WO2007010668A1 - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
WO2007010668A1
WO2007010668A1 PCT/JP2006/309931 JP2006309931W WO2007010668A1 WO 2007010668 A1 WO2007010668 A1 WO 2007010668A1 JP 2006309931 W JP2006309931 W JP 2006309931W WO 2007010668 A1 WO2007010668 A1 WO 2007010668A1
Authority
WO
WIPO (PCT)
Prior art keywords
tail pipe
discharge cover
tail
discharge
pipe
Prior art date
Application number
PCT/JP2006/309931
Other languages
French (fr)
Japanese (ja)
Inventor
Satoshi Ishikawa
Kazutaka Hori
Original Assignee
Daikin Industries, Ltd.
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 Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Publication of WO2007010668A1 publication Critical patent/WO2007010668A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • 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
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps

Definitions

  • the present invention relates to a rotary compressor in which a compression mechanism and an electric motor are housed in a hermetic casing, and in particular, a muffler provided in a high-pressure dome-shaped rotary compressor in which the inside of the casing becomes a discharge pressure of the compressor. It relates to the structure of the mechanism.
  • a compressor of this type a compression mechanism and an electric motor are provided in a sealed casing, and a suction pipe fixed to the casing communicates with an intake port of the compression mechanism and is discharged from the compression mechanism. After the filled high-pressure gas is filled in the casing, there is one that is discharged outside the discharge pipe force provided in the casing (for example, see Patent Document 1).
  • the casing is composed of a vertically long cylindrical body, an upper end panel fixed to the upper end of the body part, and a lower end panel fixed to the lower end of the body part. Consists of sealed containers.
  • the electric motor is composed of a stator and a rotor, and the stator is fixed to the casing at an intermediate position in the vertical direction of the casing.
  • the compression mechanism is fixed to the casing on the space side below the motor, and is connected to the motor port via a drive shaft.
  • the casing body is provided with a suction pipe connected to the compression mechanism, and the upper end plate is provided with a discharge pipe that opens in a space above the motor.
  • the compression mechanism is provided with a discharge port that discharges high-pressure gas upward and a discharge cover (muffler) that covers the discharge port. Further, the discharge cover is provided with a thin tube (tail tube) that passes through the discharge cover in parallel with the axial direction of the drive shaft, and a silencer mechanism is constituted by the discharge cover and the tail tube.
  • a discharge cover is provided with a thin tube (tail tube) that passes through the discharge cover in parallel with the axial direction of the drive shaft, and a silencer mechanism is constituted by the discharge cover and the tail tube.
  • Patent Document 1 Japanese Patent Laid-Open No. 63-36092
  • the tail tube is provided in parallel with the axial direction of the drive shaft, and the discharge gas is blown out toward the electric motor. Therefore, the tail pipe is longitudinally caused by the pressure wave of the discharge gas in the acoustic space in the casing.
  • the resonance mode in the direction (axial direction of the drive shaft) is likely to occur. For this reason, there has been a problem that the motor's mouth vibrates up and down and noise is caused by this vibration.
  • the tail pipe is provided parallel to the axial direction of the drive shaft, the length of the tail pipe cannot be made sufficiently long due to the close positional relationship between the compression mechanism and the electric motor. There was a problem with a small effect.
  • the present invention has been made in view of the points to be applied, and an object of the present invention is to provide vibration of an electric motor that can occur when a silencing mechanism using a tail pipe is provided in a high-pressure dome-type rotary compressor.
  • the aim is to reduce noise and increase the resonance effect of the tail tube.
  • a first invention includes a compression mechanism (20) for compressing and discharging a gas, an electric motor (30) for driving the compression mechanism (20), and the compression mechanism (20) and the electric motor (30).
  • this rotary compressor is characterized in that the tail pipe (45) is arranged such that a longitudinal line segment thereof is along a plane substantially parallel to the end face of the electric motor (30). RU
  • the tail pipe (45) of the silencer mechanism (46) is arranged so as to be substantially parallel to the end face of the electric motor (30), so that the compression mechanism (20) and the electric motor ( Regardless of the positional relationship of 30), the tail pipe (45) can be made sufficiently long. Then, the discharge gas is blown out from the tail pipe (45) substantially parallel to the end face of the electric motor (30), and the pulsation noise of the discharge gas is reduced by the resonance effect when the discharge gas passes through the tail pipe (45). Also, since the discharge gas is blown out almost parallel to the end face of the electric motor (30), resonance in the longitudinal direction (axial direction of the drive shaft) due to the pressure wave of the discharge gas in the acoustic space in the casing (10). Mode is unlikely to occur.
  • the discharge cover (44) includes a disc-shaped end plate (42) and the end plate (42).
  • a cylindrical side plate (43) connected to the peripheral edge of the end plate (42), and the tail tube (45) is disposed along a line segment extending in a substantially radial direction of the discharge cover (44). It is characterized by being.
  • the discharge cover (44) has a disc-shaped end plate (42) and a cylindrical side plate (43) connected to the peripheral edge of the end plate (42). ), And the tail pipe (45) is arranged along a line segment extending in a substantially tangential direction of the discharge cover (44).
  • the tail tube (45) is provided so as to straddle from the radially inner side to the radially outer side of the side plate (43) of the discharge cover (44). It is characterized by!
  • the fifth invention is the first, second or third invention, wherein the tail tube (45) is provided only on the radially inner side of the side plate (43) of the discharge cover (44)! It is characterized by that.
  • the sixth invention is the first, second or third invention, wherein the tail tube (45) is provided only on the radially outer side of the side plate (43) of the discharge cover (44)! Characterized by that! /
  • a seventh invention is the first, second or third invention, wherein the discharge cover in the tail pipe (45) is provided. It is characterized in that a curved portion (45c) is provided in a portion located on the radially outer side of one (44) side plate (43).
  • the curved portion (45c) can be formed in an arbitrary shape such as a substantially “U” shape, a “U” shape, or a “let” shape.
  • the curved portion (45c) is provided in a portion located on the radially outer side of the side plate (43) of the discharge cover (44) in the tail tube (45), so that the tail tube (45 ) To the inner surface of the compressor casing (10). Therefore, the pressure wave of the discharge gas blown out from the tail pipe (45) is likely to be attenuated before it hits the casing (10).
  • the tail tube (45) includes the tail tube.
  • a plurality of pores (45a) penetrating the tube wall of (45) are formed !.
  • the pressure wave of the discharge gas becomes small due to the pressure loss when the discharge gas passing through the tail pipe (45) passes through the pores (45a).
  • a ninth invention is characterized in that, in any one of the first to eighth inventions, a plurality of tail tubes (45) are attached to the discharge cover (44).
  • a plurality of tail pipes (45) are attached to the discharge cover (44).
  • the tail pipe (45) is formed integrally with the structural member (22) of the compressor structure (20) !, It is characterized by that.
  • the pulsation noise is reduced by the resonance effect when the discharge gas passes through 45).
  • the eleventh invention is characterized in that, in any one of the first to tenth inventions, the entire tail pipe (45) is housed in a space (S1) in the casing (10). Yes.
  • the reduction of pulsating noise by the tail pipe (45) is completed inside the casing (10).
  • the discharge cover (44) including the end plate (42) and the side plate (43) so as to cover the discharge port (29) provided in the compression mechanism (20) and the discharge cover ( 44)
  • a rotary compressor equipped with a silencing mechanism (46) consisting of a tail pipe (45) that allows gas to pass outside!
  • the tail pipe (45) is connected to its longitudinal direction line. Place the minute along the plane that is almost parallel to the end face of the motor (30)! / The Therefore, since the tail tube (45) can be made sufficiently long, the resonance effect can be enhanced.
  • the tail pipe (45) arranged along the line segment extending in the substantially radial direction of the discharge cover (44)? It can be selected whether the discharge cover (44) is arranged along a line segment extending in the substantially tangential direction.
  • the tail pipe (45) is provided so as to straddle the radially inner side of the side plate (43) of the discharge cover (44), the tail pipe (45) Can be made relatively long. Therefore, the resonance frequency can be set to a relatively low frequency.
  • the tail tube (45) is provided only on the radially inner side or only on the radially outer side of the side plate (43) of the discharge cover (44).
  • the length of (45) can be made relatively short. Therefore, contrary to the fourth invention, the resonance frequency can be set to a relatively high frequency.
  • the fourth to sixth inventions may be appropriately selected according to the resonance frequency to be set.
  • a curved portion such as a substantially U-shape is provided in a portion of the tail tube (45) located on the radially outer side of the side plate (43) of the discharge cover (44).
  • the pressure wave of the discharge gas blown off the tail pipe (45) hits the casing (10). It is easy to attenuate, and the noise reduction effect is enhanced.
  • the eighth aspect of the invention since the plurality of pores (45a) penetrating the tube wall of the tail pipe (45) are provided, the discharge gas passing through the tail pipe (45) ), The pressure wave of the discharge gas becomes smaller due to the pressure loss. Therefore, the noise reduction effect is enhanced.
  • a plurality of tail pipes (45) are attached to the discharge cover (44), so that it becomes easy to arbitrarily set the resonance frequency by the tail pipe (45), and the sound is muted. Increase design freedom.
  • the tail tube (45) is integrated with the structural member (22) of the compression mechanism (20).
  • the rigidity of the portion holding the tail pipe (45) increases, and the tail pipe (45) itself vibrates. Therefore, the noise reduction effect can be enhanced.
  • Japanese Patent Laid-Open No. 61-66888 discloses that a part of the tail pipe is taken out of the casing of the compressor and the tip of the tail pipe is reinserted into the casing. There is a type that discharges gas into the casing.
  • the productivity is poor and the cost is high.
  • the tail tube (45) can be formed integrally with the discharge cover (44) and the compression mechanism (20), the productivity is good and the cost is low.
  • FIG. 1 is a longitudinal sectional view of a compressor according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view showing a compression mechanism of the compressor of FIG.
  • Fig. 3 is a longitudinal sectional view of the silencing mechanism.
  • FIG. 4 is a plan view of the silencer mechanism.
  • FIG. 5 is a plan view of a silencing mechanism according to Modification 1.
  • FIG. 6 is a cross-sectional view of a silencing mechanism according to Modification 2.
  • FIG. 7 is a cross-sectional view of a silencing mechanism according to Modification 3.
  • FIG. 8 is a cross-sectional view of a silencing mechanism according to Modification 4.
  • FIG. 9 is a cross-sectional view of a silencing mechanism according to Modification 5.
  • FIG. 10 is a cross-sectional view of a silencing mechanism according to Modification 6.
  • FIG. 11 is a cross-sectional view of a silencing mechanism according to Modification 7.
  • FIG. 12 is a cross-sectional view of a silencing mechanism according to Modification 8.
  • FIG. 13 is a cross-sectional view of a silencing mechanism according to Modification 9.
  • FIG. 14 is a cross-sectional view of a silencing mechanism according to another modification.
  • FIG. 15 is a cross-sectional view of a silencing mechanism according to still another modification.
  • the compressor of this embodiment includes a so-called rotary piston type compressor (1).
  • the compressor (1) includes a casing (10) in which a compression mechanism (20) that compresses and discharges a gas and an electric motor (30) that drives the compression mechanism (20) are housed. It is configured.
  • the compressor (1) is configured as a variable capacity compressor in which the capacity is variable stepwise or continuously by the electric motor (30) force S inverter control.
  • this compressor (1) drives a compression mechanism (20) by an electric motor (30), for example, sucks and compresses a refrigerant, then discharges it and circulates it in a refrigerant circuit.
  • the casing (10) includes a cylindrical body (11), an upper end plate (12) joined to the upper end opening of the body (11), and a lower end opening of the body (11).
