EP1971777A1 - Refrigerant compressor - Google Patents

Refrigerant compressor

Info

Publication number
EP1971777A1
EP1971777A1 EP07850311A EP07850311A EP1971777A1 EP 1971777 A1 EP1971777 A1 EP 1971777A1 EP 07850311 A EP07850311 A EP 07850311A EP 07850311 A EP07850311 A EP 07850311A EP 1971777 A1 EP1971777 A1 EP 1971777A1
Authority
EP
European Patent Office
Prior art keywords
sound deadening
deadening space
opening
refrigerant compressor
hermetic container
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07850311A
Other languages
German (de)
French (fr)
Inventor
Akihiko c/o Matsushita Electric Ind. Co. Ltd. IPROC KUBOTA
Seigo c/o Matsushita Electric Ind. Co. Ltd. IPROC YANASE
Atsushi c/o Matsushita Electric Ind. Co. Ltd. IPROC NARUSE
Kiwamu c/o Matsushita Electric Ind. Co. Ltd. IPROC WATANABE
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Corp
Original Assignee
Matsushita Electric Industrial Co 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 Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of EP1971777A1 publication Critical patent/EP1971777A1/en
Withdrawn legal-status Critical Current

Links

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
    • 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
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing

Definitions

  • the present invention relates to a refrigerant compressor used in a refrigerating cycle of a refrigerator-freezer and the like.
  • this type of refrigerant compressor includes that in which a resonance chamber is arranged in a suction muffler, which is opened to the inside of a hermetic container, for taking in refrigerant gas to reduce the sound of a specific frequency.
  • a resonance chamber is arranged in a suction muffler, which is opened to the inside of a hermetic container, for taking in refrigerant gas to reduce the sound of a specific frequency.
  • Fig. 8 is a partially cut perspective view showing an overall configuration of the conventional refrigerant compressor.
  • Fig. 9 is a partially cut perspective view of one part of a compression element and an suction muffler of the conventional refrigerant compressor.
  • hermetic container 1 for storing lubricating oil supports and accommodates, by way of elastic body 11 such as a spring, compressor body 10 configured by arranging electric powered element 3 and compression element 5 on upper and lower sides of frame 9 including a bearing (not shown) for supporting a crankshaft (not shown) integrally molded to crank pin 7.
  • Crank pin 7 is formed eccentric to the crankshaft fitted into and fixed to a rotor (not shown) configuring electric powered element 3.
  • Piston 13 is inserted to cylinder 15 having a substantially cylindrical shape in a freely reciprocating and slidably moving manner, and is coupled with crank pin 7 by coupling part 17.
  • Valve plate 19 for sealing an open end face (not shown) of cylinder 15 includes a suction port (not shown) which communicates with cylinder 15 through opening/closing of a suction valve (not shown), where cylinder 15, top surface (not shown) of piston 13, and valve plate 19 define a compression chamber (not shown).
  • Cylinder head 21 forming a high pressure chamber is fixed on the side opposite to cylinder 15 by way of valve plate 19.
  • Suction muffler 23 configures tail tube 27 which is a suction passage of refrigerant gas (not shown) with opening 25 to the inside of hermetic container 1, and resonator 33 including resonance chamber 31 communicating to tail tube 27 by way of throttle hole 29.
  • One end of communication tube 35 is coupled to the suction port formed in valve plate 19 of compression element 5 by way of cylinder head 21, and the other end of communication tube 35 is coupled to suction muffler 23.
  • piston 13 reciprocates in cylinder 15 through coupling part 17 due to eccentric motion of crank pin 7, and sequentially performs suction, compression and discharge strokes.
  • the suction stroke of piston 13 the refrigerant gas filled in a space of hermetic container 1 is taken in from opening 25 of tail tube 27 and led to the suction valve closing the suction port of valve plate 19 through a suction flow channel formed by suction muffler 23, communication tube 35, and cylinder head 21, and then flowed into cylinder 15 by pushing open the suction valve.
