WO2018142564A1 - 圧縮機 - Google Patents

圧縮機 Download PDF

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Publication number
WO2018142564A1
WO2018142564A1 PCT/JP2017/003915 JP2017003915W WO2018142564A1 WO 2018142564 A1 WO2018142564 A1 WO 2018142564A1 JP 2017003915 W JP2017003915 W JP 2017003915W WO 2018142564 A1 WO2018142564 A1 WO 2018142564A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
bearing
shaft
compressor
main bearing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2017/003915
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
亮 濱田
幹一朗 杉浦
貴也 木本
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2017/003915 priority Critical patent/WO2018142564A1/ja
Priority to CZ2019-487A priority patent/CZ309104B6/cs
Priority to CN201780079272.7A priority patent/CN110249132A/zh
Priority to JP2018565189A priority patent/JPWO2018142564A1/ja
Priority to KR1020197015921A priority patent/KR102204713B1/ko
Publication of WO2018142564A1 publication Critical patent/WO2018142564A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/605—Shaft sleeves or details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/60—Shafts

Definitions

  • the present invention relates to a compressor that compresses and discharges a refrigerant.
  • Hydrofluoroolefin has a lower GWP (global warming potential) than R410A refrigerant or R32 refrigerant conventionally used as a refrigerant, and is a promising refrigerant as a refrigerant used for measures against global warming.
  • GWP global warming potential
  • hydrofluoroolefins or hydrocarbons have a lower GWP than conventional R410 or R32 refrigerants, and are promising refrigerants used as countermeasures against global warming.
  • R1123 refrigerant which is one of hydrofluoroolefins, is less stable than conventional refrigerants such as R32 refrigerant or R410A refrigerant, and releases large heat due to disproportionation reaction. May cause the reliability of the compressor and the refrigeration cycle apparatus to be lowered.
  • R1123 refrigerant is a refrigerant that is used in a higher pressure state than conventional refrigerants such as R32 refrigerant or R410A refrigerant, and is particularly uneven due to heat generated by seizure between the rotating shaft and the bearing of the compression mechanism portion of the compressor. May cause chemical reaction.
  • the present invention has been made to solve the above-described problems, and provides a compressor that suppresses seizure between the rotating shaft and the bearing of the compressor and suppresses the disproportionation reaction of the R1123 refrigerant. .
  • a compressor according to the present invention includes a hermetic container, and a compression mechanism unit that is accommodated in the hermetic container and compresses a refrigerant flowing into the hermetic container.
  • the compression mechanism unit includes a rotating shaft, a main bearing, and a bearing, the distance between the center axis F of the center axis E and the auxiliary bearing of the main bearing concentricity R [[mu] m] is, the inner diameter D a of the main bearing, the rotary shaft located within main bearing spindle a clearance X a [ ⁇ m] representing the difference between the diameter d a of the section, the clearance X B representing the inner diameter D B of the sub bearing, the difference between the diameter d B of the auxiliary shaft portion of the rotating shaft located within the auxiliary bearing [ ⁇ m], shaft deflection amount C A [ ⁇ m] representing the shaft deflection amount of the main shaft portion, shaft deflection amount C B [ ⁇ m] representing the shaft deflection amount of the sub shaft portion, the lower end portion
  • the compressor can effectively control the inclination and the swing of the rotating shaft when the motor unit is driven by satisfying the relationship of the above formulas 2 and 6. Therefore, the compressor can prevent seizure between the rotating shaft and the main bearing during driving of the electric motor unit, and can prevent seizure between the rotating shaft and the auxiliary bearing. As a result, it is possible to suppress seizure between the rotating shaft of the compressor, the main bearing, and the auxiliary bearing, and to suppress the disproportionation reaction of the R1123 refrigerant.
  • FIG. 3 is a sectional view taken along line AA in FIG. 2.
  • FIG. 3 is a sectional view taken along line BB in FIG.