  • the lower end plate (13) joined to the bottom is formed into a vertically long cylindrical sealed container.
  • the space in the casing (10) is partitioned into a first space (S1) and a second space (S2) positioned above and below the electric motor (30).
  • the first space (S1) is disposed below the electric motor (30)
  • the second space (S2) is disposed above the electric motor (30).
  • the compression mechanism (20) is arranged in the first space (SI).
  • the casing (10) is provided with a suction pipe (14) at the lower part of the body part (11), and an upper end plate (12) is provided with a discharge pipe (15).
  • the suction pipe (14) communicates with the suction side of the compression mechanism (20) via the casing (10), and the discharge pipe (15) opens to a space in the casing (10). It is fixed to the upper end plate (12). That is, the suction pipe (14) is provided at a position on the first space (S1) side in the casing (10), and the discharge pipe (15) is provided at a position on the second space (S2) side in the casing (10). Is provided.
  • An accumulator (16) is connected to the suction pipe (14).
  • the compression mechanism (20) includes a cylinder (21), a front head (22), a rear head (23), and a rotating piston (24), and a front head ( 22) Force The rear head (23) is fixed at the lower end.
  • the cylinder (21) is formed in a thick cylindrical shape.
  • a cylindrical cylinder chamber (25) is defined between the inner peripheral surface of the cylinder (21), the lower end surface of the front head (22), and the upper end surface of the rear head (23).
  • the cylinder chamber (25) is configured such that the rotating piston (24) performs an eccentric rotation operation in the cylinder chamber (25).
  • the electric motor (30) includes a stator (31) and a rotor (32).
  • a drive shaft (33) is coupled to the rotor (32).
  • the drive shaft (33) passes through the center of the casing (10) and penetrates the cylinder chamber (25) in the vertical direction.
  • the front head (22) and rear head (23) are formed with bearing portions (22a, 23a) for supporting the drive shaft (33), respectively.
  • the drive shaft (33) includes a main body (33b) and an eccentric part (33a) positioned in the cylinder chamber (25).
  • the eccentric portion (33a) is formed with a larger diameter than the main body portion (33b), and the rotational center force of the drive shaft (33) is also eccentric by a predetermined amount.
  • a rotating piston (24) of the compression mechanism (20) is attached to the eccentric part (33a).
  • the rotary piston (24) is formed in an annular shape, and its outer peripheral surface is formed so as to substantially contact with the inner peripheral surface of the cylinder (21) at one point.
  • a blade groove (21a) is formed in the cylinder (21) along the radial direction of the cylinder (21).
  • the blade groove (21a) has a blade (26) formed in a rectangular plate shape. It is mounted so that it can slide in the radial direction of the cylinder (21).
  • the blade (26) is urged radially inward by a spring (27) provided in the blade groove (21a), and the tip always contacts the outer peripheral surface of the rotary piston (24)! /
  • the blade (26) has a cylinder chamber (25) between the inner peripheral surface of the cylinder (21) and the outer peripheral surface of the rotary piston (24) as a suction chamber (25a) and a compression chamber (25b). It is partitioned.
  • the cylinder (21) passes through the cylinder (21) from the outer circumferential surface to the inner circumferential surface in the radial direction, and communicates the suction pipe (14) and the suction chamber (25a). Is formed.
  • the front head (22) is formed with a discharge port (29) penetrating in the axial direction of the drive shaft (33) and communicating the compression chamber (25b) and the space in the casing (10). Yes.
  • the front head (22) is provided with a discharge valve mechanism (40) for opening and closing the discharge port (29).
  • the discharge valve mechanism (40) includes a reed valve (41) and a valve presser (not shown) that regulates the amount of deflection of the reed valve (41).
  • the valve presser is stacked from above, and is sandwiched between the front head (22) and the valve presser.
  • the reed valve (41) and the valve retainer are fixed to the front head (22) by fastening bolts on the base end side (not shown).
  • a discharge cover (44) composed of an end plate (42) and a side plate (43) is attached to the front head (22) so as to cover the discharge port (29) provided in the compression mechanism (20). It has been.
  • a tail pipe (45) that allows gas to pass outside the intermediate force of the discharge cover (44) is fixed to the discharge cover (44).
  • the discharge cover (44) and the tail pipe (45) constitute a resonance type silencing mechanism (46).
  • the tail pipe (45) is arranged so that its longitudinal line segment is along a plane substantially parallel to the end face of the electric motor (30).
  • the discharge cover (44) includes a disc-shaped end plate (42) and a cylindrical side plate (43) connected to the peripheral edge of the end plate (42).
  • the tail pipe (45) is disposed along a line segment extending in a substantially radial direction of the discharge cover (44), as shown in FIG. 3 which is an enlarged sectional view of the silencer mechanism (46) and FIG. 4 which is a plan view. It has been. Further, the tail pipe (45) is provided from the radially inner side to the radially outer side of the side plate (43) of the discharge cover (44). Therefore, the tail tube (45) can be set to a sufficient length compared to the case where it is provided in parallel with the axial direction of the drive shaft (33).
  • It can be 42.5 (mm) or less.
  • the compression operation of the compression mechanism (20) will be described with reference to FIG.
  • the rotating piston (24) rotates clockwise (clockwise) in the figure by driving the electric motor (30)
  • the volume of the suction chamber (25a) increases according to the rotation, and a low-pressure refrigerant is introduced into the suction chamber (25a). Is sucked through the suction port (28).
  • the refrigerant is sucked into the suction chamber (25a) by rotating the rotary piston (2 4) eccentrically in the cylinder chamber (25) so that the cylinder (21) and the rotary piston (24) are located just to the right of the suction port (28). Continue until contact is made.
  • a compression chamber (25b) in which the refrigerant is compressed is formed.
  • a new suction chamber (25a) is formed next to the compression chamber (25b), and the refrigerant is repeatedly sucked into the suction chamber (25a).
  • the refrigerant in the compression chamber (25b) is compressed as the volume of the compression chamber (25b) decreases as the rotary piston (24) rotates.
  • the pressure acts on the reed valve (41) to open the discharge port (29).
  • the refrigerant in the compression chamber (25b) is discharged from the discharge port (29) into the discharge cover (44).
  • the reed valve (41) closes the discharge port (29) by its panel power. In this way, refrigerant suction, compression, and discharge are repeated.
  • Compression mechanism (20) force The discharged high-pressure refrigerant is blown out of the discharge cover (44) through the tail pipe (45) and into the first space (S1) of the casing (10). And the discharge gas is tail pipe (45) The pulsating noise is absorbed by the resonance effect when passing through.
  • the discharge gas is blown out in a direction substantially parallel to the end surface of the tail pipe (45) force electric motor (30). Therefore, the resonance mode in the vertical direction (axial direction of the drive shaft) due to the pressure wave of the discharge gas is unlikely to occur in the acoustic space in the casing (10). For this reason, the rotor (32) of the electric motor (30) is less likely to vibrate up and down.
  • the discharge cover (44) including the end plate (42) and the side plate (43) so as to cover the discharge port (29) provided in the compression mechanism (20), and the discharge cover (44).
  • a rotary compressor (1) equipped with a silencing mechanism (46) consisting of a tail pipe (45) that allows gas to pass outside from the cover (44) the tail pipe (45)
  • the direction line segment is arranged along a plane substantially parallel to the end face of the electric motor (30). Therefore, regardless of the positional relationship between the compression mechanism (20) and the electric motor (30), the tail pipe (45) can be made sufficiently long, so that the resonance effect by the tail pipe can be enhanced.
  • the tail pipe (45) is provided to straddle the radial inner side radial force of the side plate (43) of the discharge cover (44), the length of the tail pipe (45) is relatively increased. Since the resonance frequency can be increased, the resonance frequency can be set to a relatively low frequency.
  • tail pipe (45) since the entire tail pipe (45) is housed in the space (S1) in the casing (10), the reduction of pulsation noise by the tail pipe (45) is reduced by the casing (10). Since the tail pipe (45) can be formed integrally with the discharge cover (44) and the compression mechanism (20), the productivity is good and the cost is low.
  • FIG. 5 shows a plan view of the muffler mechanism (46) according to the first modification.
  • the discharge force bar (44) force has a disc-shaped end plate (42) and a cylindrical side plate (43) connected to the peripheral edge of the end plate (42).
  • the tail tube (45) is short for the discharge cover (44) It is arranged along a line segment extending in the tangential direction.
  • the structure of the above embodiment in which the tail pipe (45) is arranged along the line extending substantially in the radial direction of the discharge cover (44) is selected, or the tail pipe ( 45)
  • the structure of Modification 1 can be selected that is arranged along a line extending in the substantially tangential direction of the discharge cover (44).
  • the tail tube (45) may be slightly inclined with respect to these line segments.
  • FIG. 6 shows a cross-sectional view of the silencing mechanism (46) according to the second modification.
  • the tail pipe (45) is provided only on the radially inner side of the side plate (43) of the discharge cover (44).
  • Other structures are the same as those in the above embodiment.
  • the length of the tail tube (45) can be made relatively short as compared to the above embodiment, so that the resonance frequency can be set to a relatively high frequency.
  • FIG. 7 shows a cross-sectional view of the silencer mechanism (46) according to the third modification.
  • the tail pipe (45) is provided only on the radially outer side of the side plate (43) of the discharge cover (44).
  • Other structures are the same as those in the above embodiment.
  • the resonance frequency can be set to a relatively high frequency as in the second modification. .
  • FIG. 8 shows a cross-sectional view of the silencing mechanism (46) according to the fourth modification.
  • the tail tube (45) has a substantially U-shaped bent portion (45c) that is located on the radially outer side of the side plate (43) of the discharge cover (44).
  • Other structures are the same as those in the above embodiment.
  • FIG. 9 shows a cross-sectional view of the silencing mechanism (46) according to the fifth modification.
  • the tail tube (45) is formed with a plurality of pores (45a) penetrating the tube wall of the tail tube (45).
  • Other structures are the same as those in the above embodiment.
  • FIG. 10 shows a cross-sectional view of the silencer mechanism (46) according to Modification 6.
  • a plurality of tail tubes (45) are attached to the discharge force bar (44).
  • Other structures are the same as those in the above embodiment.
  • FIG. 11 shows a cross-sectional view of the silencing mechanism (46) according to the seventh modification.
  • the tail pipe (45) is formed by integrally forging the front head (22), which is a structural member of the compression mechanism (20), and adding a horizontal hole to the side plate ( It is provided only on the radially inner side of 43).
  • the discharge cover (44) is provided with a lateral hole (44a).
  • Other structures are the same as those in the above embodiment. If the tail pipe (45) is formed integrally with the structural member (22) of the compression mechanism (20) in this way, the rigidity of the tail pipe (45) is increased and the tail pipe (45) itself is less likely to vibrate. Therefore, the noise reduction effect can be enhanced.
  • FIG. 12 shows a cross-sectional view of the muffler mechanism (46) according to Modification 8.
  • This example is an example in which the length of the tail tube (45) is extended by inserting the tube (45b) into the lateral hole of the tail tube (45) in the modified example 7 of FIG.
  • Other structures are the same as those of the seventh modification.
  • the noise reduction effect can be enhanced by increasing the rigidity of the tail pipe (45) itself, and the resonance frequency can be set to a lower frequency by extending the length of the tail pipe (45). it can.
  • FIG. 13 shows a cross-sectional view of the silencing mechanism (46) according to Modification 9.
  • the extension part of the tail pipe (45) is also integrally formed in the modified example 8 of FIG. 12, and the discharge cover (44) is viewed from the side instead of the side hole (44a) as shown in FIG.
  • An inverted U-shaped notch (44b) is provided.