  • resonator 33 sound-deadens low frequency sound (about 400 Hz to about 600 Hz) of the noise generated as vibration sound of the suction valve of valve plate 19 or pulsation sound of the refrigerant gas.
  • the sound in the low frequency region of the refrigerant compressor is reduced as a result.
  • suction muffler 23 excites high-pass resonance frequency (e.g., about 2000 Hz or 2500 Hz) of hermetic container 1 molded by draw forming an iron plate through pressing, whereby the high frequency sound becomes higher.
  • Resonator 33 cannot be formed by a single component due to its structure of being formed by resonance chamber 31 communicating to tail tube 27 by way of throttle hole 29, and thus the resonance frequency changes due to leakage of refrigerant gas caused by adherence failure at the joining part, and the noise reducing effect lowers.
  • the present invention provides a refrigerant compressor of low noise capable of reducing resonance sound generated when high-pass resonance frequency (e.g., about 2000 Hz or 2500 Hz) of the hermetic container is excited by the suction muffler.
  • the refrigerant compressor of the present invention has a sound deadening space formed in a suction muffler communicating to a compression chamber, where the suction muffler includes a tail tube having one end (first end) opening to the inside of a hermetic container and the other end (second end) opening to the sound deadening space, the position in the opening direction of the tail tube in the sound deadening space being at the middle of the sound deadening space.
  • the high frequency sound generated as vibration sound of the suction valve or pulsation sound of the refrigerant gas thus can be reduced by having the opening position of the tail tube in the sound deadening space at the position of the acoustic node in the middle of the sound deadening space where the high frequency sound can be easily attenuated, and excitation of the high-pass resonance frequency (e.g., about 2000 Hz and 2500 Hz) of the hermetic container can be suppressed.
  • the high-pass resonance frequency e.g., about 2000 Hz and 2500 Hz
  • Fig. 1 is a side cross sectional view of a refrigerant compressor according to embodiment 1 of the present invention.
  • Fig. 2 is a front transparent view of the refrigerant compressor according to embodiment 1 of the present invention.
  • Fig. 3 is a front cross sectional view of a suction muffler in embodiment 1 of the present invention.
  • Fig. 4 is a perspective view of an Lrshaped bent part in embodiment 1 of the present invention.
  • Fig. 5 is a characteristic chart showing sound deadening characteristics of the suction muffler according to embodiment 1 of the present invention and the suction muffler of the prior art.
  • Fig. 6 is a characteristic chart showing resonance characteristics of the hermetic container in embodiment 1 of the present invention.
  • Fig. 7 is a characteristic chart showing noise levels of the refrigerant compressor according to embodiment 1 of the present invention and the prior art.
  • Fig. 8 is a partially cut perspective view showing an overall configuration of a conventional refrigerant compressor.
  • Fig. 9 is a partially cut perspective view of one part of a compression element and a suction muffler of the conventional refrigerant compressor.
  • Embodiment 1 of the present invention will now be described with reference to the drawings. It should be noted that the invention is not limited by embodiment 1.
  • Fig. 1 is a side cross sectional view of a refrigerant compressor according to embodiment 1 of the present invention.
  • Fig. 2 is a front transparent view of the refrigerant compressor according to embodiment 1 of the present invention.
  • Fig. 3 is a front cross sectional view of a suction muffler in embodiment 1 of the present invention.
  • Fig. 4 is a perspective view of an L-shaped bent part in embodiment 1 of the present invention.
  • hermetic container 101 stores lubricating oil 103 at the bottom part, and supports and accommodates, by way of elastic body 115 such as a spring, compressor body 113 configured by compression element 105 for taking in and compressing refrigerant gas (not shown), and electric powered element 111 including rotor 107 and stator 109 for driving compression element 105.
  • elastic body 115 such as a spring
  • compressor body 113 configured by compression element 105 for taking in and compressing refrigerant gas (not shown)
  • electric powered element 111 including rotor 107 and stator 109 for driving compression element 105.
  • Piston 117 is inserted to cylinder 119 of a substantially cylindrical shape in a freely reciprocating and slidably moving manner, and is coupled with crank pin 121 by connecting rod 123 or a coupling part.