  • It is a conceptual diagram which shows the compression mechanism part of the compressor which concerns on Embodiment 1 of this invention.
  • It is the schematic of the compression mechanism part of FIG. It is a figure showing the relationship between the shaft diameter d [mm] of a rotating shaft, and shaft deflection amount C [micrometer].
  • FIG. 1 is an internal configuration diagram showing the inside of the compressor according to Embodiment 1 of the present invention.
  • a twin rotary type compressor 100 having two cylindrical cylinders in the compression mechanism section will be described as an example of the compressor.
  • the compressor 100 is a hermetic electric compressor including a hermetic container 1, and an electric motor unit 2 and a compression mechanism unit 3 inside the hermetic container 1.
  • the sealed container 1 includes a bottomed cylindrical lower sealed container 13 and an upper sealed container 12 that closes an upper opening of the lower sealed container 13.
  • the connecting portion between the lower sealed container 13 and the upper sealed container 12 is fixed by welding, and the sealed state is maintained.
  • a suction pipe 15 is connected to the lower sealed container 13, and a suction muffler 14 is attached to the suction pipe 15.
  • the suction pipe 15 is a connection pipe for sending the gas refrigerant flowing in via the suction muffler 14 into the compression mechanism unit 3.
  • the lower airtight container 13 may be provided with an oil supply mechanism in which lubricating oil supplied to the compression mechanism unit 3 is stored.
  • the discharge pipe 4 is connected to the upper sealed container 12 on the axis extension line of the rotating shaft 31.
  • the discharge pipe 4 is a pipe that is attached to the sealed container 1 and discharges the refrigerant compressed by the compression mechanism unit 3 to the outside of the sealed container 1.
  • the inner diameter of the discharge pipe is always formed at a constant size.
  • the discharge pipe 4 should just be provided in the airtight container 1, and does not necessarily need to be arrange
  • the upper sealed container 12 is further provided with an airtight terminal 16 for electrical connection with the electric motor unit 2 in the sealed container 1 and a rod 17 to which a cover for protecting the airtight terminal 16 is attached.
  • the electric motor unit 2 includes a stator 21 fixed to the lower hermetic container 13 and a rotor 22 provided rotatably on the inner peripheral side of the stator 21.
  • a rotation shaft 31 is fixed to the center of the rotor 22.
  • the stator 21 is fixed to the lower sealed container 13 of the sealed container 1 by various fixing methods such as shrink fitting and welding.
  • the stator 21 is electrically connected to the hermetic terminal 16 by a lead wire 18.
  • FIG. 2 is a longitudinal sectional view showing a compression mechanism portion of the compressor according to Embodiment 1 of the present invention.
  • 3 is a cross-sectional view taken along line AA in FIG. 4 is a cross-sectional view taken along line BB in FIG.
  • the configuration of the compression mechanism unit 3 will be described with reference to FIGS. 3 and 4, the illustration of the eccentric shaft portion 31c and the eccentric shaft portion 31d is omitted.
  • the compression mechanism section 3 is accommodated in the sealed container 1 and compresses the refrigerant flowing into the sealed container 1.
  • the compression mechanism unit 3 is a twin rotary type compression mechanism having two cylindrical cylinders.
  • the compression mechanism unit 3 is disposed below the electric motor unit 2 in the sealed container 1 and fixed to the lower sealed container 13. Yes.
  • the compression mechanism unit 3 includes a rotary shaft 31, a main bearing 32, a sub bearing 33, a first cylindrical cylinder 34a, a first rolling piston 35a, a second cylindrical cylinder 34b, and a second rolling piston. 35b and a partition plate 36.
  • the rotary shaft 31 is connected to the rotor 22 of the electric motor unit 2 and transmits the rotational force of the electric motor unit 2 to the compression mechanism unit 3.
  • the rotating shaft 31 includes a main shaft portion 31a fixed to the rotor 22 of the electric motor unit 2, and a sub shaft portion 31b provided on the opposite side of the main shaft portion 31a in the axial direction.
