WO2018142536A1

WO2018142536A1 - Compressor

Info

Publication number: WO2018142536A1
Application number: PCT/JP2017/003778
Authority: WO
Inventors: 亮濱田; 幹一朗杉浦; 貴也木本
Original assignee: 三菱電機株式会社
Priority date: 2017-02-02
Filing date: 2017-02-02
Publication date: 2018-08-09
Also published as: CN110249134A; CN110249134B; CZ2019480A3; JP6840173B2; KR102388016B1; KR20190070979A; CZ309050B6; JPWO2018142536A1

Abstract

This compressor is provided with a sealed container having a built-in compression mechanism, an intake pipe connected to the compression mechanism, an intake muffler connected to the intake pipe, and a supply pipe for supplying a refrigerant to the intake muffler and connected to the intake muffler. The internal space of the intake muffler is formed such that the distance L [mm] between the supply pipe connection section and the intake pipe connection section of the intake muffler is within the range 100 [mm] < L < 300 [mm]. Setting as the operating refrigerant a mixed refrigerant containing R1234yf refrigerant and R32 refrigerant as main components, and defining α [wt%] as the ratio of R1234yf to the total operating refrigerant, one of expression 3 to expression 6 is satisfied.

Description

Compressor

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. Thus, a compressor using an operating refrigerant mainly composed of hydrofluoroolefin has been proposed (see, for example, Patent Document 1).

JP 2012-57503 A

As described above, 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. However, 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. A supply pipe for supplying to the muffler, and in the internal space of the suction muffler, a distance L “mm” between the supply pipe connection portion and the suction pipe connection portion of the suction muffler is 100 [mm] < L <300 [mm] is formed, and when a mixed refrigerant containing R1234yf refrigerant and R32 refrigerant as main components is used as an operating refrigerant, and the ratio of R1234yf to the entire operating refrigerant is α [wt%], Any one of the following formulas 3 to 6 is satisfied.

In the compressor, the ratio α [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. By satisfying any one of the formulas 3 to 6, 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.

It is an internal block diagram which shows the inside of the compressor which concerns on Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the compression mechanism part of the compressor which concerns on Embodiment 1 of this invention. 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 | unit provided with the sound insulation material in a frequency band. It is a broken line figure which shows the muffler effect E [dB] in a frequency band. It is a figure showing the relationship between ratio (alpha) [wt%] of R1234yf with respect to the whole refrigerant | coolant, and sound velocity c [mm / s]. 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.

Embodiment 1 FIG.
FIG. 1 is an internal configuration diagram showing the inside of the compressor according to Embodiment 1 of the present invention. In the following description, a twin rotary type compressor 100 having two cylindrical cylinders in the compression mechanism section will be described as an example of the compressor. As shown in FIG. 1, 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. Further, 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.

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. In the sealed container 1, 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. In addition, 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. Moreover, the discharge pipe 4 should just be provided in the airtight container 1, and does not necessarily need to be arrange | positioned on the axis extension line of the rotating shaft 31. FIG. 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. Further, as shown in FIG. 3, 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. At the same time, a compression chamber is configured to perform a suction operation and a compression operation. Returning to FIG. 3, the first vane 37a is pressed against the first rolling piston 35a by an urging means (not shown). As the eccentric shaft portion 31c rotates, 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. In addition, 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. As shown in FIG. 4, 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. At the same time, a compression chamber is configured to perform a suction operation and a compression operation. Returning to FIG. 4, 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.

As shown in FIG. 2, the partition plate 36 is provided between the first cylindrical cylinder 34a and the second cylindrical cylinder 34b. In the axial direction of the rotating shaft 31, 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. As shown in FIG. 1, 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. In the suction muffler 14, 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. In the internal space M1 of the suction muffler 14, the distance between the supply pipe connection portion 14a1 and the suction pipe connection portion 14b1 is referred to as a distance L.

Next, the operation of the compressor 100 configured as described above will be described. In the compressor 100, the rotating shaft 31 rotates when the electric motor unit 2 is driven. As the rotating shaft 31 rotates, 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, and the second rolling piston 35b attached to the eccentric shaft portion 31d serves as the second cylindrical cylinder. It rotates eccentrically within 34b.

When the first rolling piston 35a rotates in the first cylindrical cylinder 34a, 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. When 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 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.

Next, the characteristics of the operating refrigerant used in the compressor 100 described above will be described. 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 operating conditions of the compressor include the conditions when the sound speed of the refrigerant is minimum (condensation temperature CT = −10 [° C.], superheat SH = 0 [deg]) among the general compressor suction conditions, and the refrigerant Are taken into consideration when the sound speed is maximum (condensation temperature CT = 15 [° C.], superheat SH = 10 [deg]).

