section 2. As shown in FIG. As shown in FIG.
  • the air bleed hole 3e consists of an air bleed inlet 3ei formed on the upper surface of the rocking base plate 3b and an air bleed outlet 3eo formed on the lower surface of the rocking base plate 3b. Further, as shown in FIG. 4, a flow path 30c is formed between the guide frame 30 and the inner wall of the container 1, through which the high-pressure working gas flowing out from the discharge port 12 flows.
  • an intermediate pressure space 38 which is an intermediate pressure space having a pressure lower than the discharge pressure and higher than the suction pressure
  • the compliant frame 31 is formed with an intermediate pressure regulating valve space 39d that accommodates an intermediate pressure regulating valve 39a that adjusts the pressure in the intermediate pressure space 38, an intermediate pressure regulating valve retainer 39b, and an intermediate pressure regulating spring 39c.
  • the intermediate pressure adjusting spring 39c is retracted and housed in a state of natural length.
  • the compliant frame 31 is formed with an intermediate through flow passage 39e that connects the intermediate pressure space 38 and the intermediate pressure regulating valve space 39d.
  • the intermediate pressure regulating valve space 39d and the compliant frame upper space 32a are connected.
  • the compliant frame upper space 32 a is formed so as to be connected to the inside of the Oldham ring 40 . Therefore, the intermediate pressure space 38 and the reciprocating sliding surface 41 of the Oldham ring 40 are connected via the intermediate through passage 39e, the intermediate pressure regulating valve space 39d, and the compliant frame upper space 32a.
  • annular member 50 5 and 6 are perspective views showing the annular member 50 according to Embodiment 1 of the present disclosure
  • FIG. 7 is a side view showing the annular member 50 according to Embodiment 1 of the present disclosure.
  • the annular member 50 is a member provided on the upper portion of the frame 37 and arranged along the inner peripheral surface of the container 1 with the drive shaft 19 as the center. As shown in FIGS. 5, 6 and 7, the annular member 50 has a fixed portion 52, a downward slope portion 50a, and an upward slope portion 50b.
  • the fixed portion 52 has a first fixed portion 52a and a second fixed portion 52b.
  • the first fixing portion 52 a is, for example, a member extending in the vertical direction and used to be fixed to the fixing leg portion 37 a of the frame 37 .
  • a first fixing hole 53a is formed in the first fixing portion 52a, and a fastener (not shown) is inserted into the first fixing hole 53a and fixed to the fixing leg portion 37a.
  • the second fixing portion 52b is a plate-like member and is used to be fixed to the fixing leg portion 37a of the frame 37. As shown in FIG.
  • the second fixing portion 52b is positioned at the same height as the lower end portion of the first fixing portion 52a, and is positioned on the diagonal line of the first fixing portion 52a.
  • a second fixing hole 53b is formed in the second fixing portion 52b, and a fastener (not shown) is inserted into the second fixing hole 53b and fixed to the fixing leg portion 37a.
  • the downward slope portion 50a slopes downward along the direction of rotation of the drive shaft 19 to rectify the working gas.
  • the descending slope portion 50a gradually slopes downward from the upper end of the first fixing portion 52a to the second fixing portion 52b.
  • the ascending slope portion 50b slopes upward along the rotational direction of the drive shaft 19 from the lower end side of the descending slope portion 50a.
  • the rising slope portion 50b slopes upward gradually from the second fixing portion 52b to the upper end portion of the first fixing portion 52a.
  • an oil return gap 50c is formed through which oil returns. That is, the oil return gap 50c is a gap formed between the upward slope portion 50b and the frame 37. As shown in FIG.
  • the annular member 50 is connected along the rotation direction of the drive shaft 19 in the order of the fixed portion 52, the downward slope portion 50a, the fixed portion 52, and the upward slope portion 50b. 5 and 6, the distance D1 between the inner peripheral surface of the annular member 50 and the drive shaft 19 is greater than the distance D2 between the inner peripheral surface and the outer peripheral surface of the annular member 50. (D1>D2).
  • the distance D ⁇ b>2 between the inner peripheral surface and the outer peripheral surface of the annular member 50 is the width of the annular member 50 .
  • the working gas is gradually boosted from low pressure to high pressure due to the geometric volume change of the compression chamber 2b formed by the fixed scroll 4 and the orbiting scroll 3.
  • the working gas introduced into the high-pressure gas atmosphere 6 from the discharge hole 45b is guided from the flow path 30c to the annular member upper space 51a via the second through flow path 17b.
  • the working gas is discharged outside from the discharge pipe 11 provided on the side surface of the container 1 through the small gap 17c and the first through-flow passage 17a while being affected by the rotation of the electric motor rotor 16a. .
  • the inside of the container 1 becomes a high-pressure gas atmosphere 6 during the flow of the working gas.
  • the intermediate-pressure working gas that is being compressed in the compression mechanism 2 temporarily communicates with the bleed hole 3e of the rocking base plate 3b and the gas introduction passage 14 due to its rocking motion, and the compliant frame lower space. 32b.