  • crank pin 121 is formed eccentric to crankshaft 125 fitted into and fixed to rotor 107.
  • Valve plate 127 for sealing an open end face of cylinder 119 includes suction port 131 which communicates with cylinder 119 through opening/closing of suction valve 129, where cylinder 119, the top surface of piston 117, and valve plate 127 define compression chamber 133.
  • Cylinder head 135 forming a high pressure chamber is fixed on the side opposite to cylinder 119 by way of valve plate 127.
  • suction muffler 137 is made of resin material, and forms sound deadening space 139.
  • Expansion chamber 151 and resonance chamber 153 are arranged in sound deadening space 139.
  • Tail tube 147 including vertical part 143 and Irshaped bent part 145, and having one end opening to sound deadening space 139 and the other end forming suction port 141 of the refrigerant gas opened to the inside of hermetic container 101 is arranged in suction muffler 137.
  • Tail tube 147 is formed into a substantially Lrshape by Lrshaped bent part 145, where opening 161 opening to expansion chamber 151 of sound deadening space 139 is formed at a position of Li/2, which is at the middle of space length Li of sound deadening space 139 in the opening direction.
  • the shapes of connecting parts 157, 159 of vertical part 143 and L-shaped bent part 145 are respectively formed by a combination of a plurality of circular arcs and straight lines.
  • Communication tube 155 having one end (second end) opening to sound deadening space 139 and the other end (first end) coupling to suction port 131 formed in valve plate 127 of compression element 105 by way of cylinder head 135 is arranged in suction muffler 137.
  • Opening 163 through which communication tube 155 opens to expansion chamber 151 of sound deadening space 139 is formed at a position of L2/2, which is at the middle of space length L2 of sound deadening space 139 in the opening direction.
  • Opening directions of tail tube 147 and communication tube 155 to expansion chamber 151 of sound deadening space 139 are orthogonal, and the opened positions of opening 161 of tail tube 147 and opening 163 of communication tube 155 are proximate to each other.
  • Side branch resonator 149 is a side branch type in which a throttle part is not formed at the communicating portion with L-shaped bent part 145 of tail tube 147.
  • Side branch resonator 149 is partitioned into a plurality of portions having different depths (resonance frequencies) by partition wall 165, which resonance frequencies substantially match the high-pass resonance frequencies (e.g., about 2000 Hz or about 2500 Hz) generated at side surface portions and the like having small curvature in hermetic container 101.
  • the partition is made to two portions which match about 2000 Hz and about 2500 Hz.
  • crankshaft 125 When crankshaft 125 is rotatably driven by the rotation of rotor 107 of electric powered element 111, piston 117 reciprocates in cylinder 119 through connecting rod 123 by the eccentric motion of crank pin 121 and performs a predetermined compressing operation.
  • the suction stroke of piston 117 the refrigerant gas filling the space in hermetic container 101 is taken in from suction port 141 of tail tube 147 of suction muffler 137.
  • the refrigerant gas is then led to suction valve 129 closing suction port 131 of valve plate 127 through a suction flow channel formed by expansion chamber 151, communication tube 155, and cylinder head 135, and is flowed into compression chamber 133 by pushing open suction valve 129.
  • the noise generated as the vibration sound of suction valve 129 of valve plate 127 and the pulsation sound of the refrigerant gas is sound- deadened by expansion chamber 151, and released to the inside of hermetic container 101 through L-shaped bent part 145 and vertical part 143 of tail tube 147.
  • the high-pass resonance frequency e.g., about 2000 Hz and about 2500 Hz
  • the position of opening 161 where one end of L-shaped bent part 145 opens to expansion chamber 151 configuring sound deadening space 139 is at the middle of space length L 1 of sound deadening space 139 in the opening direction, and thus is a position of substantially the node of the acoustic mode of the space length of sound deadening space 139. Therefore, the sound pressure radiated to the inside of hermetic container 101 through L-shaped bent part 145 and vertical part 143 becomes extremely small.