  • the other structure is the same as that of Modification 8. Even in this way, the noise reduction effect can be enhanced by increasing the rigidity of the tail pipe (45) itself, and the resonance frequency can be set to a lower frequency by extending the length of the tail pipe (45). can do. [0075] ⁇ Other Embodiments >>
  • the compression mechanism (20) is arranged in the space below the electric motor (30) in the casing (10), but conversely in the space above the electric motor (30). Place the compression mechanism (20).
  • the suction pipe (14) is directly connected to the suction side of the compressor structure (20) via the body (11) of the casing (10). It is also possible to provide a buffer space on the suction side in the interior) and allow the compression mechanism (20) to suck the suction gas through the buffer space.
  • the curved portion (45c) is provided so that the tail tube (45) is substantially U-shaped.
  • the example in FIG. 14 is an example in which the curved portion (45c) is formed in a “U” shape
  • the example in FIG. 15 is an example in which the curved portion (45c) is formed in a “L” shape.
  • the noise reduction effect is enhanced.
  • the present invention is not limited to the rotary piston type compressor (1), and may be applied to other types of compressors such as a swing type.
  • the present invention relates to a silencing mechanism provided in a high-pressure dome-shaped rotary compressor in which a compression mechanism and an electric motor are housed in a sealed casing, and the inside of the casing becomes the discharge pressure of the compressor.
  • a silencing mechanism provided in a high-pressure dome-shaped rotary compressor in which a compression mechanism and an electric motor are housed in a sealed casing, and the inside of the casing becomes the discharge pressure of the compressor.

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

Abstract

To reduce a vibrational noise of an electric motor (30) that can occur when a noise reduction mechanism (46) having a tail pipe (45) is used in a high-pressure dome rotary compressor (1). The tail pipe (45) is placed so that its longitudinal axis is along a surface substantially in parallel to an end surface of the electric motor (30).

Description

明 細 書  Specification
回転式圧縮機  Rotary compressor
技術分野  Technical field
[0001] 本発明は、密閉ケーシング内に圧縮機構と電動機が収納された回転式圧縮機に 関し、特に、ケーシング内が圧縮機の吐出圧力になる高圧ドーム形の回転式圧縮機 に設けられる消音機構の構造に関するものである。  TECHNICAL FIELD [0001] The present invention relates to a rotary compressor in which a compression mechanism and an electric motor are housed in a hermetic casing, and in particular, a muffler provided in a high-pressure dome-shaped rotary compressor in which the inside of the casing becomes a discharge pressure of the compressor. It relates to the structure of the mechanism.
背景技術  Background art
[0002] 従来より、この種の圧縮機として、密閉型のケーシング内に圧縮機構と電動機とが 設けられ、ケーシングに固定された吸入管が圧縮機構の吸入口に連通するとともに、 圧縮機構から吐出された高圧ガスがケーシング内に充満した後、該ケーシングに設 けられた吐出管力 外部へ吐出されるものがある（例えば、特許文献 1参照)。  Conventionally, as a compressor of this type, a compression mechanism and an electric motor are provided in a sealed casing, and a suction pipe fixed to the casing communicates with an intake port of the compression mechanism and is discharged from the compression mechanism. After the filled high-pressure gas is filled in the casing, there is one that is discharged outside the discharge pipe force provided in the casing (for example, see Patent Document 1).
[0003] この特許文献 1の圧縮機では、ケーシングは、縦長円筒状の胴部と、胴部の上端に 固定された上部鏡板と、胴部の下端に固定された下部鏡板とから構成された密閉容 器により構成されている。電動機はステータとロータとから構成され、ステータがケ一 シングの上下方向の中間位置にお 1、て該ケーシングに固定されて 、る。圧縮機構は 上記電動機の下方の空間側でケーシングに固定され、駆動軸を介して電動機の口 ータと連結されている。そして、ケーシングの胴部には上記圧縮機構に接続される吸 入管が設けられる一方、上部鏡板には電動機の上方の空間に開口した吐出管が設 けられている。  [0003] In the compressor of Patent Document 1, the casing is composed of a vertically long cylindrical body, an upper end panel fixed to the upper end of the body part, and a lower end panel fixed to the lower end of the body part. Consists of sealed containers. The electric motor is composed of a stator and a rotor, and the stator is fixed to the casing at an intermediate position in the vertical direction of the casing. The compression mechanism is fixed to the casing on the space side below the motor, and is connected to the motor port via a drive shaft. The casing body is provided with a suction pipe connected to the compression mechanism, and the upper end plate is provided with a discharge pipe that opens in a space above the motor.
[0004] 圧縮機構には、上向きに高圧ガスを吐出する吐出口と、この吐出口を覆う吐出カバ 一（マフラ）が設けられている。また、吐出カバーには、該吐出カバーを駆動軸の軸方 向と平行に貫通する細い管 (尾管）が設けられていて、吐出カバーと尾管により消音 機構が構成されている。この構造では、圧縮機構から吐出される高圧ガスの脈動によ る騒音を、該高圧ガスが尾管を通る際の共鳴効果で低減するようにして 、る。  [0004] The compression mechanism is provided with a discharge port that discharges high-pressure gas upward and a discharge cover (muffler) that covers the discharge port. Further, the discharge cover is provided with a thin tube (tail tube) that passes through the discharge cover in parallel with the axial direction of the drive shaft, and a silencer mechanism is constituted by the discharge cover and the tail tube. In this structure, noise due to pulsation of the high-pressure gas discharged from the compression mechanism is reduced by a resonance effect when the high-pressure gas passes through the tail pipe.
特許文献 1：特開昭 63 - 36092号公報  Patent Document 1: Japanese Patent Laid-Open No. 63-36092
発明の開示  Disclosure of the invention
発明が解決しょうとする課題 [0005] しかし、上記の構造では、尾管を駆動軸の軸方向と平行に設けており、吐出ガスが 電動機に向かって吹き出されるため、ケーシング内の音響空間で吐出ガスの圧力波 により縦方向（駆動軸の軸方向）の共鳴モードが生じやすい。そのため、電動機の口 ータが上下に振動し、この振動に起因する騒音が発生する問題があった。また、尾管 を駆動軸の軸方向と平行に設けると、圧縮機構と電動機とが接近した位置関係にあ るために尾管の長さを十分に長くすることができず、尾管による共鳴効果も小さい問 題があった。 Problems to be solved by the invention [0005] However, in the above structure, the tail tube is provided in parallel with the axial direction of the drive shaft, and the discharge gas is blown out toward the electric motor. Therefore, the tail pipe is longitudinally caused by the pressure wave of the discharge gas in the acoustic space in the casing. The resonance mode in the direction (axial direction of the drive shaft) is likely to occur. For this reason, there has been a problem that the motor's mouth vibrates up and down and noise is caused by this vibration. In addition, if the tail pipe is provided parallel to the axial direction of the drive shaft, the length of the tail pipe cannot be made sufficiently long due to the close positional relationship between the compression mechanism and the electric motor. There was a problem with a small effect.
[0006] 本発明は、力かる点に鑑みてなされたものであり、その目的は、高圧ドーム形の回 転式圧縮機で尾管を用いた消音機構を設けた場合に生じ得る電動機の振動騒音を 低減するとともに、尾管による共鳴効果も高められるようにすることである。  [0006] The present invention has been made in view of the points to be applied, and an object of the present invention is to provide vibration of an electric motor that can occur when a silencing mechanism using a tail pipe is provided in a high-pressure dome-type rotary compressor. The aim is to reduce noise and increase the resonance effect of the tail tube.
課題を解決するための手段  Means for solving the problem
[0007] 第 1の発明は、ガスを圧縮して吐出する圧縮機構 (20)と、該圧縮機構 (20)を駆動 する電動機 (30)と、該圧縮機構 (20)及び電動機 (30)を収納するケーシング (10)と、 圧縮機構 (20)の吸入側に連通する吸入管（14)と、該ケーシング（10)内の空間に開 口するようにケーシング（10)に設けられた吐出管（15)と、圧縮機構 (20)に設けられ た吐出口（29)を覆うように端板 (42)と側板 (43)とからなる吐出カバー (44)と該吐出 カバー (44)の中から外へガスを通過させる尾管 (45)とからなる消音機構 (46)とを備 えた回転式圧縮機を前提として!/ヽる。 [0007] A first invention includes a compression mechanism (20) for compressing and discharging a gas, an electric motor (30) for driving the compression mechanism (20), and the compression mechanism (20) and the electric motor (30). A casing (10) for storage, a suction pipe (14) communicating with the suction side of the compression mechanism (20), and a discharge pipe provided in the casing (10) so as to open into a space in the casing (10) (15) and, in the end plate so as to cover the discharge port provided in the compression mechanism (20) (29) (42) and discharge cover consisting side plate (43) (44) and said discharge out cover (44) Assuming a rotary compressor equipped with a silencer mechanism (46) consisting of a tail pipe (45) that allows gas to pass from the outside!
[0008] そして、この回転式圧縮機は、上記尾管 (45)を、その長手方向線分が電動機 (30) の端面と略平行な面に沿うように配置して 、ることを特徴として 、る。  [0008] Then, this rotary compressor is characterized in that the tail pipe (45) is arranged such that a longitudinal line segment thereof is along a plane substantially parallel to the end face of the electric motor (30). RU
[0009] 上記第 1の発明では、消音機構 (46)の尾管 (45)を電動機 (30)の端面と略平行に なるように配置して 、るため、圧縮機構 (20)と電動機 (30)の位置関係に関わらず、 尾管 (45)を十分な長さにすることができる。そして、吐出ガスは尾管 (45)から電動機 (30)の端面とほぼ平行に吹き出され、吐出ガスが尾管 (45)を通る際の共鳴効果で吐 出ガスの脈動騒音が低減される。また、吐出ガスを電動機 (30)の端面とほぼ平行に 吹き出すようにしているため、ケーシング（10)内の音響空間で吐出ガスの圧力波によ る縦方向（駆動軸の軸方向）の共鳴モードは生じにくい。  [0009] In the first invention, the tail pipe (45) of the silencer mechanism (46) is arranged so as to be substantially parallel to the end face of the electric motor (30), so that the compression mechanism (20) and the electric motor ( Regardless of the positional relationship of 30), the tail pipe (45) can be made sufficiently long. Then, the discharge gas is blown out from the tail pipe (45) substantially parallel to the end face of the electric motor (30), and the pulsation noise of the discharge gas is reduced by the resonance effect when the discharge gas passes through the tail pipe (45). Also, since the discharge gas is blown out almost parallel to the end face of the electric motor (30), resonance in the longitudinal direction (axial direction of the drive shaft) due to the pressure wave of the discharge gas in the acoustic space in the casing (10). Mode is unlikely to occur.
[0010] 第 2の発明は、第 1の発明において、吐出カバー (44)が、円板状の端板 (42)と該 端板 (42)の周縁部に連接する円筒状の側板 (43)とを有し、尾管 (45)が、吐出カバ 一 (44)の略径方向にのびる線分に沿って配置されていることを特徴としている。 [0010] In a second aspect based on the first aspect, the discharge cover (44) includes a disc-shaped end plate (42) and the end plate (42). A cylindrical side plate (43) connected to the peripheral edge of the end plate (42), and the tail tube (45) is disposed along a line segment extending in a substantially radial direction of the discharge cover (44). It is characterized by being.
[0011] この第 2の発明では、吐出カバー (44)の略径方向にのびる線分に沿って配置され た尾管 (45)の中を吐出ガスが通るときに、尾管 (45)による共鳴効果で脈動騒音が低 減される。 [0011] In the second aspect of the invention, when the discharge gas passes through the tail pipe (45) arranged along the line extending in the substantially radial direction of the discharge cover (44), the tail pipe (45) Pulsating noise is reduced by the resonance effect.
