WO2021039573A1 - Compresseur et dispositif à cycle de réfrigération - Google Patents

Compresseur et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2021039573A1
WO2021039573A1 PCT/JP2020/031424 JP2020031424W WO2021039573A1 WO 2021039573 A1 WO2021039573 A1 WO 2021039573A1 JP 2020031424 W JP2020031424 W JP 2020031424W WO 2021039573 A1 WO2021039573 A1 WO 2021039573A1
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WIPO (PCT)
Prior art keywords
compressor
refrigerant
compression mechanism
winding
stator
Prior art date
Application number
PCT/JP2020/031424
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English (en)
Japanese (ja)
Inventor
平山　卓也
圭一 石田
Original Assignee
東芝キヤリア株式会社
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.)
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Application filed by 東芝キヤリア株式会社 filed Critical 東芝キヤリア株式会社
Priority to CN202080046398.6A priority Critical patent/CN114026329B/zh
Priority to JP2021542805A priority patent/JP7344969B2/ja
Publication of WO2021039573A1 publication Critical patent/WO2021039573A1/fr

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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
    • 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
    • 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
    • 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
    • F04C23/001—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 of similar working principle
    • 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
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • 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
    • F04C29/06—Silencing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type

Definitions

  • a compressor equipped with a compression unit and an open winding type motor for driving the compression unit is known.
  • the open winding type motor can output high torque with a smaller current than a motor in which power is supplied from only one end of the winding, for example, a delta connection type motor or a Y connection type motor.
  • a motor in which power is supplied from only one end of the winding for example, a delta connection type motor or a Y connection type motor.
  • a compressor driven by an open winding type motor has a higher torque output and suppresses the temperature rise of the winding than a compressor driven by a motor in which power is supplied from only one end of the winding. , Are compatible.
  • a refrigerant containing R32 refrigerant or a mixed refrigerant having a steam pressure of 2 megapascals or more at a saturated vapor temperature of 50 degrees Celsius is a refrigerant in which the temperature of the discharged refrigerant gas after compression is high. Belongs to. This high temperature discharged refrigerant gas heats the windings of the motor.
  • the present invention can be applied to the compression of an R32 refrigerant or a mixed refrigerant containing an R32 refrigerant in which the vapor pressure at a saturated vapor temperature of 50 degrees Celsius (° C.) is 2 megapascals (MPa) or more. It is an object of the present invention to provide a compressor capable of preventing overheating of the winding of an open winding type motor, and a refrigeration cycle device.
  • the compressor according to the embodiment of the present invention is a closed container and a mixed refrigerant containing an R32 refrigerant and an R32 refrigerant contained in the closed container and introduced into the closed container.
  • a compression mechanism that compresses at least one of the refrigerants whose steam pressure is 2 megapascals or more at a saturated steam temperature of 50 degrees Celsius (° C.), and a tubular stator fixed to the inner surface of the closed container.
  • an open winding type motor having a rotor which is arranged inside the stator and drives the compression mechanism portion to rotate, and the outermost diameter dimension of the stator is set to D meter (m).
  • the thickness of the iron core of the stator is T meters (m)
  • the volume of the compression chamber at the start of compression in the compression mechanism is V cubic meters (m 3 )
  • the circumference ratio is ⁇ , 14 It has a relationship of ⁇ ( ⁇ ⁇ D 2 ⁇ 4) ⁇ T ⁇ V ⁇ 21.
  • the stator of the compressor according to the embodiment of the present invention includes a tooth provided inside the iron core and a winding wound centrally wound around the tooth.
  • the closed container of the compressor according to the embodiment of the present invention is a vertically placed cylindrical type, has a discharge port for the compressed refrigerant at the top thereof, and the motor is arranged above the compression mechanism portion.
  • the height from the upper end surface of the iron core to the top of the inner surface of the closed container is preferably larger than the thickness of the iron core.
  • the maximum load torque generated while the crank angle of the compression mechanism unit advances 360 degrees during steady operation is Tmax Newton meter (Nm), and the minimum load torque is Tmin Newton.
  • Tmax Newton meter (Nm) and the average load torque are Tmean Newton meters (Nm)
  • Tmean Newton meters (Nm) it is preferable that (Tmax-Tmin) ⁇ Tmean ⁇ 0.5.
  • the compression mechanism portion of the compressor according to the embodiment of the present invention is preferably a rotary type having three or more cylinders.