  • the intermediate pressure means a pressure higher than the suction pressure and lower than the discharge pressure.
  • the period of temporary communication is referred to as the intermediate pressure bleed interval.
  • the compliant frame lower space 32b is a space sealed by an upper annular seal member 36a and a lower annular seal member 36b. Therefore, the intermediate-pressure working gas introduced into the compliant frame lower space 32b floats the compliant frame 31 in the axial direction.
  • the intermediate pressure Pm1 in the intermediate pressure space 38 is a predetermined pressure ⁇ determined by the elastic force of the intermediate pressure adjusting spring 39c and the area exposed to the intermediate pressure of the intermediate pressure adjusting valve 39a, and the pressure Ps in the suction side space 8. is the sum of Ps+ ⁇ .
  • the intermediate pressure Pm2 of the compliant frame lower space 32b is the product of the pressure Ps of the suction side space 8 and the predetermined magnification ⁇ determined at the position of the communicating compression chamber 2b, which is Ps ⁇ .
  • the compliant frame 31 floats along the inner peripheral surface of the guide frame 30 in the axial direction due to the intermediate pressure Pm1, the intermediate pressure Pm2, and the high pressure from the high-pressure gas atmosphere 6 acting on the lower end surface 34 of the compliant frame 31.
  • the force to float is called pressing force.
  • the pressing force also floats the orbiting scroll 3 via the thrust surface 33, so that the gap between the tip of the fixed spiral body 4a forming the compression chamber 2b and the orbiting base plate 3b, and the tip of the orbiting spiral body 3a and The gap with the fixed base plate 4b is reduced. Therefore, the high-pressure working gas is less likely to leak from the compression chamber 2b, and a highly efficient compressor 100 can be obtained.
  • the pressure inside the compression chamber 2b becomes abnormally high during start-up or liquid compression, the axial gas load acting on the orbiting scroll 3 becomes excessive. In this case, the orbiting scroll 3 pushes down the compliant frame 31 via the thrust surface 33 .
  • the gap between the tip of the fixed spiral body 4a forming the compression chamber 2b and the rocking plate 3b and the gap between the tip of the rocking spiral body 3a and the fixed bed plate 4b become relatively large. Therefore, it is possible to obtain a highly reliable compressor 100 that suppresses an abnormal pressure rise in the compression chamber 2b and suppresses damage to the sliding portion.
  • oil flow Next, the flow of oil will be explained.
  • the oil reservoir space 5 is exposed to the high-pressure gas atmosphere 6 during the process of sucking, compressing, and discharging the working gas. Therefore, the oil in the oil sump space 5 is sucked up by the differential pressure due to the communication between the suction side space 8 of the compression mechanism 2 and the oil supply passage 23 of the drive shaft 19 .
  • the sucked oil is supplied to the main bearing 25, the bearing 27 and the rocking bearing 26 from the oil supply passage 23 and the supply passage 24a, respectively.
  • the oil supplied to the bearings 27 lubricates the bearings 27 and then returns to the oil reservoir space 5 below the container 1 by its own weight.
  • the oil supplied to the main bearing 25 is guided to the intermediate pressure space 38 after lubricating with the main shaft 20 .
  • the oil supplied to the boss portion 3c provided on the orbiting scroll 3 is depressurized through the orbiting bearing 26, becomes intermediate pressure, and is led to the intermediate pressure space 38.
  • the oil guided to the intermediate pressure space 38 passes through the intermediate through passage 39e, it overcomes the biasing force of the intermediate pressure regulating spring 39c, pushes up the intermediate pressure regulating valve 39a, and temporarily enters the compliant frame upper space 32a. Ejected. After that, the oil is discharged inside the Oldham ring 40 and supplied to the suction side space 8 .
  • the oil is supplied to the thrust surface 33 , then to the reciprocating sliding surface 41 , and flows into the suction side space 8 .
  • the oil that has flowed into the suction side space 8 is sucked into the compression mechanism portion 2 together with the low-pressure working gas.
  • the sucked oil seals and lubricates the gaps between the fixed scroll 4 and the orbiting scroll 3 that constitute the compression mechanism 2, thereby enabling the compressor 100 to operate normally.
  • the working gas flows through the downward slope portion 50a of the annular member 50 due to the swirling flow generated by the rotation of the drive shaft 19 and its own weight. It is led to the oil reservoir space 5 through the oil return gap 50c between. Since the working gas circulates in the oil reservoir space 5 and stays below the upward slope portion 50b of the annular member 50, it is possible to suppress the oil from scattering. Thus, the amount of oil discharged out of the container 1 can be reduced simply by providing the annular member 50 . Therefore, the amount of oil discharged out of the container 1 can be reduced while suppressing an increase in the number of parts.
  • FIG. 8 is a perspective view showing the action of the annular member 50 according to Embodiment 1 of the present disclosure.
  • Excess oil in the compression mechanism portion 2 is discharged from the compression mechanism portion 2 while being contained in the working gas, and guided to the annular member upper space 51a along the flow of the working gas.