[0012] 第 3の発明は、第 1の発明において、吐出カバー (44)が、円板状の端板 (42)と該 端板 (42)の周縁部に連接する円筒状の側板 (43)とを有し、尾管 (45)が、吐出カバ 一 (44)の略接線方向にのびる線分に沿って配置されていることを特徴としている。  [0012] In a third aspect based on the first aspect, the discharge cover (44) has a disc-shaped end plate (42) and a cylindrical side plate (43) connected to the peripheral edge of the end plate (42). ), And the tail pipe (45) is arranged along a line segment extending in a substantially tangential direction of the discharge cover (44).
[0013] この第 3の発明では、吐出カバー (44)の略接線方向にのびる線分に沿って配置さ れた尾管 (45)の中を吐出ガスが通るときに、尾管 (45)による共鳴効果で脈動騒音が 低減される。  [0013] In this third aspect of the invention, when the discharge gas passes through the tail pipe (45) arranged along the line extending in the substantially tangential direction of the discharge cover (44), the tail pipe (45) The pulsation noise is reduced by the resonance effect caused by.
[0014] 第 4の発明は、第 1,第 2または第 3の発明において、尾管 (45)が吐出カバー (44) の側板 (43)の径方向内側から径方向外側に跨って設けられて!/、ることを特徴として いる。  [0014] In a fourth invention according to the first, second or third invention, the tail tube (45) is provided so as to straddle from the radially inner side to the radially outer side of the side plate (43) of the discharge cover (44). It is characterized by!
[0015] この第 4の発明では、吐出カバー (44)の側板 (43)の径方向内側から径方向外側に 跨って設けられた尾管 (45)の中を吐出ガスが通るときに、尾管 (45)による共鳴効果 で脈動騒音が低減される。  [0015] In the fourth aspect of the invention, when the discharge gas passes through the tail pipe (45) provided from the radially inner side to the radially outer side of the side plate (43) of the discharge cover (44), The pulsation noise is reduced by the resonance effect of the tube (45).
[0016] 第 5の発明は、第 1,第 2または第 3の発明において、尾管 (45)が吐出カバー (44) の側板 (43)の径方向内側にのみ設けられて!/、ることを特徴として 、る。  [0016] The fifth invention is the first, second or third invention, wherein the tail tube (45) is provided only on the radially inner side of the side plate (43) of the discharge cover (44)! It is characterized by that.
[0017] この第 5の発明では、吐出カバー (44)の側板 (43)の径方向内側にのみ設けられた 尾管 (45)の中を吐出ガスが通るときに、尾管 (45)による共鳴効果で脈動騒音が低減 される。  [0017] In the fifth invention, when the discharge gas passes through the tail pipe (45) provided only on the radially inner side of the side plate (43) of the discharge cover (44), the tail pipe (45) The pulsation noise is reduced by the resonance effect.
[0018] 第 6の発明は、第 1,第 2または第 3の発明において、尾管 (45)が吐出カバー (44) の側板 (43)の径方向外側にのみ設けられて!/、ることを特徴として！/、る。  [0018] The sixth invention is the first, second or third invention, wherein the tail tube (45) is provided only on the radially outer side of the side plate (43) of the discharge cover (44)! Characterized by that! /
[0019] この第 6の発明では、吐出カバー (44)の側板 (43)の径方向外側にのみ設けられた 尾管 (45)の中を吐出ガスが通るときに、尾管 (45)による共鳴効果で脈動騒音が低減 される。  [0019] In the sixth aspect of the invention, when the discharge gas passes through the tail pipe (45) provided only on the radially outer side of the side plate (43) of the discharge cover (44), the tail pipe (45) The pulsation noise is reduced by the resonance effect.
[0020] 第 7の発明は、第 1,第 2または第 3の発明において、尾管 (45)における吐出カバ 一 (44)の側板 (43)の径方向外側に位置する部分に曲部 (45c)を備えていることを特 徴としている。この曲部（45c)の形状としては、略「U」字状や「コ」の字状や「レ」の字 状など、任意の形状に形成することができる。 [0020] A seventh invention is the first, second or third invention, wherein the discharge cover in the tail pipe (45) is provided. It is characterized in that a curved portion (45c) is provided in a portion located on the radially outer side of one (44) side plate (43). The curved portion (45c) can be formed in an arbitrary shape such as a substantially “U” shape, a “U” shape, or a “let” shape.
[0021] この第 7の発明では、尾管 (45)における吐出カバー (44)の側板 (43)の径方向外側 に位置する部分に曲部 (45c)を設けたことにより、尾管 (45)の出口端面から圧縮機の ケーシング（10)の内面までの距離を長くすることができる。したがって、尾管 (45)から 吹き出される吐出ガスの圧力波がケーシング（10)に当たるまでに減衰しやすくなる。 [0021] In the seventh aspect of the present invention, the curved portion (45c) is provided in a portion located on the radially outer side of the side plate (43) of the discharge cover (44) in the tail tube (45), so that the tail tube (45 ) To the inner surface of the compressor casing (10). Therefore, the pressure wave of the discharge gas blown out from the tail pipe (45) is likely to be attenuated before it hits the casing (10).
[0022] 第 8の発明は、第 1から第 7の発明のいずれか 1つにおいて、尾管 (45)には該尾管 [0022] In an eighth invention according to any one of the first to seventh inventions, the tail tube (45) includes the tail tube.
(45)の管壁を貫通する複数の細孔 (45a)が形成されて!、ることを特徴として 、る。  A plurality of pores (45a) penetrating the tube wall of (45) are formed !.
[0023] この第 8の発明では、尾管 (45)を通る吐出ガスが細孔 (45a)を通るときの圧力損失 により、吐出ガスの圧力波が小さくなる。 [0023] In the eighth aspect of the invention, the pressure wave of the discharge gas becomes small due to the pressure loss when the discharge gas passing through the tail pipe (45) passes through the pores (45a).
[0024] 第 9の発明は、第 1から第 8の発明のいずれか 1つにおいて、吐出カバー (44)には 複数の尾管 (45)が取り付けられて 、ることを特徴として 、る。 [0024] A ninth invention is characterized in that, in any one of the first to eighth inventions, a plurality of tail tubes (45) are attached to the discharge cover (44).
[0025] この第 9の発明で、吐出カバー (44)に複数の尾管 (45)を取り付けて 、るため、尾管 [0025] In the ninth invention, a plurality of tail pipes (45) are attached to the discharge cover (44).
(45)による共鳴周波数を任意に設定しやすくなる。  It becomes easy to arbitrarily set the resonance frequency according to (45).
[0026] 第 10の発明は、第 1から第 9の発明のいずれか 1つにおいて、尾管 (45)が圧縮機 構 (20)の構造部材 (22)と一体的に形成されて!、ることを特徴として 、る。 [0026] In a tenth aspect of the invention according to any one of the first to ninth aspects, the tail pipe (45) is formed integrally with the structural member (22) of the compressor structure (20) !, It is characterized by that.
[0027] この第 10の発明では、圧縮機構 (20)の構造部材 (22)と一体的に形成された尾管（[0027] In the tenth aspect of the present invention, a tail pipe (integrated with the structural member (22) of the compression mechanism (20) (
45)を吐出ガスが通る際の共鳴効果により、脈動騒音が低減される。 The pulsation noise is reduced by the resonance effect when the discharge gas passes through 45).
[0028] 第 11の発明は、第 1から第 10の発明のいずれか 1つにおいて、尾管 (45)の全体が ケーシング（10)内の空間（S1)に収められていることを特徴としている。 [0028] The eleventh invention is characterized in that, in any one of the first to tenth inventions, the entire tail pipe (45) is housed in a space (S1) in the casing (10). Yes.
[0029] この第 11の発明では、尾管 (45)による脈動騒音の低減がケーシング（10)の内部 で完結する。 In the eleventh aspect of the invention, the reduction of pulsating noise by the tail pipe (45) is completed inside the casing (10).
発明の効果  The invention's effect
[0030] 本発明によれば、圧縮機構 (20)に設けられた吐出口（29)を覆うように端板 (42)と 側板 (43)とからなる吐出カバー (44)と該吐出カバー (44)の中力 外へガスを通過さ せる尾管 (45)とからなる消音機構 (46)を備えた回転式圧縮機にお!、て、上記尾管（ 45)を、その長手方向線分が電動機 (30)の端面と略平行な面に沿うように配置して！/、 る。したがって、尾管 (45)を十分な長さにすることができるので、共鳴効果を高められ る。また、吐出ガスが尾管 (45)力も電動機 (30)の端面とほぼ平行に吹き出されるため 、ケーシング（10)内の音響空間で吐出ガスの圧力波による縦方向の共鳴モードが生 じに《なり、電動機 (30)のロータ（32)が上下に振動しに《なる。したがって、電動 機 (30)のロータ (32)の振動に起因する騒音の発生を低減することができる。 [0030] According to the present invention, the discharge cover (44) including the end plate (42) and the side plate (43) so as to cover the discharge port (29) provided in the compression mechanism (20) and the discharge cover ( 44) In a rotary compressor equipped with a silencing mechanism (46) consisting of a tail pipe (45) that allows gas to pass outside! The tail pipe (45) is connected to its longitudinal direction line. Place the minute along the plane that is almost parallel to the end face of the motor (30)! / The Therefore, since the tail tube (45) can be made sufficiently long, the resonance effect can be enhanced. Also, since the discharge gas is blown out of the tail pipe (45) force almost parallel to the end face of the electric motor (30), a longitudinal resonance mode due to the pressure wave of the discharge gas is generated in the acoustic space in the casing (10). That is, the rotor (32) of the electric motor (30) vibrates up and down. Therefore, the generation of noise due to the vibration of the rotor (32) of the electric motor (30) can be reduced.
[0031] 上記第 2,第 3の発明によれば、圧縮機の内部構造に応じて、尾管 (45)を吐出カバ 一 (44)の略径方向にのびる線分に沿って配置するか、吐出カバー (44)の略接線方 向にのびる線分に沿って配置するかを選択することができる。  [0031] According to the second and third inventions, according to the internal structure of the compressor, is the tail pipe (45) arranged along the line segment extending in the substantially radial direction of the discharge cover (44)? It can be selected whether the discharge cover (44) is arranged along a line segment extending in the substantially tangential direction.
[0032] 上記第 4の発明によれば、尾管 (45)を吐出カバー (44)の側板 (43)の径方向内側 カも径方向外側に跨って設けているため、尾管 (45)の長さを比較的長くすることがで きる。したがって、共鳴周波数を比較的低い周波数に設定することができる。  [0032] According to the fourth aspect of the invention, since the tail pipe (45) is provided so as to straddle the radially inner side of the side plate (43) of the discharge cover (44), the tail pipe (45) Can be made relatively long. Therefore, the resonance frequency can be set to a relatively low frequency.
[0033] 上記第 5,第 6の発明によれば、尾管 (45)を吐出カバー (44)の側板 (43)の径方向 内側のみ、あるいは径方向外側のみに設けているため、尾管 (45)の長さを比較的短 くすることができる。したがって、第 4の発明とは逆に共鳴周波数を比較的高い周波 数に設定することができる。第 4〜第 6の発明は、設定すべき共鳴周波数に応じて適 宜選択すればよい。  [0033] According to the fifth and sixth inventions, the tail tube (45) is provided only on the radially inner side or only on the radially outer side of the side plate (43) of the discharge cover (44). The length of (45) can be made relatively short. Therefore, contrary to the fourth invention, the resonance frequency can be set to a relatively high frequency. The fourth to sixth inventions may be appropriately selected according to the resonance frequency to be set.
