WO2018142536A1 - Compresseur - Google Patents

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Publication number
WO2018142536A1
WO2018142536A1 PCT/JP2017/003778 JP2017003778W WO2018142536A1 WO 2018142536 A1 WO2018142536 A1 WO 2018142536A1 JP 2017003778 W JP2017003778 W JP 2017003778W WO 2018142536 A1 WO2018142536 A1 WO 2018142536A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
compressor
suction
pipe connection
connection portion
Prior art date
Application number
PCT/JP2017/003778
Other languages
English (en)
Japanese (ja)
Inventor
亮 濱田
幹一朗 杉浦
貴也 木本
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2017/003778 priority Critical patent/WO2018142536A1/fr
Priority to CZ2019480A priority patent/CZ309050B6/cs
Priority to CN201780084682.0A priority patent/CN110249134B/zh
Priority to KR1020197015390A priority patent/KR102388016B1/ko
Priority to JP2018565162A priority patent/JP6840173B2/ja
Publication of WO2018142536A1 publication Critical patent/WO2018142536A1/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
    • 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
    • F04C29/06—Silencing
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • 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
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise
    • 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
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise
    • F05B2260/962—Preventing, counteracting or reducing vibration or noise by means creating "anti-noise"

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
  • hydrofluoroolefin is a promising refrigerant as a refrigerant used for countermeasures against global warming because it has a smaller GWP than the conventional refrigerant R410 or R32.
  • hydrofluoroolefin when hydrofluoroolefin is used as the operating refrigerant of the compressor, hydrofluoroolefin has a lower sound velocity than R32 refrigerant. Therefore, when the hydrofluoroolefin is operated with a conventional compressor, the resonance frequency due to the resonance between the suction muffler and the refrigerant operating sound transitions to a low frequency band.
  • the operation sound in the low frequency band has a problem that the effect of the sound insulating material attached around the compressor is thin and the quietness of the compressor is deteriorated.
  • the present invention has been made to solve the above-described problems, and provides a compressor that suppresses deterioration of silence due to resonance between a suction muffler and refrigerant operating sound even when hydrofluoroolefin is used as an operating refrigerant. Is.
  • the compressor according to the present invention includes a sealed container having a compression mechanism part, a suction pipe connected to the compression mechanism part, a suction muffler connected to the suction pipe, and a suction muffler connected to the suction muffler.
  • the ratio ⁇ [wt%] of the R1234yf refrigerant to the entire operating refrigerant and the distance L “mm” between the suction pipe connection portion and the suction pipe connection portion in the internal space of the suction muffler are as described above.
  • the resonance point can be arranged at a frequency where the noise of the compressor is small or a frequency at which the effect of the sound insulating material is easily exhibited. Therefore, the compressor can effectively suppress noise due to resonance between the suction muffler and the refrigerant operation sound. As a result, the quietness of the compressor using hydrofluoroolefin as the operating refrigerant can be improved.
  • 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 line graph which shows the noise of the common single compressor in a frequency band.
  • It is a broken line figure which shows the effect of the sound insulating material in a frequency band.
  • It is a broken line figure which shows the noise of the common compressor single-piece
  • FIG. 2 is a schematic side view of an inhalation muffler. It is the schematic top view of an inhalation muffler.
  • FIG. 6 is a schematic plan view of a modification of the suction muffler.
  • FIG. 10 is a schematic plan view of another modification of the suction muffler.
  • FIG. 1 is an internal configuration diagram showing the inside of the compressor according to Embodiment 1 of the present invention.
  • the compressor 100 includes a sealed container 1 in which a compression mechanism unit 3 is built.
  • the compressor 100 includes an electric motor unit 2 inside the sealed container 1.
  • the compressor 100 is connected to the suction pipe 15 connected to the compression mechanism unit 3, the suction muffler 14 connected to the suction pipe 15, and the supply for supplying the refrigerant to the suction muffler 14.
  • a tube 19 19.
  • 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 described later is attached to the suction pipe 15.
  • the suction pipe 15 is connected to the compression mechanism unit 3 and 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 suction muffler 14 reduces the flow noise of the refrigerant sucked into the compression mechanism unit 3.