  • the rotating shaft 31 is provided between the main shaft portion 31a and the subshaft portion 31b, and an eccentric shaft portion 31c inserted into the first rolling piston 35a and an eccentric shaft inserted into the second rolling piston 35b. Part 31d.
  • the eccentric shaft portion 31c and the eccentric shaft portion 31d are arranged with a predetermined phase difference (for example, 180 °).
  • the rotary shaft 31 has a main shaft portion 31 a that is rotatably supported by a main bearing 32 and a sub shaft portion 31 b that is rotatably supported by a sub bearing 33.
  • the main bearing 32 is a closing member that closes one end face (on the motor part 2 side) of both ends of the first cylindrical cylinder 34a.
  • the main bearing 32 and the first cylindrical cylinder 34a are molded and assembled as separate articles.
  • the sub-bearing 33 is a closing member that closes one end face of the both ends of the second cylindrical cylinder 34b (on the opposite side to the electric motor part 2 in the axial direction).
  • the sub bearing 33 and the second cylindrical cylinder 34b are molded and assembled as separate articles.
  • the first cylindrical cylinder 34a is formed in a substantially cylindrical shape, and both end surfaces of the substantially cylindrical shape are closed by the main bearing 32 and the partition plate 36 in the axial direction of the rotary shaft 31, as shown in FIG.
  • a chamber 40a sealed in the internal space of the first cylindrical cylinder 34a is formed.
  • the chamber 40a accommodates an eccentric shaft portion 31c of the rotating shaft 31 shown in FIG. 2 and a first rolling piston 35a that is rotatably fitted to the eccentric shaft portion 31c.
  • the first cylindrical cylinder 34a is formed with a first vane sliding groove 41a in the radial direction.
  • a first vane 37a is provided in the first vane sliding groove 41a.
  • the first cylindrical cylinder 34a of the compression mechanism unit 3 is provided with a first suction port 42a for sucking the refrigerant.
  • the first suction port 42a is formed in the radial direction of the first cylindrical cylinder 34a.
  • the first suction port 42a is connected to the suction pipe 15 described above and serves as a path for guiding the refrigerant into the chamber 40a of the first cylindrical cylinder 34a.
  • the first rolling piston 35a is mounted on the eccentric shaft portion 31c of the rotary shaft 31 shown in FIG. 2, and the first vane 37a that rotates eccentrically in the chamber 40a as the rotary shaft 31 rotates and is pressed against the outer periphery.
  • a compression chamber is configured to perform a suction operation and a compression operation.
  • the first vane 37a is pressed against the first rolling piston 35a by an urging means (not shown).
  • the first vane 37a reciprocates in the first vane sliding groove 41a while contacting the first rolling piston 35a.
  • the first vane 37a reciprocates in the first vane sliding groove 41a, and a space formed between the first cylindrical cylinder 34a and the first rolling piston 35a is defined as a suction chamber and a compression chamber. It is divided into.
  • the second cylindrical cylinder 34b is formed in a substantially cylindrical shape, and both end surfaces of the substantially cylindrical shape are closed by the auxiliary bearing 33 and the partition plate 36 in the axial direction of the rotary shaft 31, as shown in FIG.
  • a sealed chamber 40b is formed in the internal space of the second cylindrical cylinder 34b.
  • the chamber 40b accommodates an eccentric shaft portion 31d of the rotary shaft 31 shown in FIG. 2 and a second rolling piston 35b that is rotatably fitted to the eccentric shaft portion 31d.
  • the second cylindrical cylinder 34b has a second vane sliding groove 41b formed in the radial direction.
  • a second vane 37b is provided in the second vane sliding groove 41b.
  • the second cylindrical cylinder 34b of the compression mechanism unit 3 is provided with a second suction port 42b for sucking the refrigerant.
  • the second suction port 42b is formed in the radial direction of the second cylindrical cylinder 34b.