  • the refrigeration cycle device connects the compressor, the radiator, the expander, the heat absorber, the compressor, the radiator, the expander, and the heat absorber. It is equipped with a refrigerant pipe for circulating the refrigerant.
  • the present invention can be applied to the compression of an R32 refrigerant or a mixed refrigerant containing an R32 refrigerant in which the vapor pressure at a saturated vapor temperature of 50 ° C. (° C.) is 2 megapascals (MPa) or more. It is also possible to provide a compressor and a refrigeration cycle device capable of preventing overheating of the winding of an open winding type motor.
  • FIG. 1 is a schematic view of a refrigeration cycle device and a compressor according to an embodiment of the present invention.
  • the refrigeration cycle device 1 is, for example, an air conditioner.
  • the refrigerant used in the refrigeration cycle apparatus 1 is a single refrigerant of difluoromethane (Difluoromethane, HFC-32, R32, hereinafter referred to as “R32 refrigerant”) or a mixed refrigerant containing R32, and has a saturated steam temperature. It is a refrigerant in which the pressure of steam at 50 degrees Celsius (° C.) is 2 megapascals (MPa) or more.
  • the mixed refrigerant is, for example, R410A, R446A, R448A, R449A, R454B, R459A, R463A, R466A.
  • the single refrigerant of R32 and the mixed refrigerant containing R32 are simply referred to as "refrigerants”.
  • the compressor 2 sucks in the refrigerant that has passed through the heat absorber 6 through the refrigerant pipe 8, compresses it, and discharges the high-temperature and high-pressure refrigerant through the refrigerant pipe 8 to the radiator 3.
  • a discharge pipe 8a for discharging the refrigerant is connected to the end plate 11b on the upper side of the closed container 11.
  • the discharge pipe 8a is connected to the refrigerant pipe 8.
  • the end plate 11b on the upper side of the airtight container 11 is provided with two airtight terminal portions 18 for supplying electric power.
  • the electric motor 12 generates a driving force for rotating the compression mechanism unit 13.
  • the electric motor 12 is arranged above the compression mechanism unit 13.
  • the electric motor 12 is sealed by being pulled out from the stator 21 and a tubular stator 21 fixed to the inner surface of the closed container 11, a rotor 22 arranged inside the stator 21 to rotationally drive the compression mechanism portion 13. It includes a plurality of outlet wires 23 connected to the terminal portion 18.
  • the rotor 22 includes a rotor core 25 having a magnet accommodating hole (not shown) and a permanent magnet accommodated in the magnet accommodating hole.
  • the rotor 22 is fixed to the rotating shaft 15.
  • the rotation center line C of the rotor 22 and the rotation shaft 15 substantially coincides with the center line of the stator 21.
  • the plurality of outlet wires 23 are wirings that supply electric power to the stator 21 through the sealed terminal portion 18, and are so-called lead wires.
  • a plurality of outlet wires 23 are wired according to the type of the electric motor 12. In this embodiment, six outlet wires 23 are wired.
  • the rotating shaft 15 connects the electric motor 12 and the compression mechanism unit 13.
  • the rotating shaft 15 transmits the rotational driving force generated by the electric motor 12 to the compression mechanism unit 13.
  • the intermediate portion 15a of the rotating shaft 15 connects the electric motor 12 and the compression mechanism portion 13 and is rotatably supported by the main bearing 16.
  • the lower end portion 15b of the rotating shaft 15 is rotatably supported by the auxiliary bearing 17.
  • the main bearing 16 and the auxiliary bearing 17 are also a part of the compression mechanism portion 13. In other words, the rotating shaft 15 penetrates the compression mechanism portion 13.
  • the rotating shaft 15 is provided with a plurality of eccentric portions 26 between the intermediate portion 15a supported by the main bearing 16 and the lower end portion 15b supported by the auxiliary bearing 17.
  • Each eccentric portion 26 is a disk or a cylinder having a center that does not match the rotation center line of the rotation axis 15 and has a parallel center.
  • the compression mechanism unit 13 compresses the refrigerant, that is, a single refrigerant or a mixed refrigerant.
  • the compression mechanism unit 13 sucks the gaseous refrigerant from the refrigerant pipe 8 to compress it, and discharges it into the closed container 11.
  • the compression mechanism unit 13 is a rotary type having a plurality of, for example, three cylinders.