  • the suction muffler 14 is connected to the suction pipe 15 and is connected to the compression mechanism unit 3 through the suction pipe 15.
  • a supply pipe 19 for supplying a refrigerant to the inner space M ⁇ b> 1 of the suction muffler 14 is connected to a top part 14 a of the suction muffler 14, and a suction pipe 15 is connected to a bottom part 14 b of the suction muffler 14. ing.
  • a connection portion between the suction muffler 14 provided on the top portion 14 a of the suction muffler 14 and the supply pipe 19 is referred to as a supply pipe connection portion 14 a 1, and the connection between the suction muffler 14 provided on the bottom portion 14 b of the suction muffler 14 and the suction pipe 15.
  • This part is referred to as a suction pipe connecting part 14b1.
  • the distance between the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 is referred to as a distance L.
  • 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 low-pressure refrigerant supplied from the refrigerant circuit outside the compressor 100 to the suction muffler 14 through the supply pipe 19 is supplied from the suction pipe 15 to the first cylindrical cylinder. 34a is supplied.
  • the second rolling piston 35b rotates in the second cylindrical cylinder 34b the low-pressure refrigerant supplied from the refrigerant circuit outside the compressor 100 to the suction muffler 14 through the supply pipe 19 is supplied from the suction pipe 15 to the second cylinder. It is supplied into the cylindrical cylinder 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 operating refrigerant used in the compressor 100 described above As the operating refrigerant of the compressor 100, a mixed refrigerant obtained by mixing an R32 refrigerant and an R1234yf refrigerant which is one type of hydrofluoroolefin is used. Note that the GWP of the mixed refrigerant is desirably less than 500, and more desirably less than 100. Table 1 shows physical property values of the R1234yf refrigerant and the R32 refrigerant used as a conventional refrigerant.
  • the R1234yf refrigerant has a lower sound speed than the conventional refrigerant R32.
  • the resonance frequency f [Hz] of the suction muffler 14 transitions to a low frequency band.
  • the operation noise in the low frequency band has a small effect of the sound insulating material attached around the compressor, and the quietness of the compressor is deteriorated.
  • the compressor using the R1234yf refrigerant as the operating refrigerant may deteriorate the quietness of the compressor as compared with the R32 refrigerant that is a conventional refrigerant.
  • the noise of the compressor as a whole can be reduced by arranging the resonance point at a frequency where the noise of the compressor other than resonance occurs. Moreover, the noise of the whole compressor can be reduced by arranging the resonance point at a frequency at which the effect of the sound insulating material is easily exhibited.
  • FIG. 5 is a line diagram showing noise of a general compressor alone in the frequency band.
  • the operating conditions of the compressor shown in FIG. 5 are as follows: the single refrigerant of the R32 refrigerant is the working refrigerant, the condensation temperature is 52 [° C.], the evaporation temperature is 5 [° C.], and the rotation speed of the compressor is 60 [rps]. It is.
  • the noise [dB] of the compressor alone generally increases almost monotonically below 900 [Hz] and becomes flat at 900 [Hz] or higher. Therefore, the noise of the whole compressor 100 can be reduced by setting the resonance frequency f [Hz] of the compressor 100 to less than 900 [Hz].
  • FIG. 6 is a line diagram showing the effect of the sound insulating material in the frequency band.
  • the effect [dB] of the sound insulating material is generally greater at 1000 [Hz] or more. Therefore, by making the resonance frequency f [Hz] larger than 1000 [Hz], the effect of the sound insulating material can be applied, and the noise of the entire compressor 100 can be reduced.
  • FIG. 7 is a line diagram showing the noise of a general compressor having a sound insulating material in the frequency band.
  • the noise [dB] of the compressor alone is generally maximum in the range of 900 [Hz] to 1000 [Hz]. Therefore, the noise of the compressor 100 as a whole can be reduced by making the resonance frequency f [Hz] of the compressor 100 less than 900 [Hz] or greater than 1000 [Hz].
  • the muffler effect E [dB] of the suction muffler 14 is that the distance between the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 in the inner space M1 of the suction muffler 14 is the distance L “mm”, and the suction frequency is f.
  • [Hz] and the sound speed are c [mm / s], they are expressed by the following formula 1.
  • the resonance frequency f [Hz] at which the muffler effect E [dB] of the inhalation muffler 14 becomes small is when * of sin (*) is ⁇ , 2 ⁇ , 3 ⁇ . Therefore, the resonance frequency f [Hz] at which the muffler effect E [dB] of the suction muffler 14 is reduced is expressed by the following equation 2.