[0034] 上記第 7の発明によれば、尾管 (45)における吐出カバー (44)の側板 (43)の径方 向外側に位置する部分に略 U字状などの曲部を設けているので、尾管 (45)の出口 端面から圧縮機のケーシング（10)の内面までの距離が長くなつて、尾管 (45)力 吹 き出される吐出ガスの圧力波がケーシング（10)に当たるまでに減衰しやすくなり、騒 音低減効果が高められる。  [0034] According to the seventh aspect of the present invention, a curved portion such as a substantially U-shape is provided in a portion of the tail tube (45) located on the radially outer side of the side plate (43) of the discharge cover (44). As the distance from the outlet end face of the tail pipe (45) to the inner surface of the compressor casing (10) increases, the pressure wave of the discharge gas blown off the tail pipe (45) hits the casing (10). It is easy to attenuate, and the noise reduction effect is enhanced.
[0035] 上記第 8の発明によれば、尾管 (45)の管壁を貫通する複数の細孔 (45a)を設けて いるので、尾管 (45)を通る吐出ガスが細孔 (45a)を通るときの圧力損失により、吐出 ガスの圧力波が小さくなる。したがって、騒音低減効果が高められる。  [0035] According to the eighth aspect of the invention, since the plurality of pores (45a) penetrating the tube wall of the tail pipe (45) are provided, the discharge gas passing through the tail pipe (45) ), The pressure wave of the discharge gas becomes smaller due to the pressure loss. Therefore, the noise reduction effect is enhanced.
[0036] 上記第 9の発明によれば、吐出カバー (44)に複数の尾管 (45)を取り付けて 、るた め、尾管 (45)による共鳴周波数を任意に設定しやすくなり、消音設計の自由度を高 められる。  [0036] According to the ninth aspect of the present invention, a plurality of tail pipes (45) are attached to the discharge cover (44), so that it becomes easy to arbitrarily set the resonance frequency by the tail pipe (45), and the sound is muted. Increase design freedom.
[0037] 上記第 10の発明によれば、尾管 (45)を圧縮機構 (20)の構造部材 (22)と一体的に 形成しているため、尾管 (45)を保持する部分の剛性が高まり、尾管 (45)自体が振動 しに《なる。そのため、騒音低減効果を高められる。 [0037] According to the tenth aspect of the invention, the tail tube (45) is integrated with the structural member (22) of the compression mechanism (20). As a result, the rigidity of the portion holding the tail pipe (45) increases, and the tail pipe (45) itself vibrates. Therefore, the noise reduction effect can be enhanced.
[0038] 上記第 11の発明に関し、特開昭 61— 66888号公報には、尾管の一部をー且圧 縮機のケーシング外に出し、尾管の先端部を再度ケーシングに挿入してケーシング 内に吐出ガスを吹き出すようにしたものがある。しかし、この構造では、尾管を吐出力 バーや圧縮機構と一体的に形成できないため、製造性が悪く高コストである。これに 対して、上記第 11の発明によれば、尾管 (45)を吐出カバー (44)や圧縮機構 (20)と 一体的に形成できるため、製造性が良く低コストである。 [0038] With respect to the eleventh aspect of the invention, Japanese Patent Laid-Open No. 61-66888 discloses that a part of the tail pipe is taken out of the casing of the compressor and the tip of the tail pipe is reinserted into the casing. There is a type that discharges gas into the casing. However, in this structure, since the tail tube cannot be formed integrally with the discharge force bar and the compression mechanism, the productivity is poor and the cost is high. On the other hand, according to the eleventh aspect of the invention, since the tail tube (45) can be formed integrally with the discharge cover (44) and the compression mechanism (20), the productivity is good and the cost is low.
図面の簡単な説明  Brief Description of Drawings
[0039] [図 1]図 1は、本発明の実施形態に係る圧縮機の縦断面図である。 FIG. 1 is a longitudinal sectional view of a compressor according to an embodiment of the present invention.
[図 2]図 2は、図 1の圧縮機の圧縮機構を示す横断面図である。  FIG. 2 is a cross-sectional view showing a compression mechanism of the compressor of FIG.
[図 3]図 3は、消音機構の縦断面図である。  [Fig. 3] Fig. 3 is a longitudinal sectional view of the silencing mechanism.
[図 4]図 4は、消音機構の平面図である。  FIG. 4 is a plan view of the silencer mechanism.
[図 5]図 5は、変形例 1に係る消音機構の平面図である。  FIG. 5 is a plan view of a silencing mechanism according to Modification 1.
[図 6]図 6は、変形例 2に係る消音機構の断面図である。  FIG. 6 is a cross-sectional view of a silencing mechanism according to Modification 2.
[図 7]図 7は、変形例 3に係る消音機構の断面図である。  FIG. 7 is a cross-sectional view of a silencing mechanism according to Modification 3.
[図 8]図 8は、変形例 4に係る消音機構の断面図である。  FIG. 8 is a cross-sectional view of a silencing mechanism according to Modification 4.
[図 9]図 9は、変形例 5に係る消音機構の断面図である。  FIG. 9 is a cross-sectional view of a silencing mechanism according to Modification 5.
[図 10]図 10は、変形例 6に係る消音機構の断面図である。  FIG. 10 is a cross-sectional view of a silencing mechanism according to Modification 6.
[図 11]図 11は、変形例 7に係る消音機構の断面図である。  FIG. 11 is a cross-sectional view of a silencing mechanism according to Modification 7.
[図 12]図 12は、変形例 8に係る消音機構の断面図である。  FIG. 12 is a cross-sectional view of a silencing mechanism according to Modification 8.
[図 13]図 13は、変形例 9に係る消音機構の断面図である。  FIG. 13 is a cross-sectional view of a silencing mechanism according to Modification 9.
[図 14]図 14は、他の変形例に係る消音機構の断面図である。  FIG. 14 is a cross-sectional view of a silencing mechanism according to another modification.
[図 15]図 15は、さらに他の変形例に係る消音機構の断面図である。  FIG. 15 is a cross-sectional view of a silencing mechanism according to still another modification.
符号の説明  Explanation of symbols
[0040] 1 圧縮機 [0040] 1 Compressor
10 ケーシング  10 Casing
14 吸入管 15 吐出管 14 Suction pipe 15 Discharge pipe
20 圧縮機構  20 Compression mechanism
22 フロントヘッド (構造部材）  22 Front head (Structural member)
29 吐出口  29 Discharge port
30 電動機  30 electric motor
42 端板  42 End plate
43 側板  43 Side plate
44 吐出カバー  44 Discharge cover
45 尾管  45 tail pipe
45a細孔  45a pore
45c曲部  45c music part
46 消音機構  46 Silencer
発明を実施するための最良の形態  BEST MODE FOR CARRYING OUT THE INVENTION
[0041] 以下、本発明の実施形態を図面に基づいて詳細に説明する。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
[0042] この実施形態の圧縮機は、図 1及び図 2に示すように、いわゆる回転ピストン型の圧 縮機（1)で構成されている。この圧縮機（1)は、ケーシング（10)内に、ガスを圧縮して 吐出する圧縮機構 (20)と、該圧縮機構 (20)を駆動する電動機 (30)とが収納され、全 密閉型に構成されている。また、この圧縮機（1)は、電動機 (30)力 Sインバータ制御さ れて容量が段階的または連続的に可変となる可変容量型の圧縮機に構成されてい る。そして、この圧縮機（1)は、電動機 (30)によって圧縮機構 (20)を駆動することによ り、例えば、冷媒を吸入、圧縮した後に吐出して冷媒回路内で循環させるものである [0042] As shown in Figs. 1 and 2, the compressor of this embodiment includes a so-called rotary piston type compressor (1). The compressor (1) includes a casing (10) in which a compression mechanism (20) that compresses and discharges a gas and an electric motor (30) that drives the compression mechanism (20) are housed. It is configured. In addition, the compressor (1) is configured as a variable capacity compressor in which the capacity is variable stepwise or continuously by the electric motor (30) force S inverter control. And this compressor (1) drives a compression mechanism (20) by an electric motor (30), for example, sucks and compresses a refrigerant, then discharges it and circulates it in a refrigerant circuit.
[0043] 上記ケーシング（10)は、円筒状の胴部（11)と、この胴部（11)の上端開口部に接合 された上部鏡板（12)と、胴部（11)の下端開口部に接合された下部鏡板（13)とから 縦長円筒状の密閉容器に構成されて ヽる。 [0043] The casing (10) includes a cylindrical body (11), an upper end plate (12) joined to the upper end opening of the body (11), and a lower end opening of the body (11). The lower end plate (13) joined to the bottom is formed into a vertically long cylindrical sealed container.
[0044] 上記ケーシング（10)内の空間は、電動機 (30)を挟んで上下に位置する第 1空間（S 1)及び第 2空間（S2)に区画されている。この実施形態では、第 1空間（S1)が電動機 (30)の下方に配置され、第 2空間 (S2)が電動機 (30)の上方に配置されている。そし て、第 1空間 (SI)に圧縮機構 (20)が配置されている。 [0044] The space in the casing (10) is partitioned into a first space (S1) and a second space (S2) positioned above and below the electric motor (30). In this embodiment, the first space (S1) is disposed below the electric motor (30), and the second space (S2) is disposed above the electric motor (30). And The compression mechanism (20) is arranged in the first space (SI).
[0045] 上記ケーシング（10)には、胴部（11)の下部に吸入管（14)が設けられ、上部鏡板（1 2)には吐出管（15)が設けられている。上記吸入管（14)は、上記ケーシング（10)を介 して圧縮機構 (20)の吸入側に連通し、上記吐出管（15)は、該ケーシング（10)内の 空間に開口するように上部鏡板（12)に固定されている。つまり、上記吸入管（14)は ケーシング（10)における第 1空間（S1)側の位置に設けられ、上記吐出管（15)はケー シング（10)における第 2空間（S2)側の位置に設けられている。なお、上記吸入管（14 )にはアキュムレータ（16)が接続されて!、る。  [0045] The casing (10) is provided with a suction pipe (14) at the lower part of the body part (11), and an upper end plate (12) is provided with a discharge pipe (15). The suction pipe (14) communicates with the suction side of the compression mechanism (20) via the casing (10), and the discharge pipe (15) opens to a space in the casing (10). It is fixed to the upper end plate (12). That is, the suction pipe (14) is provided at a position on the first space (S1) side in the casing (10), and the discharge pipe (15) is provided at a position on the second space (S2) side in the casing (10). Is provided. An accumulator (16) is connected to the suction pipe (14).
[0046] 上記圧縮機構 (20)は、シリンダ (21)と、フロントヘッド (22)と、リャヘッド (23)と、回 転ピストン (24)とを備え、シリンダ (21)の上端にフロントヘッド (22)力 下端にリャへッ ド (23)が固定されている。  The compression mechanism (20) includes a cylinder (21), a front head (22), a rear head (23), and a rotating piston (24), and a front head ( 22) Force The rear head (23) is fixed at the lower end.
[0047] 上記シリンダ (21)は、厚肉の円筒状に形成されている。そして、上記シリンダ (21) の内周面とフロントヘッド (22)の下端面とリャヘッド (23)の上端面との間には、円柱 状のシリンダ室 (25)が区画形成されている。このシリンダ室 (25)は、該シリンダ室 (25 )内で回転ピストン (24)が偏心回転動作をするように構成されている。  [0047] The cylinder (21) is formed in a thick cylindrical shape. A cylindrical cylinder chamber (25) is defined between the inner peripheral surface of the cylinder (21), the lower end surface of the front head (22), and the upper end surface of the rear head (23). The cylinder chamber (25) is configured such that the rotating piston (24) performs an eccentric rotation operation in the cylinder chamber (25).