  • the position where one end of L-shaped bent part 145 opens to expansion chamber 151 configuring sound deadening space 139 is defined by the combination of a plurality of straight lines and circular arcs of connecting parts 157, 159 of vertical part 143 and L-shaped bent part 145, and thus L-shaped bent part 145 will not shift in a rotating direction in the axis of vertical part 143.
  • the noise is less likely to be transmitted to the outside of suction muffler 137 by having the positions of opening 161 where L-shaped bent part 145 of tail tube 147 opens to expansion chamber 151 configuring sound deadening space 139 and opening 163 where communication tube 155 opens to expansion chamber 151 configuring sound deadening space 139 at the middle of space lengths Li, L2 of sound deadening space 139 in the respective opening directions.
  • Opening 161 and opening 163 where L-shaped bent part 145 configuring tail tube 147 and communication tube 155 respectively open to expansion chamber 151 configuring sound deadening space 139 are proximate to each other, and an angle formed by a line connecting the two openings and each of the opening directions is smaller than or equal to 90°. Therefore, the suction flow of the refrigerant gas becomes smoother, the heat receiving loss decreases, and the refrigerating efficiency is enhanced.
  • Side branch resonator 149 partitioned into a plurality of portions having different resonance frequencies by partition wall 165 is arranged at Lrshaped bent part 145 of tail tube 147.
  • frequency f (resonance frequency f) of the noise that can be sound- deadened by a side branch resonance muffler is defined by length Lp and inner diameter D of the resonance chamber of the muffler, as well as sound velocity C of the refrigerant gas in the muffler.
  • Frequency f is expressed by Equation 1.
  • n is a natural number
  • the inner diameter and the length of side branch resonator 149 are adjusted, so that the resonance frequency substantially matches the high-pass resonance frequency (e.g., about 2000 Hz and about 2500 Hz) of hermetic container 101.
  • the high-pass resonance frequency e.g., about 2000 Hz and about 2500 Hz
  • suction muffler 137 is made of resin material and is integrally molded with side branch resonator 149, so that the leakage of refrigerant gas at side branch resonator 149 does not occur.
  • side branch resonator 149 When lubricating oil 103 taken into tail tube 147 along with the refrigerant gas collects in side branch resonator 149, length Lp of side branch resonator 149 changes and thus resonance frequency f changes as expressed by (Eq. l).
  • side branch resonator 149 is formed with the opening to L-shaped bent part 145 oriented downward, and thus lubricating oil 103 will not collect in side branch resonator 149.
  • side branch resonator 149 is partitioned into a plurality of portions having different depths, that is, resonance frequencies by partition wall 165, noises of a plurality of high-pass resonance frequencies of hermetic container 101 can be reduced.
  • tail tube 147 includes Lr shaped bent part 145, and side branch resonator 149 is extended and formed on one axis line of
  • L-shaped bent part 145 L-shaped bent part 145. Therefore, L-shaped bent part 145 and side branch resonator 149 can be not only integrally molded by a die, but the die can be easily removed, since the stroke in the molding process is small. Resonance frequency ' f of side branch resonator 149 does not change since leakage of the refrigerant gas at the communicating portion of L-shaped bent part 145 and side branch resonator 149 does not occur due to the integral molding.
  • side branch resonator 149 is formed with the opening to Lrshaped bent part 145 oriented downward. Therefore, lubricating oil 103 will not collect in side branch resonator 149, the length of side branch resonator 149 does not change, and resonance frequency f of side branch resonator 149 does not change.
  • suction muffler 137 stably maintains the sound deadening characteristics of the frequency that substantially matches the high-pass resonance frequency (e.g., about 2000 Hz and about 2500 Hz) of hermetic container 101.
  • Fig. 5 is a characteristic chart showing sound deadening characteristics of the suction muffler according to embodiment 1 of the present invention and the suction muffler according to the prior art.