  • the compression mechanism unit 13 includes a plurality of cylinders 32 each having a circular cylinder chamber 31, and a plurality of annular rollers 33 arranged in the respective cylinder chambers 31.
  • the cylinder 32 closest to the electric motor 12 is the first cylinder 32A
  • the cylinder 32 farthest from the electric motor 12 is the third cylinder 32C
  • the cylinder 32 arranged between the first cylinder 32A and the third cylinder 32C is the second cylinder. It is set to 32B.
  • the upper surface of the first cylinder 32A is closed by the main bearing 16.
  • the lower surface of the first cylinder 32A is closed by the first partition plate 35A.
  • the upper surface of the second cylinder 32B is closed by the first partition plate 35A.
  • the lower surface of the second cylinder 32B is closed by the second partition plate 35B.
  • the upper surface of the third cylinder 32C is closed by the second partition plate 35B.
  • the lower surface of the third cylinder 32C is closed by the auxiliary bearing 17.
  • the main bearing 16 is fixed to the first cylinder 32A by a fastening member (not shown) such as a bolt.
  • the main bearing 16 is provided with a discharge valve mechanism 16a that discharges the compressed refrigerant in the cylinder chamber 31 of the first cylinder 32A, and a first discharge muffler 38A that covers the discharge valve mechanism 16a.
  • the first partition plate 35A is provided with a discharge valve mechanism 35C for discharging the compressed refrigerant in the cylinder chamber 31 of the second cylinder 32B, and a discharge chamber 35D.
  • the main bearing 16, the first cylinder 32A, and the first partition plate 35A have holes (not shown) that connect the discharge chamber 35D into the first discharge muffler 38A.
  • the discharge valve mechanism 16a When the pressure difference between the pressure in the cylinder chamber 31 of the first cylinder 32A and the pressure in the first discharge muffler 38A reaches a predetermined value due to the compression action of the compression mechanism unit 13, the discharge valve mechanism 16a has a discharge port ( The compressed refrigerant is discharged into the first discharge muffler 38A by opening (not shown).
  • the discharge valve mechanism 35C opens the discharge port when the pressure difference between the pressure in the cylinder chamber 31 of the second cylinder 32B and the pressure in the discharge chamber 35D reaches a predetermined value due to the compression action of the compression mechanism unit 13. Then, the compressed refrigerant is discharged into the discharge chamber 35D.
  • the first discharge muffler 38A has a discharge hole (not shown) that connects the inside and outside of the first discharge muffler 38A.
  • the compressed refrigerant discharged into the first discharge muffler 38A is discharged into the closed container 11 through the discharge holes.
  • the first cylinder 32A is fixed to the closed container 11 by welding at a plurality of places, for example, to a frame fixed by spot welding with bolts 37.
  • the auxiliary bearing 17 is fixed to the third cylinder 32C by a fastening member (not shown) such as a bolt.
  • the auxiliary bearing 17 is provided with a discharge valve mechanism 17a that discharges the compressed refrigerant in the cylinder chamber 31 of the third cylinder 32C, and a second discharge muffler 38B that covers the discharge valve mechanism.
  • the discharge valve mechanism 17a has a discharge port (a discharge port (17a) when the pressure difference between the pressure in the cylinder chamber 31 of the third cylinder 32C and the pressure in the second discharge muffler 38B reaches a predetermined value due to the compression action of the compression mechanism unit 13.
  • the compressed refrigerant is discharged into the second discharge muffler 38B by opening (not shown).
  • the space in the second discharge muffler 38B is connected to the space in the first discharge muffler 38A through a passage (not shown).
  • the refrigerant compressed in the cylinder chamber 31 of the third cylinder 32C and discharged into the second discharge muffler 38B is discharged into the closed container 11 through the space in the first discharge muffler 38A.
  • the suction pipe 39 penetrates the closed container 11 and is connected to the cylinder chamber 31 of the cylinder 32.
  • the cylinder 32 has a suction hole that is connected to the suction pipe 39 and reaches the cylinder chamber 31.
  • the first suction pipe 39A is connected to the cylinder chamber 31 of the first cylinder 32A.
  • the second suction pipe 39B passes through the second partition plate 35B, branches at the second partition plate 35B, and is connected to the cylinder chamber 31 of the second cylinder 32B and the cylinder chamber 31 of the third cylinder 32C.