  • Equation 2 n represents n-th order resonance.
  • FIG. 8 is a line diagram showing the muffler effect E [dB] in the frequency band.
  • the operating conditions of the compressor shown in FIG. 8 are as follows: the condensation temperature CT is 52 [° C.], the evaporation temperature ET is ⁇ 10 [° C.], the subcool SC is 5 [deg], the superheat SH is 0 [deg], and the suction muffler 14
  • the distance L “mm” between the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 in the internal space M1 is set to 300 [mm].
  • the solid line shown in FIG. 8 represents the muffler effect E [dB] of the R1234yf refrigerant.
  • the sound velocity c [m / s] of the R1234yf refrigerant is 135.8 [m / s].
  • the broken line shown in FIG. 8 represents the muffler effect E [dB] of the R32 refrigerant.
  • the sound speed c [m / s] of the R32 refrigerant is 211.5 [m / s].
  • the general suction muffler is formed such that the distance L “mm” between the supply pipe connection portion and the suction pipe connection portion in the inner space of the suction muffler is in the range of 100 [mm] ⁇ L ⁇ 300 [mm].
  • the distance L “mm” between the supply pipe connection portion and the suction pipe connection portion in the internal space of the suction muffler is 100 [ mm] ⁇ L ⁇ 300 [mm] may be considered.
  • the resonance frequency f [ For [Hz], a secondary, tertiary, or quartic resonance frequency that affects the generation of noise may be considered.
  • FIG. 9 is a graph showing the relationship between the ratio ⁇ [wt%] of R1234yf to the entire refrigerant and the sound velocity c [mm / s].
  • the speed of sound c1 [mm / s] represented by the solid line is the speed of sound based on the operating conditions of the compressor when the sound speed of the refrigerant shown in Table 1 is maximum.
  • the sound speed c2 [mm / s] represented by the broken line is a sound speed based on the operating condition of the compressor when the sound speed of the refrigerant shown in Table 1 is minimum.
  • a distance L “mm” between the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 in the internal space M1 of the suction muffler 14 is formed in a range of 100 [mm] ⁇ L ⁇ 300 [mm].
  • the mixed refrigerant containing R1234yf refrigerant and R32 refrigerant as main components is the working refrigerant and the ratio of R1234yf to the whole working refrigerant is ⁇ [wt%]
  • Equation 3 represents that the secondary resonance frequency f [Hz] is located in a range larger than 1000 [Hz] when the sound speed of the refrigerant is the sound speed c2.
  • Equation 4 indicates that the secondary resonance frequency f [Hz] is in a range less than 900 [Hz] when the sound speed of the refrigerant is the sound speed c1, and the third order when the sound speed of the refrigerant is the sound speed c2.
  • the resonance frequency f [Hz] is located in a range larger than 1000 [Hz].
  • Equation 5 is quaternary when the third-order resonance frequency f [Hz] is in a range less than 900 [Hz] when the sound speed of the refrigerant is the sound speed c1 and the sound speed of the refrigerant is the sound speed c2.
  • the resonance frequency f [Hz] is located in a range larger than 1000 [Hz].
  • Formula 6 represents that the resonance frequency f [Hz] is located in the range below 900 [Hz] when the sound speed of the refrigerant is the sound speed c1.
  • the ratio ⁇ [wt%] of the R1234yf refrigerant and the distance L “mm” between the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 in the internal space M1 of the suction muffler 14 are expressed by the above equation 3
  • the resonance point can be arranged at a frequency at which the compressor noise is low or a frequency at which the effect of the sound insulating material is easily exhibited. Therefore, the compressor can effectively suppress noise due to resonance between the suction muffler and the refrigerant operation sound. As a result, the quietness of the compressor using hydrofluoroolefin as the operating refrigerant can be improved.
  • FIG. 10 is a schematic side view of the inhalation muffler.
  • FIG. 11 is a schematic plan view of the suction muffler. Parts having the same configuration as those of the compressors of FIGS. 1 to 9 are denoted by the same reference numerals and description thereof is omitted.
  • a second embodiment in which the arrangement positions of the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 are specified will be described. As shown in FIGS. 10 and 11, at least one of the supply pipe connection portion 14 a 1 and the suction pipe connection portion 14 b 1 is disposed so as to be eccentric with respect to the longitudinal axis Y of the suction muffler 14.
  • FIG. 12 is a schematic plan view of a modified example of the inhalation muffler.
  • FIG. 12 shows a case where a plurality of supply pipe connection portions 14a1 or suction pipe connection portions 14b1 are provided.
  • the center point P1 of the line segment P is arranged eccentrically in the normal direction N of the line segment P connecting the centers of the supply pipe connection portions 14a1.