  • characteristic curve a indicates a level of sound deadening characteristic of suction muffler 137 according to the technique of the present invention and characteristic curve b indicates a level of sound deadening characteristic of the suction muffler according to the technique of the prior art. It is apparent that the sound deadening effect from 2000 Hz to 3000 Hz is greatly improved in characteristic curve a compared to characteristic curve b. This is because the positions of opening 161 of tail tube 147 and opening 163 of communication tube 155 are at the middle of space lengths L 1 , L2 of sound deadening space 139, and side branch resonator 149 partitioned into a plurality of portions having different resonance frequencies by partition wall 165 is arranged on Lrshaped bent part 145. Fig.
  • characteristic curve c indicates a level of resonance characteristics of hermetic container 101. It can be recognized that a plurality of resonance frequencies exist in a high frequency region at higher than or equal to 2000 Hz.
  • Fig. 7 is a characteristic chart showing a noise level of the refrigerant compressor according to embodiment 1 of the present invention and the prior art.
  • characteristic curve d indicates a noise level of the refrigerant compressor lowered by the sound deadening function of suction muffler 137.
  • Characteristic curve e indicates a noise level of the refrigerant compressor at the suction muffler of the prior art.
  • the noise level at frequency f (about 2000 Hz and about 2500 Hz) around the high-pass resonance frequency of hermetic container 101 is greatly reduced by suction muffler 137 of the present invention. Accordingly, generation of noise by resonance of hermetic container
  • the resonator of side branch type has been illustrated in embodiment 1, but high sound deadening characteristics can be obtained even if a Helmholtz resonator or a perforated tube resonator is arranged in tail tube 147.
  • the refrigerant compressor according to the present invention thus can reduce generation of noise caused by resonance of the hermetic container, and can be applied to refrigerant compressors of air conditioners, refrigerator-freezers and the like.

Abstract

Suction muffler (137) includes tail tube (147) having one end opening to sound deadening space (139) and communication tube (155) having one end opening to sound deadening space (139), where respective openings (161), (163) are at the middle of sound deadening space (139) and side branch resonator (149) having a resonance frequency that substantially matches a high-pass resonance frequency of hermetic container is arranged at tail tube (147). According to a refrigerant compressor having such a configuration, generation of noise caused by resonance of hermetic container can be reduced by suppressing radiation of noise that substantially matches the high-pass resonance frequency of hermetic container and further sound-deadening the same with side branch resonator (149).

Description

DESCRIPTION
REFRIGERANT COMPRESSOR
TECHNICAL FIELD The present invention relates to a refrigerant compressor used in a refrigerating cycle of a refrigerator-freezer and the like.
BACKGROUND ART
Conventionally, this type of refrigerant compressor includes that in which a resonance chamber is arranged in a suction muffler, which is opened to the inside of a hermetic container, for taking in refrigerant gas to reduce the sound of a specific frequency. The technical content thereof is disclosed in Unexamined Japanese Patent Publication No. 10-184542.
The conventional refrigerant compressor will be described below with reference to the drawings.
Fig. 8 is a partially cut perspective view showing an overall configuration of the conventional refrigerant compressor. Fig. 9 is a partially cut perspective view of one part of a compression element and an suction muffler of the conventional refrigerant compressor. In Figs. 8 and 9, hermetic container 1 for storing lubricating oil (not shown) supports and accommodates, by way of elastic body 11 such as a spring, compressor body 10 configured by arranging electric powered element 3 and compression element 5 on upper and lower sides of frame 9 including a bearing (not shown) for supporting a crankshaft (not shown) integrally molded to crank pin 7. Crank pin 7 is formed eccentric to the crankshaft fitted into and fixed to a rotor (not shown) configuring electric powered element 3.
Piston 13 is inserted to cylinder 15 having a substantially cylindrical shape in a freely reciprocating and slidably moving manner, and is coupled with crank pin 7 by coupling part 17.
Valve plate 19 for sealing an open end face (not shown) of cylinder 15 includes a suction port (not shown) which communicates with cylinder 15 through opening/closing of a suction valve (not shown), where cylinder 15, top surface (not shown) of piston 13, and valve plate 19 define a compression chamber (not shown).
Cylinder head 21 forming a high pressure chamber is fixed on the side opposite to cylinder 15 by way of valve plate 19.