  • the second suction port 42b is connected to the suction pipe 15 described above and serves as a path for guiding the refrigerant into the chamber 40b of the second cylindrical cylinder 34b.
  • the second rolling piston 35b is attached to the eccentric shaft portion 31d of the rotary shaft 31 shown in FIG. 2, and the second vane 37b is rotated eccentrically in the chamber 40b by the rotation of the rotary shaft 31 and pressed against the outer periphery.
  • a compression chamber is configured to perform a suction operation and a compression operation.
  • the second vane 37 b is pressed against the second rolling piston 35 b by urging means (not shown).
  • the second vane 37b reciprocates in the second vane sliding groove 41b while being in contact with the second rolling piston 35b as the eccentric shaft portion 31d rotates.
  • the second vane 37b reciprocates in the second vane sliding groove 41b, and a space formed between the second cylindrical cylinder 34b and the second rolling piston 35b is defined as a suction chamber and a compression chamber. It is divided into.
  • the partition plate 36 is provided between the first cylindrical cylinder 34a and the second cylindrical cylinder 34b.
  • the partition plate 36 has one end face (opposite to the electric motor section 2) of one end of the first cylindrical cylinder 34a and one end (electric motor section) of the second cylindrical cylinder 34b.
  • 2 is a closing member that closes the end surface on the second side.
  • the rotating shaft 31 rotates when the electric motor unit 2 is driven.
  • the eccentric shaft portion 31c and the eccentric shaft portion 31d of the rotating shaft 31 rotate.
  • the first rolling piston 35a attached to the eccentric shaft portion 31c rotates eccentrically in the first cylindrical cylinder 34a
  • the second rolling piston 35b attached to the eccentric shaft portion 31d serves as the second cylindrical cylinder. It rotates eccentrically within 34b.
  • the first rolling piston 35a covering the eccentric shaft portion 31c of the rotating shaft 31 is eccentrically rotated in the first cylindrical cylinder 34a by the rotation of the rotating shaft 31, and is delimited by the first vane 37a.
  • the compression chamber capacity in the first cylindrical cylinder 34a changes continuously. That is, as the first rolling piston 35a rotates, the volume of the space surrounded by the first cylindrical cylinder 34a, the first rolling piston 35a, and the first vane 37a is reduced in the chamber 40a. The refrigerant is compressed.
  • the second rolling piston 35b covering the eccentric shaft portion 31d of the rotating shaft 31 is eccentrically rotated in the second cylindrical cylinder 34b by the rotation of the rotating shaft 31, thereby being separated by the second vane 37b.
  • the compression chamber capacity in the second cylindrical cylinder 34b is continuously changed. That is, the rotation of the second rolling piston 35b reduces the volume of the space surrounded by the second cylindrical cylinder 34b, the second rolling piston 35b, and the second vane 37b in the chamber 40b.
  • the refrigerant is compressed.
  • the compression chamber is provided with a discharge valve (not shown) that is released when the pressure exceeds a predetermined pressure, and high-pressure refrigerant gas is discharged from the chamber 40a and the chamber 40b into the sealed container 1 when the pressure exceeds the predetermined pressure.
  • the compressed refrigerant gas passes through the clearance of the electric motor unit 2 and is discharged from the discharge pipe 4 into the refrigerant circuit outside the compressor 100.
  • Refrigerating machine oil is stored in the lower part of the hermetic container 1, and the oil is supplied to each part by an oil supply mechanism (not shown) of the rotating shaft 31 to keep the compression mechanism part 3 lubricated.
  • An extreme pressure additive of 0.5 to 2 [wt%] may be added to the refrigerating machine oil enclosed in the compressor with respect to the total weight of the refrigerating machine oil. Thereby, seizure of the rotating shaft and the bearing during the operation of the R1123 refrigerant can be further suppressed.
  • the compressor 100 uses a single refrigerant of R1123 refrigerant, which is one type of hydrofluoroolefin, as an operating refrigerant.