  • the annular member upper space 51a is in a state in which a swirling flow is generated by the rotation of the electric motor rotor 16a.
  • the working gas is rectified at the descending slope portion 50a using the flow along the swirling flow and its own weight, and flows along the circumference of the annular member 50 from the oil return gap 50c to the oil sump space 5. led to.
  • the working gas circulates in the oil reservoir space 5 and stays below the ascending slope portion 50b. Therefore, it is possible to suppress the oil from splashing into the annular member upper space 51a.
  • the refrigerant escapes into the annular member upper space 51a, passes through the minute gap 17c and the first through-flow passage 17a, and is discharged to the outside from the discharge pipe 11 provided on the side surface of the container 1. .
  • the oil contained in the working gas actively returns to the oil reservoir space 5 while being separated from the working gas.
  • the distance D1 between the inner peripheral surface of the annular member 50 and the drive shaft 19 is greater than the distance D2 between the inner peripheral surface and the outer peripheral surface of the annular member 50 (D1>D2). Therefore, the oil in the oil sump space 5 is less likely to scatter while making it easier to rectify the swirling working gas.
  • the oil contained in the working gas can be actively returned to the oil reservoir space 5 while separating the working gas from the oil. Therefore, depletion of oil in the oil reservoir space 5 can be suppressed, and the reliability of the sliding portion and the sealing performance of the compression mechanism portion 2 can be ensured.
  • FIG. 9 is a perspective view showing annular member 150 according to Embodiment 2 of the present disclosure
  • FIG. 10 is a side view showing annular member 150 according to Embodiment 2 of the present disclosure.
  • the second embodiment differs from the first embodiment in the shape of the annular member 150 .
  • the same reference numerals are given to the parts that are common to the first embodiment, and the description thereof is omitted.
  • the annular member 150 has a fixed portion 152, a downward slope portion 150a, and an upward slope portion 150b.
  • the fixed portion 152 is a plate-like member and is used to be fixed to the fixed leg portion 37 a of the frame 37 .
  • a fixing hole 152a is formed in the fixing portion 152, and a fastener (not shown) is inserted into the fixing hole 152a and fixed to the fixing leg portion 37a.
  • two fixing portions 152 are provided, and the two fixing portions 152 are positioned at the same height and positioned diagonally to each other.
  • the downward slope portion 150 a slopes downward along the rotation direction of the drive shaft 19 .
  • the descending slope portion 150a is a member that descends substantially vertically from the upper end portion of the ascending slope portion 150b to the fixing portion 152 in the vertical direction.
  • two descending slope portions 150a are provided, and the two descending slope portions 150a are positioned diagonally to each other.
  • the ascending slope portion 150b is inclined upward from the lower end portion of the descending slope portion 150a and the fixed portion 152 along the rotation direction of the drive shaft 19 to rectify the working gas.
  • the ascending slope portion 150b slopes upward gradually from the fixed portion 152 to the upper end of the descending slope portion 150a.
  • an oil return gap 150c through which oil returns.
  • two upslope portions 150b are provided, and the two upslope portions 150b are positioned diagonally to each other.
  • the annular member 150 is connected along the rotational direction of the drive shaft 19 in the order of the fixed portion 152, the upward slope portion 150b, the downward slope portion 150a, the fixed portion 152, the upward slope portion 150b, and the downward slope portion 150a. ing. Further, as shown in FIG. 9, the distance D1 between the inner peripheral surface of the annular member 150 and the drive shaft 19 is greater than the distance D2 between the inner peripheral surface and the outer peripheral surface of the annular member 150 (D1> D2). Here, the distance D ⁇ b>2 between the inner peripheral surface and the outer peripheral surface of the annular member 150 is the width of the annular member 150 .
  • FIG. 11 is a perspective view showing the action of the annular member 150 according to Embodiment 2 of the present disclosure.
  • the working gas is rectified on the upward slope portion 150b using the flow along the swirling flow and its own weight, and flows along the circumference of the annular member 150 from the oil return gap 150c to the oil sump space 5. led to.
  • the working gas circulates in the oil reservoir space 5 and stays below the ascending slope portion 150b. Therefore, it is possible to suppress the oil from splashing into the annular member upper space 51a.
  • the refrigerant After being separated from the oil, the refrigerant escapes into the annular member upper space 51a, passes through the minute gap 17c and the first through-flow passage 17a, and is discharged to the outside from the discharge pipe 11 provided on the side surface of the container 1. .
  • the oil contained in the working gas actively returns to the oil reservoir space 5 while being separated from the working gas.
  • the distance D1 between the inner peripheral surface of the annular member 150 and the drive shaft 19 is greater than the distance D2 between the inner peripheral surface and the outer peripheral surface of the annular member 150 (D1>D2). Therefore, the oil in the oil sump space 5 is less likely to scatter while making it easier to rectify the swirling working gas.