  • the center point Q1 of the line segment Q is decentered in the normal direction N of the line segment Q connecting the centers of the suction pipe connection portions 14b1. To do.
  • the compressor 100 increases the length of the bottom portion 14b and the top portion 14a of the suction muffler 14 depending on the ratio ⁇ [wt%] of the R1234yf refrigerant in order to effectively suppress noise due to resonance between the suction muffler and the refrigerant operation sound. By doing so, the distance L “mm” may be secured.
  • the lengths of the bottom portion 14b and the top portion 14a of the suction muffler 14 may be substantially restricted by the internal space of the refrigeration cycle apparatus in which the compressor 100 is mounted. Therefore, at least one of the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 is disposed so as to be eccentric with respect to the longitudinal axis Y of the suction muffler 14. At least one of the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 is decentered with respect to the longitudinal axis Y of the suction muffler 14 so that an appropriate distance L “mm” can be ensured.
  • the compressor 100 is configured so that the ratio ⁇ [wt%] of the R1234yf refrigerant and the distance L “mm” between the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 in the internal space M1 of the suction muffler 14 are as described above.
  • the resonance point can be arranged at a frequency where the noise of the compressor is low or a frequency where the effect of the sound insulating material is easily exhibited. Therefore, the compressor can effectively suppress noise due to resonance between the suction muffler and the refrigerant operation sound. As a result, the quietness of the compressor using hydrofluoroolefin as the operating refrigerant can be improved.
  • FIG. 13 is a schematic plan view of another modification of the suction muffler.
  • the suction muffler 14 is formed in an oval shape in a plan view, and the suction pipe muffler 14 and the suction pipe muffler 14 are connected to the supply pipe connecting portion 14 a 1 along the long axis J. At least one of the pipe connection portions 14b1 is disposed.
  • the suction muffler 14 is formed in an oval shape in plan view, and the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 are arranged along the long axis J of the oval shape. It has been established.
  • the compressor 100 increases the length of the bottom portion 14b and the top portion 14a of the suction muffler 14 depending on the ratio ⁇ [wt%] of the R1234yf refrigerant in order to effectively suppress noise due to resonance between the suction muffler and the refrigerant operation sound. By doing so, the distance L “mm” may be secured. However, the lengths of the bottom portion 14b and the top portion 14a of the suction muffler 14 may be substantially restricted by the internal space of the refrigeration cycle apparatus in which the compressor 100 is mounted.
  • the suction muffler 14 is formed in an oval shape in plan view, and at least one of the supply pipe connection portion 14 a 1 and the suction pipe connection portion 14 b 1 along the long axis J of the suction muffler 14. Is provided.
  • the compressor 100 ensures an appropriate distance L “mm” by arranging the oval shape of the suction muffler 14 and at least one of the supply pipe connection part 14a1 and the suction pipe connection part 14b1 eccentrically. Can do.
  • the suction muffler 14 is formed in an oval shape in plan view, and the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 are arranged along the long axis J of the oval shape. It has been established.
  • the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 are arranged side by side along the oval shape of the suction muffler 14 and the long axis J of the oval shape. A length of “mm” can be ensured.
  • the compressor 100 is configured so that the ratio ⁇ [wt%] of the R1234yf refrigerant and the distance L “mm” between the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 in the internal space M1 of the suction muffler 14 are as described above.
  • the resonance point can be arranged at a frequency where the noise of the compressor is low or a frequency where the effect of the sound insulating material is easily exhibited. Therefore, the compressor can effectively suppress noise due to resonance between the suction muffler and the refrigerant operation sound. As a result, the quietness of the compressor using hydrofluoroolefin as the operating refrigerant can be improved.
  • the suction muffler 14 is formed in an oval shape in plan view.
  • the compressor 100 can secure the volume of the suction muffler 14 by forming the shape of the upper wall of the suction muffler 14 in an oval shape in plan view. As a result, the amount of liquid refrigerant that can be stored in the suction muffler 14 can be increased, and liquid refrigerant can be prevented from flowing into the compression mechanism section 3.
  • 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)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Abstract