Suction muffler 23 configures tail tube 27 which is a suction passage of refrigerant gas (not shown) with opening 25 to the inside of hermetic container 1, and resonator 33 including resonance chamber 31 communicating to tail tube 27 by way of throttle hole 29. One end of communication tube 35 is coupled to the suction port formed in valve plate 19 of compression element 5 by way of cylinder head 21, and the other end of communication tube 35 is coupled to suction muffler 23. The operation of the refrigerant compressor configured as above will be described below.
When the crankshaft integrally molded to crank pin 7 is rotatably driven by electric powered element 3, piston 13 reciprocates in cylinder 15 through coupling part 17 due to eccentric motion of crank pin 7, and sequentially performs suction, compression and discharge strokes. In the suction stroke of piston 13, the refrigerant gas filled in a space of hermetic container 1 is taken in from opening 25 of tail tube 27 and led to the suction valve closing the suction port of valve plate 19 through a suction flow channel formed by suction muffler 23, communication tube 35, and cylinder head 21, and then flowed into cylinder 15 by pushing open the suction valve. In this case, resonator 33 sound-deadens low frequency sound (about 400 Hz to about 600 Hz) of the noise generated as vibration sound of the suction valve of valve plate 19 or pulsation sound of the refrigerant gas. The sound in the low frequency region of the refrigerant compressor is reduced as a result.
However, since the sound in high frequency regions is not sufficiently attenuated, suction muffler 23 excites high-pass resonance frequency (e.g., about 2000 Hz or 2500 Hz) of hermetic container 1 molded by draw forming an iron plate through pressing, whereby the high frequency sound becomes higher. Resonator 33 cannot be formed by a single component due to its structure of being formed by resonance chamber 31 communicating to tail tube 27 by way of throttle hole 29, and thus the resonance frequency changes due to leakage of refrigerant gas caused by adherence failure at the joining part, and the noise reducing effect lowers.
DISCLOSURE OF THE INVENTION
The present invention provides a refrigerant compressor of low noise capable of reducing resonance sound generated when high-pass resonance frequency (e.g., about 2000 Hz or 2500 Hz) of the hermetic container is excited by the suction muffler. The refrigerant compressor of the present invention has a sound deadening space formed in a suction muffler communicating to a compression chamber, where the suction muffler includes a tail tube having one end (first end) opening to the inside of a hermetic container and the other end (second end) opening to the sound deadening space, the position in the opening direction of the tail tube in the sound deadening space being at the middle of the sound deadening space. The high frequency sound generated as vibration sound of the suction valve or pulsation sound of the refrigerant gas thus can be reduced by having the opening position of the tail tube in the sound deadening space at the position of the acoustic node in the middle of the sound deadening space where the high frequency sound can be easily attenuated, and excitation of the high-pass resonance frequency (e.g., about 2000 Hz and 2500 Hz) of the hermetic container can be suppressed.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is a side cross sectional view of a refrigerant compressor according to embodiment 1 of the present invention.
Fig. 2 is a front transparent view of the refrigerant compressor according to embodiment 1 of the present invention. Fig. 3 is a front cross sectional view of a suction muffler in embodiment 1 of the present invention.
Fig. 4 is a perspective view of an Lrshaped bent part in embodiment 1 of the present invention.
Fig. 5 is a characteristic chart showing sound deadening characteristics of the suction muffler according to embodiment 1 of the present invention and the suction muffler of the prior art.
Fig. 6 is a characteristic chart showing resonance characteristics of the hermetic container in embodiment 1 of the present invention.
Fig. 7 is a characteristic chart showing noise levels of the refrigerant compressor according to embodiment 1 of the present invention and the prior art.
Fig. 8 is a partially cut perspective view showing an overall configuration of a conventional refrigerant compressor.
Fig. 9 is a partially cut perspective view of one part of a compression element and a suction muffler of the conventional refrigerant compressor.
PREFERRED EMBODIMENTS FOR CARRYING OUT THE INVENTION (Embodiment l)
Embodiment 1 of the present invention will now be described with reference to the drawings. It should be noted that the invention is not limited by embodiment 1.