  • the second partition plate 35B has a branching refrigerant passage (not shown).
  • the lower part of the closed container 11 is filled with the lubricating oil 41. Most of the compression mechanism portion 13 is immersed in the lubricating oil 41 in the closed container 11.
  • the accumulator 7 prevents the liquid refrigerant that could not be completely gasified by the heat absorber 6 from being sucked into the compressor 2.
  • FIG. 2 is a plan view of the cylinder of the compressor according to the embodiment of the present invention.
  • first cylinder 32A Since the first cylinder 32A, the second cylinder 32B, and the third cylinder 32C have the same structure, one cylinder 32 will be described.
  • the compressor 2 includes a blade 45 that reciprocates in contact with the outer peripheral surface of the roller 33.
  • the blade 45 divides the inside of the cylinder chamber 31 into a suction chamber 46 and a compression chamber 47.
  • the suction chamber 46 is a portion connected to a suction hole 48 provided in the cylinder 32.
  • the compression chamber 47 is connected to the first discharge muffler 38A or the second discharge muffler 38B.
  • the cylinder chamber 31 is a space inside the cylinder 32.
  • the cylinder chamber 31 accommodates an eccentric portion 26 of the rotating shaft 15.
  • the roller 33 is fitted to the peripheral surface of the eccentric portion 26.
  • the outer peripheral surface of the roller 33 is in line contact with the inner peripheral surface of the cylinder chamber 31.
  • the roller 33 moves eccentrically with the rotation of the rotating shaft 15 while making the outer peripheral surface of the roller 33 in line contact with the inner peripheral surface of the cylinder chamber 31.
  • the contact between the roller 33 and the cylinder 32 is not a direct contact but an indirect one with an oil film (not shown) of the lubricating oil 41 interposed therebetween, but for convenience of explanation, these oil films are used.
  • the contact made is simply expressed as "contact”.
  • stator 21 of the electric motor 12 will be described.
  • FIG. 3 is a diagram showing the stator of the electric motor of the compressor according to the embodiment of the present invention from the direction of the center line of the rotation axis.
  • the outlet wire 23 of the winding 58W is also connected to the W phase of the first inverter circuit 62 and the W phase of the second inverter circuit 63, similarly to the U-phase outlet wire 23.
  • One outlet wire 23 of the W phase is connected to the W phase of the first inverter circuit 62 of the drive circuit 61 of the electric motor 12 via one of the two sealed terminal portions 18.
  • the other outlet wire 23 of the W phase is connected to the W phase of the second inverter circuit 63 of the drive circuit of the electric motor 12 via the other of the two sealed terminal portions 18.
  • the volume Vc of each cylinder does not necessarily have to be the same volume.
  • the compression mechanism unit 13 may include at least one cylinder 32.
  • the number of cylinders N according to this embodiment is 3.
  • the total volume Vct is also referred to as the exclusion volume of the compression mechanism unit 13.
  • the dimensionless number obtained by dividing the apparent volume Vm of the electric motor 12 by the exclusion volume Vct of the compression mechanism unit 13 is defined as the volume ratio R.
  • FIG. 4 is a diagram showing the relationship between the apparent volume of the electric motor and the total volume of the compression chamber of the compressor according to the embodiment of the present invention.
  • the horizontal axis of FIG. 4 shows the volume ratio R, and the vertical axis of FIG. 4 shows the temperature of the winding of the open winding type motor 12.
  • the double wire AT in FIG. 4 indicates the allowable temperature AT of the winding of the open winding type motor 12.
  • the winding of the open winding type motor 12 functions soundly if the allowable temperature is AT or less.
  • the permissible temperature AT is set in consideration of the heat resistant surface of the winding and the efficiency surface of the motor 12.
  • the permissible temperature AT is set to, for example, 125 degrees Celsius (° C.).
  • the solid line ⁇ in FIG. 4 shows the volume ratio R of the open winding motor 12 and the winding temperature of the open winding motor 12 of the compressor 2 during operation, which is exposed to the high temperature refrigerant gas compressed by the compressor 2. And, the relationship is shown.
  • the solid line ⁇ is the temperature of the winding during steady operation when the compressor 2 is operated with an AC power supply having an AC voltage of 200 volts (V).
  • the winding temperature decreases as the volume ratio R increases.
  • the volume Vm of the electric motor 12 per compressive load increases as the volume ratio R increases.