  • Table 1 shows pressure comparison and physical property values of R1123 refrigerant and R410A refrigerant and R32 refrigerant used as conventional refrigerants.
  • the operating conditions of the compressor were determined as a condensing temperature of 68 ° C., an evaporating temperature of 12 ° C., and a compressor speed of 140 rps as the conditions that put the most weight on the rotating shaft of the compressor.
  • the maximum load and maximum deflection in Table 1 are finite elements for a bearing system of a rotary compressor having a stroke volume V st [cc] in the range of 5 [cc] ⁇ V st [cc] ⁇ 80 [cc]. Calculated by the law.
  • the R1123 refrigerant has a larger refrigerant gas load than the R32 refrigerant or the R410A refrigerant, and the amount of deflection of the rotating shaft is larger than when the R32 refrigerant or the R410A refrigerant is used. That is, the R1123 refrigerant is a refrigerant that is used in a higher pressure state than the R32 refrigerant or the R410A refrigerant, and the rotating shaft has a large amount of bending during operation of the refrigerant that receives the refrigerant.
  • the compressor 100 needs to be assembled with the coaxiality of the main bearing and the auxiliary bearing satisfying the following formula in order to prevent seizure between the rotating shaft 31 and the main bearing 32. is there.
  • FIG. 5 is a conceptual diagram showing a compression mechanism section of the compressor according to Embodiment 1 of the present invention.
  • FIG. 6 is a schematic view of the compression mechanism portion of FIG. The white arrow shown in FIG. 6 shows the direction of the gas load by a gas refrigerant.
  • FIG. 5 In the conceptual diagram of FIG. 5, the relationship among the rotating shaft 31, the main bearing 32, and the auxiliary bearing 33 will be described.
  • portions corresponding to the first cylindrical cylinder 34 a, the second cylindrical cylinder 34 b, and the partition plate 36 in FIG. 2 are collectively referred to as a cylinder 34. Note that when a single rotary compressor is used, the cylinder 34 used in the compressor corresponds to the cylinder 34.
  • the compression mechanism unit 3 has a ratio of the distance between the lower end 33a of the sub bearing 33 and the upper end 32b of the main bearing 32 to the distance between the lower end 32a and the upper end 32b of the main bearing 32 is 1: ⁇ . Further, in the compression mechanism section 3, the ratio between the distance between the lower end 33a of the auxiliary bearing 33 and the upper end 32b of the main bearing 32 and the distance between the lower end 33a and the upper end 33b of the auxiliary bearing 33 is 1: ⁇ .
  • the distance between the central axis E of the main bearing 32 and the central axis F of the auxiliary bearing 33 is expressed as a coaxiality R [ ⁇ m]. Further, the amount of axial deviation between the central axis E of the main bearing 32 and the central axis F of the auxiliary bearing 33 is represented as R / 2.
  • the shaft diameter of the main shaft portion 31a of the rotating shaft 31 located in the main bearing 32 is defined as a diameter d A [mm]
  • the inner diameter of the bearing portion of the main bearing 32 is defined as D A [mm].
  • a [ ⁇ m] and the ratio of the distance between the lower end 32a and the upper end 32b of the main bearing 32 when the distance between the lower end 33a of the auxiliary bearing 33 and the upper end 32b of the main bearing 32 is 1 (reference).
  • ⁇ it is expressed by the following formula 1.
  • the coaxiality R [ ⁇ m] which is the distance between the central axis E of the main bearing 32 and the central axis F of the auxiliary bearing 33, is 0 or more. Therefore, the coaxiality R [ ⁇ m] for avoiding the contact between the main bearing 32 and the rotating shaft 31 at the contact portion that becomes a seizure location is such that the coaxiality R [ ⁇ m] is 0 or more and the formula 1 From the above, it is expressed as Equation 2.
  • the amount of shaft deflection C A [ ⁇ m] is calculated by the finite element method for the rotating shaft 31, the main bearing 32, and the auxiliary bearing 33.