Fig. 1 is a side cross sectional view of a refrigerant compressor according to embodiment 1 of the present invention. Fig. 2 is a front transparent view of the refrigerant compressor according to embodiment 1 of the present invention. Fig. 3 is a front cross sectional view of a suction muffler in embodiment 1 of the present invention. Fig. 4 is a perspective view of an L-shaped bent part in embodiment 1 of the present invention.
In Figs. 1 to 4, hermetic container 101 stores lubricating oil 103 at the bottom part, and supports and accommodates, by way of elastic body 115 such as a spring, compressor body 113 configured by compression element 105 for taking in and compressing refrigerant gas (not shown), and electric powered element 111 including rotor 107 and stator 109 for driving compression element 105.
Piston 117 is inserted to cylinder 119 of a substantially cylindrical shape in a freely reciprocating and slidably moving manner, and is coupled with crank pin 121 by connecting rod 123 or a coupling part.
Crank pin 121 is formed eccentric to crankshaft 125 fitted into and fixed to rotor 107.
Valve plate 127 for sealing an open end face of cylinder 119 includes suction port 131 which communicates with cylinder 119 through opening/closing of suction valve 129, where cylinder 119, the top surface of piston 117, and valve plate 127 define compression chamber 133.
Cylinder head 135 forming a high pressure chamber is fixed on the side opposite to cylinder 119 by way of valve plate 127. In Fig. 3, suction muffler 137 is made of resin material, and forms sound deadening space 139. Expansion chamber 151 and resonance chamber 153 are arranged in sound deadening space 139.
Tail tube 147 including vertical part 143 and Irshaped bent part 145, and having one end opening to sound deadening space 139 and the other end forming suction port 141 of the refrigerant gas opened to the inside of hermetic container 101 is arranged in suction muffler 137.
Tail tube 147 is formed into a substantially Lrshape by Lrshaped bent part 145, where opening 161 opening to expansion chamber 151 of sound deadening space 139 is formed at a position of Li/2, which is at the middle of space length Li of sound deadening space 139 in the opening direction. The shapes of connecting parts 157, 159 of vertical part 143 and L-shaped bent part 145 are respectively formed by a combination of a plurality of circular arcs and straight lines.
Communication tube 155 having one end (second end) opening to sound deadening space 139 and the other end (first end) coupling to suction port 131 formed in valve plate 127 of compression element 105 by way of cylinder head 135 is arranged in suction muffler 137.
Opening 163 through which communication tube 155 opens to expansion chamber 151 of sound deadening space 139 is formed at a position of L2/2, which is at the middle of space length L2 of sound deadening space 139 in the opening direction.
Opening directions of tail tube 147 and communication tube 155 to expansion chamber 151 of sound deadening space 139 are orthogonal, and the opened positions of opening 161 of tail tube 147 and opening 163 of communication tube 155 are proximate to each other.
Side branch resonator 149 opening downward to L-shaped bent part 145 is extended and formed on one axis line of L-shaped bent part 145 of tail tube 147.
Side branch resonator 149 is a side branch type in which a throttle part is not formed at the communicating portion with L-shaped bent part 145 of tail tube 147. Side branch resonator 149 is partitioned into a plurality of portions having different depths (resonance frequencies) by partition wall 165, which resonance frequencies substantially match the high-pass resonance frequencies (e.g., about 2000 Hz or about 2500 Hz) generated at side surface portions and the like having small curvature in hermetic container 101. In embodiment 1, the partition is made to two portions which match about 2000 Hz and about 2500 Hz.
The operation and the effect of the refrigerant compressor configured as above will be described below. When crankshaft 125 is rotatably driven by the rotation of rotor 107 of electric powered element 111, piston 117 reciprocates in cylinder 119 through connecting rod 123 by the eccentric motion of crank pin 121 and performs a predetermined compressing operation. In the suction stroke of piston 117, the refrigerant gas filling the space in hermetic container 101 is taken in from suction port 141 of tail tube 147 of suction muffler 137. The refrigerant gas is then led to suction valve 129 closing suction port 131 of valve plate 127 through a suction flow channel formed by expansion chamber 151, communication tube 155, and cylinder head 135, and is flowed into compression chamber 133 by pushing open suction valve 129. Of the noise generated as the vibration sound of suction valve 129 of valve plate 127 and the pulsation sound of the refrigerant gas, the noise that substantially matches the high-pass resonance frequency (e.g., about 2000 Hz and about 2500 Hz) generated at the side surface portions and the like having a small curvature in hermetic container 101 is sound- deadened by expansion chamber 151, and released to the inside of hermetic container 101 through L-shaped bent part 145 and vertical part 143 of tail tube 147.