[0048] 上記電動機 (30)は、ステータ（31)とロータ (32)とを備えて!/、る。上記ロータ (32)に は、駆動軸 (33)が連結されている。この駆動軸 (33)は、ケーシング（10)内の中心を 通り、且つシリンダ室（25)を上下方向に貫通している。上記フロントヘッド（22)および リャヘッド (23)には、駆動軸 (33)を支持するための軸受部（22a,23a)がそれぞれ形 成されている。  [0048] The electric motor (30) includes a stator (31) and a rotor (32). A drive shaft (33) is coupled to the rotor (32). The drive shaft (33) passes through the center of the casing (10) and penetrates the cylinder chamber (25) in the vertical direction. The front head (22) and rear head (23) are formed with bearing portions (22a, 23a) for supporting the drive shaft (33), respectively.
[0049] 上記駆動軸 (33)は、本体部（33b)と、シリンダ室 (25)内に位置する偏心部（33a)と によって構成されている。この偏心部（33a)は、本体部（33b)よりも大径に形成され、 駆動軸 (33)の回転中心力も所定量偏心している。そして、この偏心部（33a)には、圧 縮機構 (20)の回転ピストン (24)が装着されている。図 2に示すように、この回転ピスト ン (24)は、円環状に形成され、その外周面がシリンダ (21)の内周面と実質的に一点 で接触するように形成されて ヽる。  [0049] The drive shaft (33) includes a main body (33b) and an eccentric part (33a) positioned in the cylinder chamber (25). The eccentric portion (33a) is formed with a larger diameter than the main body portion (33b), and the rotational center force of the drive shaft (33) is also eccentric by a predetermined amount. A rotating piston (24) of the compression mechanism (20) is attached to the eccentric part (33a). As shown in FIG. 2, the rotary piston (24) is formed in an annular shape, and its outer peripheral surface is formed so as to substantially contact with the inner peripheral surface of the cylinder (21) at one point.
[0050] 上記シリンダ (21)には、該シリンダ (21)の径方向に沿ってブレード溝 (21a)が形成 されている。このブレード溝 (21a)には、長方形の板状に形成されたブレード (26)が シリンダ (21)の径方向へ摺動可能に装着されている。上記ブレード (26)は、ブレード 溝 (21a)内に設けられたスプリング (27)によって径方向内方へ付勢され、先端が常に 回転ピストン (24)の外周面に接触して！/、る。 [0050] A blade groove (21a) is formed in the cylinder (21) along the radial direction of the cylinder (21). The blade groove (21a) has a blade (26) formed in a rectangular plate shape. It is mounted so that it can slide in the radial direction of the cylinder (21). The blade (26) is urged radially inward by a spring (27) provided in the blade groove (21a), and the tip always contacts the outer peripheral surface of the rotary piston (24)! /
[0051] 上記ブレード (26)は、シリンダ（21)の内周面と回転ピストン (24)の外周面との間の シリンダ室 (25)を吸入室 (25a)と圧縮室 (25b)とに区画している。そして、上記シリン ダ (21)には、該シリンダ (21)の外周面から内周面へ径方向に貫通し、吸入管（14)と 吸入室 (25a)とを連通する吸入口（28)が形成されている。また、上記フロントヘッド (2 2)には、駆動軸 (33)の軸方向に貫通し、圧縮室 (25b)とケーシング（10)内の空間と を連通する吐出口（29)が形成されている。  [0051] The blade (26) has a cylinder chamber (25) between the inner peripheral surface of the cylinder (21) and the outer peripheral surface of the rotary piston (24) as a suction chamber (25a) and a compression chamber (25b). It is partitioned. The cylinder (21) passes through the cylinder (21) from the outer circumferential surface to the inner circumferential surface in the radial direction, and communicates the suction pipe (14) and the suction chamber (25a). Is formed. The front head (22) is formed with a discharge port (29) penetrating in the axial direction of the drive shaft (33) and communicating the compression chamber (25b) and the space in the casing (10). Yes.
[0052] 上記フロントヘッド (22)には、吐出口（29)を開閉するための吐出弁機構 (40)が設 けられている。上記吐出弁機構 (40)は、リード弁 (41)と、このリード弁 (41)のたわみ 量を規制する弁押さえ（図示せず)とを備えている。上記リード弁 (41)は、弁押さえが 上方から重ねられ、フロントヘッド (22)と弁押さえとの間に挟まれている。そして、上 記リード弁 (41)および弁押さえは、基端側で締付ボルトによってフロントヘッド (22)に 固定されている（図示省略)。  [0052] The front head (22) is provided with a discharge valve mechanism (40) for opening and closing the discharge port (29). The discharge valve mechanism (40) includes a reed valve (41) and a valve presser (not shown) that regulates the amount of deflection of the reed valve (41). In the reed valve (41), the valve presser is stacked from above, and is sandwiched between the front head (22) and the valve presser. The reed valve (41) and the valve retainer are fixed to the front head (22) by fastening bolts on the base end side (not shown).
[0053] 上記フロントヘッド (22)には、圧縮機構 (20)に設けられた吐出口（29)を覆うように 端板 (42)と側板 (43)とからなる吐出カバー (44)が取り付けられている。この吐出カバ 一 (44)には、該吐出カバー (44)の中力 外へガスを通過させる尾管 (45)が固定され ている。これら吐出カバー (44)と尾管 (45)とにより、共鳴式の消音機構 (46)が構成さ れている。上記尾管 (45)は、その長手方向線分が電動機 (30)の端面と略平行な面 に沿うように配置されている。  A discharge cover (44) composed of an end plate (42) and a side plate (43) is attached to the front head (22) so as to cover the discharge port (29) provided in the compression mechanism (20). It has been. A tail pipe (45) that allows gas to pass outside the intermediate force of the discharge cover (44) is fixed to the discharge cover (44). The discharge cover (44) and the tail pipe (45) constitute a resonance type silencing mechanism (46). The tail pipe (45) is arranged so that its longitudinal line segment is along a plane substantially parallel to the end face of the electric motor (30).
[0054] 上記吐出カバー (44)は、円板状の端板 (42)と該端板 (42)の周縁部に連接する円 筒状の側板 (43)とを有している。上記尾管 (45)は、消音機構 (46)の拡大断面図で ある図 3及び平面図である図 4に示すように、吐出カバー（44)の略径方向にのびる 線分に沿って配置されて 、る。また、尾管 (45)は、吐出カバー (44)の側板 (43)の径 方向内側から径方向外側に跨って設けられている。したがって、尾管 (45)は、駆動 軸 (33)の軸方向に平行に設ける場合と比較して、十分な長さに設定することができる [0055] なお、第 1空間（SI)における圧力変動の騒音に対する相関は、 500Hz〜： LOOOHz で大きいことが知られている。尾管 (45)の長さ 1 (mm)は、例えば、周波数を f= 1000 ( Hz)、音速を c = 170 (m/sec)として、 [0054] The discharge cover (44) includes a disc-shaped end plate (42) and a cylindrical side plate (43) connected to the peripheral edge of the end plate (42). The tail pipe (45) is disposed along a line segment extending in a substantially radial direction of the discharge cover (44), as shown in FIG. 3 which is an enlarged sectional view of the silencer mechanism (46) and FIG. 4 which is a plan view. It has been. Further, the tail pipe (45) is provided from the radially inner side to the radially outer side of the side plate (43) of the discharge cover (44). Therefore, the tail tube (45) can be set to a sufficient length compared to the case where it is provided in parallel with the axial direction of the drive shaft (33). [0055] It is known that the correlation between pressure fluctuation and noise in the first space (SI) is large from 500Hz to: LOOOHz. The length 1 (mm) of the tail pipe (45) is, for example, when the frequency is f = 1000 (Hz) and the sound speed is c = 170 (m / sec)
f< c/41 で表される関係式から、  From the relational expression represented by f <c / 41,
42.5 (mm)以下とすることができる。  It can be 42.5 (mm) or less.
[0056] 運転動作  [0056] Driving action
次に、上述した圧縮機（1)の運転動作について説明する。  Next, the operation of the compressor (1) described above will be described.
[0057] まず、上記電動機 (30)に通電すると、ロータ (32)が回転し、該ロータ (32)の回転が 駆動軸 (33)を介して圧縮機構 (20)の回転ピストン (24)に伝達される。これによつて、 上記圧縮機構 (20)が所定の圧縮動作を行う。  First, when the electric motor (30) is energized, the rotor (32) rotates and the rotation of the rotor (32) is applied to the rotating piston (24) of the compression mechanism (20) via the drive shaft (33). Communicated. Thereby, the compression mechanism (20) performs a predetermined compression operation.
[0058] 具体的に、図 2を参照しながら圧縮機構 (20)の圧縮動作について説明する。上記 回転ピストン (24)が電動機 (30)の駆動によって図の右回り（時計回り）に回転すると、 その回転に従って吸入室 (25a)の容積が拡大し、該吸入室 (25a)に低圧の冷媒が吸 入口（28)を介して吸入される。この吸入室 (25a)への冷媒の吸入は、回転ピストン (2 4)がシリンダ室 (25)内を偏心回転して吸入口（28)のすぐ右側でシリンダ (21)と回転 ピストン (24)とが接触する状態となるまで続く。  Specifically, the compression operation of the compression mechanism (20) will be described with reference to FIG. When the rotating piston (24) rotates clockwise (clockwise) in the figure by driving the electric motor (30), the volume of the suction chamber (25a) increases according to the rotation, and a low-pressure refrigerant is introduced into the suction chamber (25a). Is sucked through the suction port (28). The refrigerant is sucked into the suction chamber (25a) by rotating the rotary piston (2 4) eccentrically in the cylinder chamber (25) so that the cylinder (21) and the rotary piston (24) are located just to the right of the suction port (28). Continue until contact is made.
[0059] 上記のように、回転ピストン (24)が 1回転して冷媒の吸入が終了すると、冷媒が圧 縮される圧縮室 (25b)が形成される。なお、この圧縮室 (25b)の隣には、新たな吸入 室 (25a)が形成され、該吸入室 (25a)への冷媒の吸入が繰り返される。上記圧縮室 (2 5b)の冷媒は、回転ピストン (24)の回転に伴って圧縮室 (25b)の容積が減少すること により、圧縮される。  [0059] As described above, when the rotary piston (24) makes one rotation and the suction of the refrigerant is completed, a compression chamber (25b) in which the refrigerant is compressed is formed. A new suction chamber (25a) is formed next to the compression chamber (25b), and the refrigerant is repeatedly sucked into the suction chamber (25a). The refrigerant in the compression chamber (25b) is compressed as the volume of the compression chamber (25b) decreases as the rotary piston (24) rotates.
[0060] 上記圧縮室 (25b)が所定の高圧になると、該圧力がリード弁 (41)に作用することに よって、吐出口（29)が開く。上記圧縮室 (25b)の冷媒は、吐出口（29)から吐出カバ 一 (44)内に吐出される。そして、上記高圧の冷媒が吐出されて圧縮室 (25b)が低圧 になると、リード弁 (41)が自身のパネ力によって吐出口（29)を閉鎖する。このようにし て、冷媒の吸入、圧縮および吐出が繰り返される。  [0060] When the compression chamber (25b) reaches a predetermined high pressure, the pressure acts on the reed valve (41) to open the discharge port (29). The refrigerant in the compression chamber (25b) is discharged from the discharge port (29) into the discharge cover (44). When the high-pressure refrigerant is discharged and the compression chamber (25b) becomes low pressure, the reed valve (41) closes the discharge port (29) by its panel power. In this way, refrigerant suction, compression, and discharge are repeated.