  • the longitudinal elastic modulus is set to 170 [GPa] and the Poisson's ratio is set to 0.25.
  • FIG. 7 shows the calculation result of the axial deflection amount C A [ ⁇ m].
  • FIG. 7 is a diagram illustrating the relationship between the shaft diameter d [mm] of the rotating shaft 31 and the shaft deflection amount C [ ⁇ m]. From FIG. 7, the relationship between the shaft diameter d A [mm] of the rotating shaft 31 and the shaft deflection amount C A [ ⁇ m] is expressed by the following formula 3.
  • Equation 4 the coaxiality R [ ⁇ m] for avoiding the contact between the main bearing 32 and the rotating shaft 31 at the contact portion D, which is a seizure location, is obtained as in Equation 4.
  • a clearance X B [ ⁇ m] representing the difference between the diameter d B of the auxiliary shaft portion 31b of the rotary shaft 31 located within the inner diameter D B and the sub-bearing 33 of the sub-bearing 33 described above, the auxiliary bearing 33
  • the shaft deflection amount C B [ ⁇ m] representing the shaft deflection amount C of the auxiliary shaft portion 31b of the rotary shaft 31 is set to 1 (the distance between the lower end portion 33a of the auxiliary bearing 33 and the upper end portion 32b of the main bearing 32 is 1 (
  • ⁇ the distance between the lower end portion 33a and the upper end portion 33b of the sub-bearing 33
  • the coaxiality R [ ⁇ m] which is the distance between the central axis E of the main bearing 32 and the central axis F of the auxiliary bearing 33, is 0 or more. Therefore, the coaxiality R [ ⁇ m] for avoiding contact between the sub-bearing 33 and the rotating shaft 31 at the contact portion that becomes the seizure location is defined by the condition that the coaxiality R [ ⁇ m] is 0 or more and Formula 5 From the above, it is expressed as Expression 6.
  • the shaft deflection amount C B [ ⁇ m] is calculated by the finite element method for the rotating shaft 31, the main bearing 32, and the auxiliary bearing 33.
  • the longitudinal elastic modulus is set to 170 [GPa] and the Poisson's ratio is set to 0.25.
  • FIG. 7 shows the calculation result of the axial deflection amount C B [ ⁇ m].
  • FIG. 7 is a diagram illustrating the relationship between the shaft diameter d [mm] of the rotating shaft 31 and the shaft deflection amount C [ ⁇ m]. From FIG. 7, the relationship between the shaft diameter d B [mm] of the rotating shaft 31 and the shaft deflection amount C B [ ⁇ m] is expressed by the following Expression 7.
  • Equation 8 the coaxiality R [ ⁇ m] for avoiding contact between the sub-bearing 33 and the rotating shaft 31 at the contact portion that becomes a seizure location is obtained as in Equation 8.
  • the compressor 100 according to Embodiment 1 of the present invention effectively satisfies the relationship of the above formulas 2 and 6, thereby effectively reducing the inclination and swinging of the rotating shaft 31 when the motor unit 2 is driven. Can be controlled. Therefore, the compressor 100 can prevent seizure between the rotary shaft 31 and the main bearing 32 during driving of the electric motor unit 2, and can prevent seizure between the rotary shaft 31 and the auxiliary bearing 33. As a result, seizure between the rotary shaft 31 of the compressor 100, the main bearing 32, and the sub bearing 33 can be suppressed, and the disproportionation reaction of the R1123 refrigerant can be suppressed.
  • the shaft deflection amount C A [ ⁇ m] and the shaft deflection amount C B [ ⁇ m] are set in the following formulas 3 and 7, so that the electric motor It is possible to effectively control the tilt and swing of the rotary shaft 31 when the unit 2 is driven. Therefore, the compressor 100 can prevent seizure between the rotary shaft 31 and the main bearing 32 during driving of the electric motor unit 2, and can prevent seizure between the rotary shaft 31 and the auxiliary bearing 33. As a result, seizure between the rotary shaft 31 of the compressor 100, the main bearing 32, and the sub bearing 33 can be suppressed, and the disproportionation reaction of the R1123 refrigerant can be suppressed.