  • Increasing the volume Vm of the motor 12 per compressive load improves the efficiency of the motor 12 and increases the heat dissipation area of the motor 12. Then, the temperature of the winding is lowered.
  • the broken line ⁇ in FIG. 4 indicates a volume ratio R in a compressor including a motor in which power is supplied from only one end of the winding, and an operation in which the compressor is exposed to a high-temperature refrigerant gas compressed by the compressor.
  • the relationship with the temperature of the winding of the motor of the compressor inside is shown.
  • the broken line ⁇ is the temperature of the winding during steady operation when operating a compressor equipped with a motor in which power is supplied from only one end of the winding with an AC power supply having an AC voltage of 200 volts (V). ..
  • the temperature of the winding decreases as the volume ratio R increases.
  • the intercept on the vertical axis of the broken line ⁇ is higher than the intercept on the vertical axis of the solid line ⁇ . That is, the broken line ⁇ is biased upward in FIG. 4 from the solid line ⁇ . Further, the broken line ⁇ does not intersect the solid line ⁇ .
  • the volume ratio R is 21 or more
  • the winding temperature drops below the allowable temperature AT
  • the volume ratio R is smaller than 21, the winding temperature exceeds the allowable temperature AT.
  • the electric motor 12 is driven by a plurality of inverter circuits (first inverter circuit 62, second inverter circuit 63). Therefore, the power loss in the drive circuit 61 increases as compared with the motor in which the power is supplied from only one end of the winding. That is, in the range of (volume ratio R)> 21, both the motor and the motor 12 to which power is supplied from only one end of the winding keep the winding temperature within the allowable temperature AT or less. Therefore, the motor in which the electric power is supplied from only one end of the winding is superior to the electric motor 12 in terms of efficiency.
  • the compressor 2 has the relationship of the following equation.
  • torque volatility Tr is determined by the following formula.
  • the load torque acting on the electric motor 12 is T Newton meter (Nm)
  • the maximum load torque acting on the electric motor 12 is Tmax Newton meter (Nm)
  • the minimum load torque acting on the electric motor 12 is Tmin Newton meter. Let it be metric (Nm) and let the average load torque acting on the electric motor 12 be Tmean Newton meter (Nm).
  • the solid line ⁇ in FIG. 5 shows the relationship between the crank angle ⁇ and the torque fluctuation Tf in the 3-cylinder rotary compressor 2.
  • the torque volatility Tr on the solid line ⁇ is 0.25 (dimensionless number).
  • the three-cylinder rotary compressor 2 has a range of 0 degrees ⁇ crank angle ⁇ ⁇ 360 degrees, that is, three maximum values in the compression stroke of the three cylinders 32 during one rotation of the rotating shaft 15.
  • the broken line ⁇ in FIG. 5 shows the relationship between the crank angle ⁇ and the torque volatility Tr in the two-cylinder rotary compressor 2.
  • the torque volatility Tr on the broken line ⁇ is 0.79 (dimensionless number).
  • the two-cylinder rotary compressor 2 has two maximum values in the compression stroke of the two cylinders 32 while the rotating shaft 15 makes one rotation.
  • the 2-cylinder rotary compressor 2 is inferior to the 3-cylinder rotary compressor 2 in terms of torque volatility Tr, maximum value, and minimum value.
  • the double line ⁇ in FIG. 5 shows the relationship between the crank angle ⁇ and the torque volatility Tr in the one-cylinder scroll type compressor 2.
  • the torque volatility Tr on the double line ⁇ is 0.25 (dimensionless number).
  • the one-cylinder scroll type compressor 2 has one maximum value in the compression stroke of the scroll type cylinder 32 while the rotation shaft 15 makes one rotation.
  • the 1-cylinder scroll type compressor 2 has the same characteristics as the 3-cylinder rotary type compressor 2 in terms of torque volatility Tr, maximum value, and minimum value.
  • FIG. 6 is a diagram showing the relationship between the torque fluctuation rate of the compressor according to the embodiment of the present invention and the amplitude of vibration in the rotation direction of the rotating shaft.
  • the horizontal axis of FIG. 6 shows the torque fluctuation rate shown in [Equation 7], and the vertical axis shows the amplitude of vibration in the rotation direction of the rotation shaft 15.