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

Abstract

La présente invention concerne un compresseur (100) comprenant : un contenant (1) qui forme un contour et est formé de telle sorte qu'un espace de stockage d'huile pour stocker de l'huile est formé dans sa section inférieure intérieure ; un moteur électrique (16) qui est disposé à l'intérieur du contenant ; un arbre d'entraînement (19) qui est disposé sur le moteur électrique et transmet la force de rotation du moteur électrique ; une unité de mécanisme de compression (2) qui se met en rotation en accompagnant la rotation de l'arbre d'entraînement et comprime un gaz fonctionnel ; des paliers d'arbre (25, 27) qui sont disposés dans le contenant et supportent de manière rotative l'arbre d'entraînement ; un cadre (37) qui est disposé au-dessus de l'espace de stockage d'huile du contenant et supporte les paliers d'arbre ; et un élément annulaire (50) qui est disposé sur une partie supérieure du cadre et est disposé le long de la surface périphérique interne du contenant centré autour de l'arbre d'entraînement. L'élément annulaire présente une partie inclinée vers le bas (50a) qui s'incline vers le bas le long de la direction de rotation de l'arbre d'entraînement, et une partie inclinée vers le haut (50b) qui est inclinée vers le haut à partir de la partie inclinée vers le bas dans la direction de rotation de l'arbre d'entraînement et forme un espace de retour d'huile (50c) à travers lequel l'huile retourne entre la partie inclinée vers le haut et le cadre.
PCT/JP2022/004176 2022-02-03 2022-02-03 Compresseur et dispositif à cycle de réfrigération WO2023148867A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/004176 WO2023148867A1 (fr) 2022-02-03 2022-02-03 Compresseur et dispositif à cycle de réfrigération

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/004176 WO2023148867A1 (fr) 2022-02-03 2022-02-03 Compresseur et dispositif à cycle de réfrigération

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20060120386A (ko) * 2005-05-19 2006-11-27 엘지전자 주식회사 스크롤 압축기의 유분리 장치
JP2013217281A (ja) * 2012-04-09 2013-10-24 Mitsubishi Electric Corp ロータリー式圧縮機
WO2016084121A1 (fr) * 2014-11-25 2016-06-02 三菱電機株式会社 Compresseur

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20060120386A (ko) * 2005-05-19 2006-11-27 엘지전자 주식회사 스크롤 압축기의 유분리 장치
JP2013217281A (ja) * 2012-04-09 2013-10-24 Mitsubishi Electric Corp ロータリー式圧縮機
WO2016084121A1 (fr) * 2014-11-25 2016-06-02 三菱電機株式会社 Compresseur

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