La présente invention concerne un compresseur pourvu d'un contenant étanche comportant un mécanisme de compression intégré, d'une conduite d'admission raccordée au mécanisme de compression, d'un silencieux d'admission raccordé à la conduite d'admission, et d'une conduite d'alimentation servant à alimenter en réfrigérant le silencieux d'admission et raccordée au silencieux d'admission. L'espace interne du silencieux d'admission est formé de sorte que la distance L [mm] entre la section de raccordement de conduite d'alimentation et la section de raccordement de conduite d'admission du silencieux d'admission s'inscrive dans la plage de 100 [mm] < L < 300 [mm]. En tant que réfrigérant d'exploitation, un réfrigérant mélangé contenant un réfrigérant R1234yf et un réfrigérant R32 en tant que constituants principaux, et définissant α [% en poids] en tant que rapport de R1234yf au réfrigérant d'exploitation total, une expression parmi les expressions 3 à 6 est satisfaite.
PCT/JP2017/003778 2017-02-02 2017-02-02 Compresseur WO2018142536A1 (fr)

Priority Applications (5)

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PCT/JP2017/003778 WO2018142536A1 (fr) 2017-02-02 2017-02-02 Compresseur
CZ2019480A CZ309050B6 (cs) 2017-02-02 2017-02-02 Kompresor
CN201780084682.0A CN110249134B (zh) 2017-02-02 2017-02-02 压缩机
KR1020197015390A KR102388016B1 (ko) 2017-02-02 2017-02-02 압축기
JP2018565162A JP6840173B2 (ja) 2017-02-02 2017-02-02 圧縮機

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PCT/JP2017/003778 WO2018142536A1 (fr) 2017-02-02 2017-02-02 Compresseur

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WO (1) WO2018142536A1 (fr)

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JP2001221046A (ja) * 2000-02-07 2001-08-17 Nissan Motor Co Ltd 自動車用排気消音装置
JP2006233890A (ja) * 2005-02-25 2006-09-07 Futaba Industrial Co Ltd 内燃機関用マフラ
WO2009078355A1 (fr) * 2007-12-14 2009-06-25 Daikin Industries, Ltd. Compresseur à carter fermé
JP2011185123A (ja) * 2010-03-05 2011-09-22 Daikin Industries Ltd 圧縮機ユニット、空気調和機及び給湯機
WO2011135817A1 (fr) * 2010-04-28 2011-11-03 パナソニック株式会社 Compresseur rotatif
JP2016121607A (ja) * 2014-12-24 2016-07-07 オイレス工業株式会社 自動車排気管用マフラ及びその製造方法

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JPH0631629B2 (ja) * 1987-03-09 1994-04-27 三菱電機株式会社 回転式圧縮機
KR100677515B1 (ko) * 2005-05-09 2007-02-02 엘지전자 주식회사 다단 로터리 압축기 및 이를 적용한 에어콘
JP4609583B2 (ja) * 2009-03-25 2011-01-12 ダイキン工業株式会社 吐出マフラ及び吐出マフラを備えた二段圧縮機
JP2012057503A (ja) 2010-09-07 2012-03-22 Panasonic Corp 回転式圧縮機
JP5818731B2 (ja) * 2012-03-29 2015-11-18 三菱電機株式会社 密閉型圧縮機及びこれを備えた冷凍サイクル装置
KR20140142802A (ko) * 2013-06-04 2014-12-15 삼성전자주식회사 실외 열교환기 및 공기조화기
KR20160051289A (ko) * 2014-11-03 2016-05-11 이상목 비대칭성 소음기
JP6466219B2 (ja) * 2015-03-20 2019-02-06 日立ジョンソンコントロールズ空調株式会社 空気調和機の室内機

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Publication number Priority date Publication date Assignee Title
JP2001221046A (ja) * 2000-02-07 2001-08-17 Nissan Motor Co Ltd 自動車用排気消音装置
JP2006233890A (ja) * 2005-02-25 2006-09-07 Futaba Industrial Co Ltd 内燃機関用マフラ
WO2009078355A1 (fr) * 2007-12-14 2009-06-25 Daikin Industries, Ltd. Compresseur à carter fermé
JP2011185123A (ja) * 2010-03-05 2011-09-22 Daikin Industries Ltd 圧縮機ユニット、空気調和機及び給湯機
WO2011135817A1 (fr) * 2010-04-28 2011-11-03 パナソニック株式会社 Compresseur rotatif
JP2016121607A (ja) * 2014-12-24 2016-07-07 オイレス工業株式会社 自動車排気管用マフラ及びその製造方法

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CN110249134A (zh) 2019-09-17
JP6840173B2 (ja) 2021-03-10
CZ309050B6 (cs) 2021-12-29
KR20190070979A (ko) 2019-06-21
CZ2019480A3 (cs) 2019-09-18
KR102388016B1 (ko) 2022-04-19
JPWO2018142536A1 (ja) 2019-11-07
CN110249134B (zh) 2021-10-29

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