  • the unit of amplitude is micrometer ( ⁇ m). This vibration amplitude is generated by the operation of the compression mechanism unit 13. Further, this vibration amplitude is evaluated at the connection portion 65 (FIG. 1) between the accumulator 7 and the refrigerant pipe 8 in which the vibration response is remarkably exhibited.
  • the solid line ⁇ in FIG. 6 shows the relationship between the torque volatility and the amplitude of vibration in the rotation direction of the rotating shaft 15. There is a positive correlation between the torque volatility and the amplitude of vibration in the direction of rotation of the rotating shaft 15.
  • the solid line ⁇ is the temperature of the winding during steady operation when the compressor 2 satisfying the relationship of [Equation 4] is operated by an AC power source having an AC voltage of 200 volts (V).
  • the number of rotations of the electric motor 12 at this time is 30 times per second (revolutions per second, rps).
  • the maximum amplitude should be suppressed to 50 micrometers ( ⁇ m) or less in consideration of mechanical soundness such as fatigue fracture at the relevant portion.
  • the double line AA in FIG. 6 shows the allowable amplitude AA at the connecting portion 65.
  • the torque volatility Tr is preferably 0.5 or less as shown in the following equation.
  • the volume Vm of the electric motor 12 with respect to the load torque is smaller than that of a general compressor. That is, the moment of inertia of the rotor 22 is small, and the vibration of the compression mechanism portion 13 in the rotation direction tends to be large. Therefore, if the torque volatility Tr becomes larger than 0.5, the vibration amplitude at the connection portion 65, which is the evaluation point of the vibration amplitude, becomes larger than the permissible amplitude AA under the operating condition drawing the solid line ⁇ . In such a case, in the operation control of the electric motor 12, there is a method of performing torque control to reduce the load torque and reduce the vibration amplitude. In torque control, the motor torque is changed according to the load torque by changing the supply voltage to the electric motor 12 while the rotating shaft 15 is rotating. As a result, the difference between the motor torque and the load torque becomes small, and the exciting force decreases.
  • first inverter circuit 62 when torque control is performed by the compressor 2 provided with the open winding type motor 12, there are a plurality of inverter circuits (first inverter circuit 62, second inverter circuit 63) having a plurality of power losses for adjusting the motor torque to the load torque. ) Occurs. That is, when torque control is performed by the compressor 2 provided with the open winding type motor 12, the power loss in the drive circuit 61 increases as compared with the motor in which power is supplied from only one end of the winding. It ends up.
  • the compressor 2 according to the present embodiment satisfies the condition of [Equation 8], omits torque control, and suppresses deterioration in performance.
  • the compressor 2 and the refrigeration cycle device 1 have a relationship represented by [Equation 4], that is, 14 ⁇ (volume ratio R) ⁇ 21. Therefore, the compressor 2 and the refrigeration cycle device 1 are used to compress the R32 refrigerant or the mixed refrigerant containing the R32 refrigerant whose steam pressure at a saturated steam temperature of 50 ° C. is 2 megapascals (MPa) or more. Even when a high torque output is required for the electric motor 12, it is possible to suppress an increase in the current flowing through the winding 58 and avoid overheating of the winding 58.
  • the compressor 2 and the refrigeration cycle device 1 include a winding 58 that is wound by a centralized winding method. Therefore, the compressor 2 and the refrigeration cycle device 1 can shorten the peripheral length of the winding 58 to suppress the winding resistance. This suppression of winding resistance contributes to prevention of overheating of the winding 58.
  • the compressor 2 and the refrigeration cycle device 1 have a relationship represented by [Equation 5]. That is, the height from the upper end surface of the stator core 53 to the top of the inner surface of the closed container 11 is larger than the thickness dimension of the stator core 53. Therefore, the compressor 2 and the refrigeration cycle device 1 provide a space above the electric motor 12 to accommodate the six outlet wires 23 connected to both ends of the winding 58 of the open winding motor 12. It has a space above the electric motor 12 to install the two sealed terminal portions 18. Further, even if the oil contained in the compressed refrigerant gas adheres to the outlet wire 23 and the sealed terminal portion 18, the amount of oil flowing out from the space above the electric motor 12 to the discharge pipe 8a can be reduced.
  • the compressor 2 and the refrigeration cycle device 1 have a relationship represented by [Equation 8], that is, (torque volatility Tr) ⁇ 0.5. Therefore, the compressor 2 and the refrigeration cycle device 1 can omit the torque control and suppress the deterioration of the performance.