[0061] 圧縮機構 (20)力 吐出された高圧の冷媒は、吐出カバー (44)内から尾管 (45)を 通ってケーシング（10)の第 1空間（S1)に吹き出される。そして、吐出ガスが尾管 (45) を通る際の共鳴効果によって脈動騒音が吸収される。 [0061] Compression mechanism (20) force The discharged high-pressure refrigerant is blown out of the discharge cover (44) through the tail pipe (45) and into the first space (S1) of the casing (10). And the discharge gas is tail pipe (45) The pulsating noise is absorbed by the resonance effect when passing through.
[0062] 一方、上記吐出ガスは、尾管 (45)力 電動機 (30)の端面と略平行な方向に吹き出 される。したがって、ケーシング（10)内の音響空間で吐出ガスの圧力波による縦方向 (駆動軸の軸方向）の共鳴モードは生じにくい。このため、電動機 (30)のロータ (32) は上下に振動しにくくなる。  On the other hand, the discharge gas is blown out in a direction substantially parallel to the end surface of the tail pipe (45) force electric motor (30). Therefore, the resonance mode in the vertical direction (axial direction of the drive shaft) due to the pressure wave of the discharge gas is unlikely to occur in the acoustic space in the casing (10). For this reason, the rotor (32) of the electric motor (30) is less likely to vibrate up and down.
[0063] 一実施形態の効果  [0063] Effects of one embodiment
このように、本実施形態によれば、圧縮機構 (20)に設けられた吐出口（29)を覆うよ うに端板 (42)と側板 (43)とからなる吐出カバー (44)と該吐出カバー (44)の中から外 へガスを通過させる尾管 (45)とからなる消音機構 (46)を備えた回転式圧縮機（1)に おいて、上記尾管 (45)を、その長手方向線分が電動機 (30)の端面と略平行な面に 沿うように配置している。したがって、圧縮機構 (20)と電動機 (30)の位置関係に関わ らず、尾管 (45)を十分な長さにすることができるので、尾管による共鳴効果を高めら れる。また、吐出ガスが尾管 (45)力 電動機 (30)の端面とほぼ平行に吹き出される ため、ケーシング（10)内の音響空間で吐出ガスの圧力波による縦方向の共鳴モード が生じに《なり、電動機 (30)のロータ (32)が上下に振動しに《なる。したがって、 電動機 (30)のロータ (32)の振動に起因する騒音の発生を低減することができる。  Thus, according to the present embodiment, the discharge cover (44) including the end plate (42) and the side plate (43) so as to cover the discharge port (29) provided in the compression mechanism (20), and the discharge cover (44). In a rotary compressor (1) equipped with a silencing mechanism (46) consisting of a tail pipe (45) that allows gas to pass outside from the cover (44), the tail pipe (45) The direction line segment is arranged along a plane substantially parallel to the end face of the electric motor (30). Therefore, regardless of the positional relationship between the compression mechanism (20) and the electric motor (30), the tail pipe (45) can be made sufficiently long, so that the resonance effect by the tail pipe can be enhanced. Also, since the discharge gas is blown out almost parallel to the end face of the tail pipe (45) force motor (30), a longitudinal resonance mode due to the pressure wave of the discharge gas occurs in the acoustic space in the casing (10). Thus, the rotor (32) of the electric motor (30) vibrates up and down. Therefore, the generation of noise due to the vibration of the rotor (32) of the electric motor (30) can be reduced.
[0064] また、尾管 (45)を吐出カバー (44)の側板 (43)の径方向内側力 径方向外側に跨 つて設けるようにしたことにより、尾管 (45)の長さを比較的長くすることができるので、 共鳴周波数を比較的低 、周波数に設定することもできる。  [0064] Further, since the tail pipe (45) is provided to straddle the radial inner side radial force of the side plate (43) of the discharge cover (44), the length of the tail pipe (45) is relatively increased. Since the resonance frequency can be increased, the resonance frequency can be set to a relatively low frequency.
[0065] さらに、本実施形態では、尾管 (45)の全体がケーシング（10)内の空間（S1)に収め られているため、尾管 (45)による脈動騒音の低減がケーシング（10)の内部で完結す るし、尾管 (45)を吐出カバー (44)や圧縮機構 (20)と一体的に形成できるため、製造 性が良く低コストである。  [0065] Further, in this embodiment, since the entire tail pipe (45) is housed in the space (S1) in the casing (10), the reduction of pulsation noise by the tail pipe (45) is reduced by the casing (10). Since the tail pipe (45) can be formed integrally with the discharge cover (44) and the compression mechanism (20), the productivity is good and the cost is low.
[0066] 実施形態の変形例  [0066] Modification of Embodiment
(変形例 1)  (Modification 1)
図 5は、変形例 1に係る消音機構 (46)の平面図を示している。この例では、吐出力 バー (44)力 円板状の端板 (42)と該端板 (42)の周縁部に連接する円筒状の側板 (4 3)とを有する点は上記実施形態と同じであるが、尾管 (45)が、吐出カバー (44)の略 接線方向にのびる線分に沿って配置されている。圧縮機（1)の内部構造に応じて、 尾管 (45)を吐出カバー (44)の略径方向にのびる線分に沿って配置する上記実施形 態の構造を選択するか、尾管 (45)吐出カバー (44)の略接線方向にのびる線分に沿 つて配置する変形例 1の構造を選択することができる。また、尾管 (45)は、これらの線 分に対して多少は傾けてもよい。 FIG. 5 shows a plan view of the muffler mechanism (46) according to the first modification. In this example, the discharge force bar (44) force has a disc-shaped end plate (42) and a cylindrical side plate (43) connected to the peripheral edge of the end plate (42). Same, but the tail tube (45) is short for the discharge cover (44) It is arranged along a line segment extending in the tangential direction. Depending on the internal structure of the compressor (1), the structure of the above embodiment in which the tail pipe (45) is arranged along the line extending substantially in the radial direction of the discharge cover (44) is selected, or the tail pipe ( 45) The structure of Modification 1 can be selected that is arranged along a line extending in the substantially tangential direction of the discharge cover (44). The tail tube (45) may be slightly inclined with respect to these line segments.
[0067] (変形例 2)  [0067] (Modification 2)
図 6は、変形例 2に係る消音機構 (46)の断面図を示している。この例では、尾管 (45 )が吐出カバー (44)の側板 (43)の径方向内側にのみ設けられている。その他の構造 は、上記実施形態と同じである。このように構成すると、上記実施形態に比べて尾管（ 45)の長さを比較的短くすることができるため、共鳴周波数を比較的高い周波数に設 定することができる。  FIG. 6 shows a cross-sectional view of the silencing mechanism (46) according to the second modification. In this example, the tail pipe (45) is provided only on the radially inner side of the side plate (43) of the discharge cover (44). Other structures are the same as those in the above embodiment. With this configuration, the length of the tail tube (45) can be made relatively short as compared to the above embodiment, so that the resonance frequency can be set to a relatively high frequency.
[0068] (変形例 3)  [0068] (Modification 3)
図 7は、変形例 3に係る消音機構 (46)の断面図を示している。この例では、尾管 (45 )が吐出カバー (44)の側板 (43)の径方向外側にのみ設けられている。その他の構造 は、上記実施形態と同じである。このように構成すると、上記実施形態に比べて尾管（ 45)の長さを比較的短くすることができるため、変形例 2と同様に共鳴周波数を比較 的高 、周波数に設定することができる。  FIG. 7 shows a cross-sectional view of the silencer mechanism (46) according to the third modification. In this example, the tail pipe (45) is provided only on the radially outer side of the side plate (43) of the discharge cover (44). Other structures are the same as those in the above embodiment. With this configuration, since the length of the tail tube (45) can be relatively shortened compared to the above embodiment, the resonance frequency can be set to a relatively high frequency as in the second modification. .
[0069] (変形例 4)  [0069] (Modification 4)
図 8は、変形例 4に係る消音機構 (46)の断面図を示している。この例では、尾管 (45 )は吐出カバー (44)の側板 (43)の径方向外側に位置する部分が略 U字状の曲部 (4 5c)に形成されている。その他の構造は、上記実施形態と同じである。このように構成 すると、尾管 (45)の出口端面から圧縮機（1)のケーシング（10)の内壁面までの距離 が長くなつて、尾管 (45)から吹き出される吐出ガスの圧力波がケーシングに当たるま でに減衰しやすくなる。したがって、騒音低減効果が高められる。  FIG. 8 shows a cross-sectional view of the silencing mechanism (46) according to the fourth modification. In this example, the tail tube (45) has a substantially U-shaped bent portion (45c) that is located on the radially outer side of the side plate (43) of the discharge cover (44). Other structures are the same as those in the above embodiment. With this configuration, the distance from the outlet end face of the tail pipe (45) to the inner wall surface of the casing (10) of the compressor (1) becomes long, and the pressure wave of the discharge gas blown out from the tail pipe (45). It tends to be attenuated before it hits the casing. Therefore, the noise reduction effect is enhanced.
[0070] (変形例 5)  [0070] (Variation 5)
図 9は、変形例 5に係る消音機構 (46)の断面図を示している。この例では、尾管 (45 )には、該尾管 (45)の管壁を貫通する複数の細孔 (45a)が形成されている。その他の 構造は、上記実施形態と同じである。このように構成すると、尾管 (45)を流れる吐出 ガスが細孔 (45a)を通るために圧力損失が生じ、吐出ガスの圧力波が弱くなる。した がって、騒音低減効果が高められる。 FIG. 9 shows a cross-sectional view of the silencing mechanism (46) according to the fifth modification. In this example, the tail tube (45) is formed with a plurality of pores (45a) penetrating the tube wall of the tail tube (45). Other structures are the same as those in the above embodiment. With this configuration, the discharge flowing through the tail pipe (45) Since the gas passes through the pores (45a), pressure loss occurs, and the pressure wave of the discharge gas becomes weak. Therefore, the noise reduction effect is enhanced.
[0071] (変形例 6)  [Modification 6]
図 10は、変形例 6に係る消音機構 (46)の断面図を示している。この例では、吐出力 バー (44)には複数の尾管 (45)が取り付けられている。その他の構造は、上記実施形 態と同じである。このように吐出カバー (44)に複数の尾管 (45)を取り付けると、尾管（ 45)による共鳴周波数を任意に設定しやすくなり、消音設計の自由度を高められる。  FIG. 10 shows a cross-sectional view of the silencer mechanism (46) according to Modification 6. In this example, a plurality of tail tubes (45) are attached to the discharge force bar (44). Other structures are the same as those in the above embodiment. By attaching a plurality of tail pipes (45) to the discharge cover (44) in this way, it becomes easy to arbitrarily set the resonance frequency by the tail pipe (45), and the degree of freedom in noise reduction design can be increased.
[0072] (変形例 7)  [Modification 7]
図 11は、変形例 7に係る消音機構 (46)の断面図を示している。この例では、尾管（ 45)は圧縮機構 (20)の構造部材であるフロントヘッド (22)と一体的に铸造して横穴加 ェをすることにより形成され、吐出カバー (44)の側板 (43)の径方向内側にのみ設け られている。吐出カバー（44)には横穴（44a)が設けられている。その他の構造は、上 記実施形態と同じである。このように尾管 (45)を圧縮機構 (20)の構造部材 (22)と一 体的に形成すると、尾管 (45)の剛性が高まり、尾管 (45)自体が振動しにくくなる。そ のため、騒音低減効果を高められる。  FIG. 11 shows a cross-sectional view of the silencing mechanism (46) according to the seventh modification. In this example, the tail pipe (45) is formed by integrally forging the front head (22), which is a structural member of the compression mechanism (20), and adding a horizontal hole to the side plate ( It is provided only on the radially inner side of 43). The discharge cover (44) is provided with a lateral hole (44a). Other structures are the same as those in the above embodiment. If the tail pipe (45) is formed integrally with the structural member (22) of the compression mechanism (20) in this way, the rigidity of the tail pipe (45) is increased and the tail pipe (45) itself is less likely to vibrate. Therefore, the noise reduction effect can be enhanced.