  • FIG. 1 of the present invention has been described using a single refrigerant of R1123 refrigerant, which is one type of hydrofluoroolefin, as the operating refrigerant of the compressor 100.
  • R1123 refrigerant which is one type of hydrofluoroolefin
  • another operating refrigerant used for the compressor 100 will be described.
  • the operating refrigerant is not limited to a single refrigerant of the R1123 refrigerant, and the R1123 refrigerant may be used in combination with the R32 refrigerant in order to ensure the refrigerating capacity.
  • the GWP of the mixed refrigerant is desirably less than 500, and more desirably less than 100.
  • Table 2 shows the pressure comparison and physical property values of the mixed refrigerant of R1123 refrigerant and R32 refrigerant used as a conventional refrigerant.
  • the operating conditions of the compressor were determined as a condensing temperature of 68 ° C., an evaporating temperature of 12 ° C., and a compressor speed of 140 rps as the conditions that put the most weight on the rotating shaft of the compressor.
  • clearance X A representing the difference between the diameter d A of the main shaft portion 31a of the rotary shaft 31 located within the inner diameter D A and a main bearing 32 of the main bearing 32 described above [[mu] m], the central axis of the main bearing 32 A coaxial deflection R [ ⁇ m], which is a distance between E and the center axis F of the auxiliary bearing 33, and an axial deflection amount C A [representing an axial deflection amount C of the main shaft portion 31 a of the rotary shaft 31 disposed in the main bearing 32.
  • a clearance X B [ ⁇ m] representing the difference between the diameter d B of the auxiliary shaft portion 31b of the rotary shaft 31 located within the inner diameter D B and the sub-bearing 33 of the sub-bearing 33 described above, the central axis of the main bearing 32 A coaxial degree R [ ⁇ m], which is a distance between E and the center axis F of the auxiliary bearing 33, and an axial deflection quantity C B representing the axial deflection quantity C of the auxiliary shaft part 31b of the rotary shaft 31 disposed in the auxiliary bearing 33.
  • clearance X A [ ⁇ m] and clearance X B [ ⁇ m] are common to those of the single refrigerant of the R1123 refrigerant of the compressor 100 according to the first embodiment.
  • coaxiality R [ ⁇ m] for avoiding the contact between the main bearing 32 and the rotating shaft 31 at the contact portion that becomes the seizure location the condition that the coaxiality R [ ⁇ m] is 0 or more and Formula 1 From the above, it is expressed as the following formula 2.
  • the coaxiality R [ ⁇ m] for avoiding the contact between the sub-bearing 33 and the rotating shaft 31 at the contact portion that becomes the burn-in portion is a condition that the coaxiality R [ ⁇ m] is 0 or more and Formula 5 From the above, the following expression 6 is obtained.
  • the shaft deflection amount C A [ ⁇ m] and the shaft deflection amount C B [ ⁇ m] are set to any one of the conditions (1) to (5) in Table 3 below from the mixing ratio of the refrigerant composition. Yes.
  • the compressor 100 can prevent seizure between the rotary shaft 31 and the main bearing 32 during driving of the electric motor unit 2, and can prevent seizure between the rotary shaft 31 and the auxiliary bearing 33. As a result, seizure between the rotating shaft 31 of the compressor 100, the main bearing 32, and the sub bearing 33 can be suppressed, and the disproportionation reaction of R1123 can be suppressed.
  • the compressor 100 can prevent seizure between the rotary shaft 31 and the main bearing 32 during driving of the electric motor unit 2, and can prevent seizure between the rotary shaft 31 and the auxiliary bearing 33.
  • seizure between the rotary shaft 31 of the compressor 100, the main bearing 32, and the sub bearing 33 can be suppressed, and the disproportionation reaction of the R1123 refrigerant can be suppressed.