  • the refrigeration cycle device 1 and the compressor 2 according to the present embodiment, it is applicable to the compression of the R32 refrigerant or the mixed refrigerant containing the R32 refrigerant, and the winding 58 of the open winding type motor 12 is overheated. Can be prevented.
  • Refrigeration cycle device 2 ... Compressor, 3 ... Dissipator, 5 ... Expansion device, 6 ... Heat absorber, 7 ... Accumulator, 8 ... Refrigerator pipe, 8a ... Discharge pipe, 11 ... Sealed container, 11a ... Body , 11b ... upper end plate, 11c ... lower end plate, 12 ... open winding type motor (electric motor), 13 ... compression mechanism, 15 ... rotating shaft, 15a ... intermediate part, 15b ... lower end part, 16 ... main bearing, 17 ... Sub-bearing, 18 ... Sealed terminal, 21 ... Stator, 22 ... Rotor, 23 ... Mouth wire, 25 ... Rotor iron core, 26 ... Eccentric part, 31 ...
  • Second insulated end plate 58 ... Winding, 58U ... U phase winding, 58V ... V phase winding , 58W ... W phase winding, 59 ... slot, 61 ... drive circuit, 62 ... first inverter circuit, 63 ... second inverter circuit, 65 ... connection part.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un compresseur et un dispositif à cycle de réfrigération qui sont applicables à la compression d'un réfrigérant R32 ou d'un réfrigérant mélangé contenant le réfrigérant R32, et permettent d'empêcher une surchauffe des enroulements dans un moteur de type à enroulement ouvert. L'invention concerne également un compresseur (2) pourvu d'un récipient hermétiquement scellé (11), d'une unité mécanisme de compression (31) qui est logée dans le récipient hermétiquement fermé (11) et est capable de comprimer un réfrigérant R32 ou un réfrigérant mélangé contenant le réfrigérant R32 introduit dans le récipient hermétiquement scellé (11), et d'un moteur électrique de type à enroulement ouvert (12) comprenant un stator tubulaire (21) fixé à une surface interne du récipient hermétiquement scellé (11), et un rotor (22) qui est disposé à l'intérieur du stator (21) pour entraîner en rotation l'unité mécanisme de compression (13) ; si la dimension du diamètre extérieur maximal du stator (21) est de D mètres (m), l'épaisseur d'un noyau de stator (53) du stator (21) est de T mètres (m), le volume d'une chambre de compression (47) au début de la compression par l'unité mécanisme de compression (13) est de V mètres cubes (m3), et le rapport de la circonférence d'un cercle sur le diamètre de celui-ci est π, la relation 14≤(π×D2÷4)×T÷V≤ 21 est satisfaite.
PCT/JP2020/031424 2019-08-23 2020-08-20 Compresseur et dispositif à cycle de réfrigération WO2021039573A1 (fr)

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JP2021542805A JP7344969B2 (ja) 2019-08-23 2020-08-20 圧縮機、および冷凍サイクル装置

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009047063A (ja) * 2007-08-20 2009-03-05 Sanyo Electric Co Ltd 密閉式電動圧縮機
JP2012197693A (ja) * 2011-03-18 2012-10-18 Daikin Industries Ltd 回転式圧縮機
JP2015211603A (ja) * 2014-04-30 2015-11-24 三菱電機株式会社 電動機、密閉型圧縮機及び冷凍サイクル装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015063871A1 (fr) * 2013-10-29 2015-05-07 三菱電機株式会社 Moteur électrique encastré à aimant permanent, compresseur et dispositif de réfrigération et de climatisation
CN204578237U (zh) * 2014-04-30 2015-08-19 三菱电机株式会社 电动机、密闭型压缩机以及制冷循环装置
JP6703921B2 (ja) * 2016-09-14 2020-06-03 東芝キヤリア株式会社 回転式圧縮機及び冷凍サイクル装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009047063A (ja) * 2007-08-20 2009-03-05 Sanyo Electric Co Ltd 密閉式電動圧縮機
JP2012197693A (ja) * 2011-03-18 2012-10-18 Daikin Industries Ltd 回転式圧縮機
JP2015211603A (ja) * 2014-04-30 2015-11-24 三菱電機株式会社 電動機、密閉型圧縮機及び冷凍サイクル装置

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