From Table 1, it can be seen that the R1234yf refrigerant has a lower sound speed than the conventional refrigerant R32. When the sound speed c [m / s] of the refrigerant decreases, 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. For this reason, 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.

Generally, loud noise is generated at the resonance point of sound. Therefore, 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. As shown in FIG. 5, 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. As shown in FIG. 6, 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. As shown in FIG. 7, 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].

Here, 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. When [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 π, 2π, 3π. 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. In 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]. Has been. Therefore, when a mixed refrigerant of R1234yf refrigerant and R32 refrigerant is used as the operating refrigerant of the compressor, 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. Considering that 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], 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 α [wt%] of R1234yf to the entire refrigerant and the sound velocity c [mm / s]. In FIG. 9, the solid line represents c1 = −776α + 215700. The broken line represents c2 = −757α + 211500. 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. Moreover, 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.

Based on the above description, the conditional expression where the resonance frequency f “Hz” of the second order, the third order, or the fourth order (n = 2, 3, 4) becomes f <900 [Hz] or 1000 [Hz] <f is It is determined as follows.

In the compressor 100, 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]. When 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 α [wt%], any one of the following formulas 3 to 6 Satisfies one expression.

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.

In the compressor 100, the ratio α [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 By satisfying any one of the formulas (6) to (6), 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.

Embodiment 2.
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. When a plurality of supply pipe connection portions 14a1 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. When a plurality of suction pipe connection portions 14b1 are provided, 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 α [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. 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.

Further, the compressor 100 is configured so that the ratio α [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. By satisfying any one of the expressions 3 to 6, 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. As shown in FIG. 13, in the compressor 100, 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. Alternatively, in the compressor 100, 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 α [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. In the compressor 100, 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. Alternatively, in the compressor 100, 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. In the compressor 100, 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.

Further, since the R1234yf refrigerant has a large flow rate for operating the compressor 100, the amount of liquid refrigerant flowing from the suction muffler 14 to the compression mechanism unit 3 may increase. In addition, when the liquid refrigerant flows into the compression mechanism unit 3, a liquid compression state occurs, which may cause a compressor failure. Therefore, 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 embodiment of the present invention is not limited to the above-described

Embodiments

1 and 2, and various modifications can be added. For example, 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.

DESCRIPTION OF SYMBOLS 1 Airtight container, 2 Electric motor part, 3 Compression mechanism part, 4 Discharge pipe, 12 Upper airtight container, 13 Lower airtight container, 14 Inhalation muffler, 14a Top part, 14a1 Supply pipe connection part, 14b Bottom part, 14b1 Intake pipe connection part, 15 Suction tube, 16 airtight terminal, 17 rod, 18 lead wire, 19 supply tube, 21 stator, 22 rotor, 31 rotating shaft, 31a main shaft portion, 31b sub shaft portion, 31c eccentric shaft portion, 31d eccentric shaft portion, 32 Main bearing, 33 secondary bearing, 34a first cylindrical cylinder, 34b second cylindrical cylinder, 35a first rolling piston, 35b second rolling piston, 36 partition plate, 37a first vane, 37b second vane , 40a chamber, 40b chamber, 41a first vane sliding groove, 41b second vane sliding groove, 2a first suction port, 42b second suction port, 100 compressor.

Claims

A sealed container with a built-in compression mechanism,
A suction pipe connected to the compression mechanism;
A suction muffler connected to the suction pipe;
A supply pipe connected to the suction muffler for supplying refrigerant to the suction muffler;
With
In the inner space of the suction muffler, a distance L “mm” between the supply pipe connection portion and the suction pipe connection portion of the suction muffler is formed in a range of 100 [mm] <L <300 [mm]. ,
When a mixed refrigerant containing R1234yf refrigerant and R32 refrigerant as main components is an operating refrigerant and the ratio of R1234yf to the entire operating refrigerant is α [wt%], one of the following formulas 3 to 6 is satisfied. Compressor.
2. The compressor according to claim 1, wherein at least one of the supply pipe connection portion and the suction pipe connection portion is arranged to be eccentric with respect to a longitudinal axis of the suction muffler.
3. The suction muffler is formed in an oval shape in a plan view, and at least one of the supply pipe connection portion and the suction pipe connection portion is disposed along a long axis of the oval shape. The compressor described.
3. The suction muffler is formed in an oval shape in a plan view, and the supply pipe connection portion and the suction pipe connection portion are arranged side by side along a long axis of the oval shape. The compressor described.
The compressor according to any one of claims 1 to 4, wherein the working refrigerant has a GWP of less than 500.
The compressor according to any one of claims 1 to 5, wherein the working refrigerant has a GWP of less than 100.