  • the present inventor also satisfies the relationship of the following formulas 2 and 6 when the three types of mixed refrigerants including the R1123 refrigerant and the R32 refrigerant are used as the operating refrigerant. It has been found that the tilt and swing of the rotary shaft 31 can be effectively controlled. Note that the GWP of the mixed refrigerant is desirably less than 500, and more desirably less than 100.
  • the refrigerant flow rate required for the compressor changes, so the ratio of each refrigerant to the mass of the entire operating refrigerant
  • the axial deflection amount C A [ ⁇ m] and the axial deflection amount C B [ ⁇ m] are set within the range of the conditions shown in Table 4 below from the mixing ratio of the refrigerant composition.
  • the compressor 100 can prevent seizure between the rotary shaft 31 and the main bearing 32 during driving of the electric motor unit 2, and can prevent seizure between the rotary shaft 31 and the auxiliary bearing 33. As a result, seizure between the rotating shaft 31 of the compressor 100, the main bearing 32, and the sub bearing 33 can be suppressed, and the disproportionation reaction of R1123 can be suppressed.
  • the compressor 100 can prevent seizure between the rotary shaft 31 and the main bearing 32 during driving of the electric motor unit 2, and can prevent seizure between the rotary shaft 31 and the auxiliary bearing 33.
  • seizure between the rotary shaft 31 of the compressor 100, the main bearing 32, and the sub bearing 33 can be suppressed, and the disproportionation reaction of the R1123 refrigerant can be suppressed.
  • Embodiment 3 FIG.
  • the rotating shaft 31 of the compressor 100 is subjected to solid lubrication treatment.
  • the solid lubrication treatment may be performed on the main bearing 32 or the sub bearing 33 together with the rotating shaft 31 or instead of the rotating shaft 31.
  • seizure of the rotary shaft 31 and the main bearing 32 or the rotary shaft 31 and the sub bearing 33 during the R1123 refrigerant operation is performed. Further suppression can be achieved.
  • the sub-shaft portion 31b of the rotating shaft 31 and the portion that contacts the inner wall of the sub-bearing 33 serve as a support point
  • the sub-shaft portion 31b may be selectively subjected to solid lubrication treatment.
  • the structure of the rotating shaft 31 has a simpler structure in the region of the tip portion of the rotating shaft 31 than the region in which the eccentric shaft portion 31c and the eccentric shaft portion 31d are provided. Is also easy.
  • the portion of the rotary shaft 31 that contacts the tip of the auxiliary shaft portion 31b and the inner wall of the auxiliary bearing 33 serves as a support point, so that the rotation shaft 31 and the bearing Can be prevented from coming into solid contact.
  • the compressor 100 according to the embodiment of the present invention is a twin rotary type compressor having two cylindrical cylinders in the compression mechanism unit 3, but may be a single rotary type compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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PCT/JP2017/003915 2017-02-03 2017-02-03 圧縮機 Ceased WO2018142564A1 (ja)

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PCT/JP2017/003915 WO2018142564A1 (ja) 2017-02-03 2017-02-03 圧縮機
CZ2019-487A CZ309104B6 (cs) 2017-02-03 2017-02-03 Kompresor
CN201780079272.7A CN110249132A (zh) 2017-02-03 2017-02-03 压缩机
JP2018565189A JPWO2018142564A1 (ja) 2017-02-03 2017-02-03 圧縮機
KR1020197015921A KR102204713B1 (ko) 2017-02-03 2017-02-03 압축기

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CN111271243A (zh) * 2018-12-05 2020-06-12 广东美芝精密制造有限公司 压缩机

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CN111271243B (zh) * 2018-12-05 2022-04-26 广东美芝精密制造有限公司 压缩机

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CZ2019487A3 (cs) 2019-08-21
CN110249132A (zh) 2019-09-17
CZ309104B6 (cs) 2022-02-02
KR102204713B1 (ko) 2021-01-19
KR20190072644A (ko) 2019-06-25

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