[0073] (変形例 8)  [0073] (Modification 8)
図 12は、変形例 8に係る消音機構 (46)の断面図を示している。この例は、図 11の 変形例 7にお 、て尾管 (45)の横穴に管 (45b)を挿入して、尾管 (45)の長さを延長し た例である。その他の構造は、変形例 7と同じである。このようにすると、尾管 (45)自 体の剛性を高めることにより騒音低減効果を高められるとともに、尾管 (45)の長さを 延長することにより共鳴周波数をより低周波数に設定することができる。  FIG. 12 shows a cross-sectional view of the muffler mechanism (46) according to Modification 8. This example is an example in which the length of the tail tube (45) is extended by inserting the tube (45b) into the lateral hole of the tail tube (45) in the modified example 7 of FIG. Other structures are the same as those of the seventh modification. In this way, the noise reduction effect can be enhanced by increasing the rigidity of the tail pipe (45) itself, and the resonance frequency can be set to a lower frequency by extending the length of the tail pipe (45). it can.
[0074] (変形例 9)  [0074] (Modification 9)
図 13は、変形例 9に係る消音機構 (46)の断面図を示している。この例では、図 12 の変形例 8において尾管 (45)の延長部も一体的に形成し、吐出カバー (44)には図 1 1のような横穴（44a)の代わりに側面から見て逆 U形の切り欠き（44b)を設けている。 その他の構造は、変形例 8と同じである。このようにしても、尾管 (45)自体の剛性を高 めることにより騒音低減効果を高められるとともに、尾管 (45)の長さを延長することに より共鳴周波数をより低周波数に設定することができる。 [0075] 《その他の実施形態》 FIG. 13 shows a cross-sectional view of the silencing mechanism (46) according to Modification 9. In this example, the extension part of the tail pipe (45) is also integrally formed in the modified example 8 of FIG. 12, and the discharge cover (44) is viewed from the side instead of the side hole (44a) as shown in FIG. An inverted U-shaped notch (44b) is provided. The other structure is the same as that of Modification 8. Even in this way, the noise reduction effect can be enhanced by increasing the rigidity of the tail pipe (45) itself, and the resonance frequency can be set to a lower frequency by extending the length of the tail pipe (45). can do. [0075] << Other Embodiments >>
上記実施形態にっ 、ては、以下のような構成としてもょ 、。  According to the above embodiment, the following configuration may be adopted.
[0076] 例えば、上記実施形態では、ケーシング（10)内には電動機 (30)の下方の空間に 圧縮機構 (20)を配置して 、るが、逆に電動機 (30)の上方の空間に圧縮機構 (20)を 酉己置してちょい。 For example, in the above embodiment, the compression mechanism (20) is arranged in the space below the electric motor (30) in the casing (10), but conversely in the space above the electric motor (30). Place the compression mechanism (20).
[0077] また、上記実施形態では吸入管（14)をケーシング（10)の胴部（11)を介して圧縮機 構 (20)の吸入側に直接接続するようにしているが、ケーシング（10)内の吸入側にバ ッファ空間を設け、このノ ッファ空間を介して圧縮機構 (20)が吸入ガスを吸い込むよ うにしてもよい。  [0077] In the above embodiment, the suction pipe (14) is directly connected to the suction side of the compressor structure (20) via the body (11) of the casing (10). It is also possible to provide a buffer space on the suction side in the interior) and allow the compression mechanism (20) to suck the suction gas through the buffer space.
[0078] また、図 8に示した変形例 4は、尾管 (45)が略 U字状になるように曲部 (45c)を設け たものであるが、曲部の形状は、図 14や図 15に示すようにしてもよい。図 14の例は、 曲部 (45c)を「コ」の字状に形成した例であり、図 15の例は、曲部 (45c)を「レ」の字状 に形成した例である。いずれの場合も、図 8の例と同様に尾管 (45)力も吹き出される 吐出ガスの圧力波がケーシングに当たるまでに減衰しやすくなるため、騒音低減効 果が高められる。  [0078] Further, in Modification 4 shown in Fig. 8, the curved portion (45c) is provided so that the tail tube (45) is substantially U-shaped. Or as shown in FIG. The example in FIG. 14 is an example in which the curved portion (45c) is formed in a “U” shape, and the example in FIG. 15 is an example in which the curved portion (45c) is formed in a “L” shape. In either case, as in the example of FIG. 8, since the pressure wave of the discharge gas from which the tail pipe (45) force is blown out is easily attenuated before it hits the casing, the noise reduction effect is enhanced.
[0079] また、本発明は、回転ピストン型の圧縮機（1)に限らず、スイング型など、他の形式 の圧縮機に適用してもよい。  [0079] Further, the present invention is not limited to the rotary piston type compressor (1), and may be applied to other types of compressors such as a swing type.
[0080] なお、以上の実施形態は、本質的に好ましい例示であって、本発明、その適用物、 あるいはその用途の範囲を制限することを意図するものではない。 [0080] The above embodiments are essentially preferable examples, and are not intended to limit the scope of the present invention, its application, or its use.
産業上の利用可能性  Industrial applicability
[0081] 以上説明したように、本発明は、密閉ケーシング内に圧縮機構と電動機が収納され 、ケーシング内が圧縮機の吐出圧力になる高圧ドーム形の回転式圧縮機に設けられ る消音機構の構造について有用である。 [0081] As described above, the present invention relates to a silencing mechanism provided in a high-pressure dome-shaped rotary compressor in which a compression mechanism and an electric motor are housed in a sealed casing, and the inside of the casing becomes the discharge pressure of the compressor. Useful for structure.

Claims

請求の範囲 The scope of the claims
[1] ガスを圧縮して吐出する圧縮機構 (20)と、該圧縮機構 (20)を駆動する電動機 (30) と、該圧縮機構 (20)及び電動機 (30)を収納するケーシング (10)と、圧縮機構 (20)の 吸入側に連通する吸入管（14)と、該ケーシング（10)内の空間に開口するようにケー シング (10)に設けられた吐出管（15)と、圧縮機構 (20)に設けられた吐出口（29)を覆 うように端板 (42)と側板 (43)とからなる吐出カバー (44)と該吐出カバー (44)の中から 外へガスを通過させる尾管 (45)とからなる消音機構 (46)とを備えた回転式圧縮機で あって、  [1] A compression mechanism (20) that compresses and discharges gas, an electric motor (30) that drives the compression mechanism (20), and a casing (10) that houses the compression mechanism (20) and the electric motor (30) A suction pipe (14) communicating with the suction side of the compression mechanism (20), a discharge pipe (15) provided in the casing (10) so as to open into a space in the casing (10), a compression pipe (14) A discharge cover (44) composed of an end plate (42) and a side plate (43) so as to cover the discharge port (29) provided in the mechanism (20) and gas is discharged from the discharge cover (44) to the outside. A rotary compressor having a silencing mechanism (46) composed of a tail pipe (45) to be passed through,
上記尾管 (45)は、その長手方向線分が電動機 (30)の端面と略平行な面に沿うよう に配置されていることを特徴とする回転式圧縮機。  The tail compressor (45) is a rotary compressor characterized in that its longitudinal line segment is disposed along a plane substantially parallel to the end face of the electric motor (30).
[2] 請求項 1において、 [2] In claim 1,
吐出カバー (44)は、円板状の端板 (42)と該端板 (42)の周縁部に連接する円筒状 の側板 (43)とを有し、  The discharge cover (44) has a disc-shaped end plate (42) and a cylindrical side plate (43) connected to the peripheral edge of the end plate (42).
尾管 (45)は、吐出カバー (44)の略径方向にのびる線分に沿って配置されているこ とを特徴とする回転式圧縮機。  The tail pipe (45) is a rotary compressor characterized in that the tail pipe (45) is arranged along a line segment extending in a substantially radial direction of the discharge cover (44).
[3] 請求項 1において、 [3] In claim 1,
吐出カバー (44)は、円板状の端板 (42)と該端板 (42)の周縁部に連接する円筒状 の側板 (43)とを有し、  The discharge cover (44) has a disc-shaped end plate (42) and a cylindrical side plate (43) connected to the peripheral edge of the end plate (42).
尾管 (45)は、吐出カバー (44)の略接線方向にのびる線分に沿って配置されている ことを特徴とする回転式圧縮機。  The tail pipe (45) is arranged along a line segment extending in a substantially tangential direction of the discharge cover (44).
[4] 請求項 1において、 [4] In claim 1,
尾管 (45)は吐出カバー (44)の側板 (43)の径方向内側力 径方向外側に跨って設 けられて 、ることを特徴とする回転式圧縮機。  The tail compressor (45) is provided so as to straddle the radially inner force of the side plate (43) of the discharge cover (44) across the radially outer side.
[5] 請求項 1において、 [5] In claim 1,
尾管 (45)は吐出カバー (44)の側板 (43)の径方向内側にのみ設けられていることを 特徴とする回転式圧縮機。  A rotary compressor characterized in that the tail pipe (45) is provided only on the radially inner side of the side plate (43) of the discharge cover (44).
[6] 請求項 1において、 [6] In claim 1,
尾管 (45)は吐出カバー (44)の側板 (43)の径方向外側にのみ設けられていることを 特徴とする回転式圧縮機。 Make sure that the tail pipe (45) is installed only on the radially outer side of the side plate (43) of the discharge cover (44). Features a rotary compressor.
[7] 請求項 1において、 [7] In claim 1,
尾管 (45)は吐出カバー (44)の側板 (43)の径方向外側に位置する部分に曲部 (45 c)を備えていることを特徴とする回転式圧縮機。  The tail pipe (45) is provided with a curved portion (45c) in a portion located on the radially outer side of the side plate (43) of the discharge cover (44).
[8] 請求項 1において、 [8] In claim 1,
尾管 (45)には該尾管 (45)の管壁を貫通する複数の細孔 (45a)が形成されて!、るこ とを特徴とする回転式圧縮機。  A rotary compressor characterized in that the tail pipe (45) has a plurality of pores (45a) penetrating the pipe wall of the tail pipe (45)!
[9] 請求項 1において、 [9] In claim 1,
吐出カバー (44)には複数の尾管 (45)が取り付けられていることを特徴とする回転 式圧縮機。  A rotary compressor characterized in that a plurality of tail pipes (45) are attached to the discharge cover (44).
[10] 請求項 1において、 [10] In claim 1,
尾管 (45)は圧縮機構 (20)の構造部材 (22)と一体的に形成されて!ヽることを特徴と する回転式圧縮機。  A rotary compressor characterized in that the tail pipe (45) is formed integrally with the structural member (22) of the compression mechanism (20).
[11] 請求項 1において、 [11] In claim 1,
尾管 (45)の全体がケーシング（10)内の空間（S1)に収められていることを特徴とす る回転式圧縮機。  A rotary compressor characterized in that the entire tail pipe (45) is housed in a space (S1) in the casing (10).
PCT/JP2006/309931 2005-07-15 2006-05-18 Rotary compressor WO2007010668A1 (en)

Applications Claiming Priority (4)

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JP2005206675 2005-07-15
JP2005-206675 2005-07-15
JP2006106444A JP2007046595A (en) 2005-07-15 2006-04-07 Rotary compressor
JP2006-106444 2006-04-07

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