The position of opening 161 where one end of L-shaped bent part 145 opens to expansion chamber 151 configuring sound deadening space 139 is at the middle of space length L1 of sound deadening space 139 in the opening direction, and thus is a position of substantially the node of the acoustic mode of the space length of sound deadening space 139. Therefore, the sound pressure radiated to the inside of hermetic container 101 through L-shaped bent part 145 and vertical part 143 becomes extremely small. The position where one end of L-shaped bent part 145 opens to expansion chamber 151 configuring sound deadening space 139 is defined by the combination of a plurality of straight lines and circular arcs of connecting parts 157, 159 of vertical part 143 and L-shaped bent part 145, and thus L-shaped bent part 145 will not shift in a rotating direction in the axis of vertical part 143. The position of opening 163 where one end of communication tube
155 opens to expansion chamber 151 configuring sound deadening space 139 is at the middle of space length L2 of sound deadening space 139 in the opening direction, and thus is a position of substantially the node of the acoustic mode of the space length of sound deadening space 139. Therefore, the excitation in the acoustic mode becomes small and the amplification of noise in sound deadening space 139 is suppressed.
Thus, the noise is less likely to be transmitted to the outside of suction muffler 137 by having the positions of opening 161 where L-shaped bent part 145 of tail tube 147 opens to expansion chamber 151 configuring sound deadening space 139 and opening 163 where communication tube 155 opens to expansion chamber 151 configuring sound deadening space 139 at the middle of space lengths Li, L2 of sound deadening space 139 in the respective opening directions.
Opening 161 and opening 163 where L-shaped bent part 145 configuring tail tube 147 and communication tube 155 respectively open to expansion chamber 151 configuring sound deadening space 139 are proximate to each other, and an angle formed by a line connecting the two openings and each of the opening directions is smaller than or equal to 90°. Therefore, the suction flow of the refrigerant gas becomes smoother, the heat receiving loss decreases, and the refrigerating efficiency is enhanced.
Side branch resonator 149 will now be described.
Side branch resonator 149 partitioned into a plurality of portions having different resonance frequencies by partition wall 165 is arranged at Lrshaped bent part 145 of tail tube 147. Generally, frequency f (resonance frequency f) of the noise that can be sound- deadened by a side branch resonance muffler is defined by length Lp and inner diameter D of the resonance chamber of the muffler, as well as sound velocity C of the refrigerant gas in the muffler. Frequency f is expressed by Equation 1.
f= ^ -^ - (Eq. 1)
MLp + 0.8D)
where n is a natural number.
In the refrigerant compressor according to embodiment 1 of the present invention, the inner diameter and the length of side branch resonator 149 are adjusted, so that the resonance frequency substantially matches the high-pass resonance frequency (e.g., about 2000 Hz and about 2500 Hz) of hermetic container 101.
In the resonance muffler, when leakage of the refrigerant gas occurs in side branch resonator 149, length Lp and inner diameter D of side branch resonator 149 change, and resonance frequency f changes as expressed by (Eq. l). In the refrigerant compressor according to embodiment 1 of the present invention, suction muffler 137 is made of resin material and is integrally molded with side branch resonator 149, so that the leakage of refrigerant gas at side branch resonator 149 does not occur. When lubricating oil 103 taken into tail tube 147 along with the refrigerant gas collects in side branch resonator 149, length Lp of side branch resonator 149 changes and thus resonance frequency f changes as expressed by (Eq. l). In the refrigerant compressor according to . embodiment 1 of the present invention, side branch resonator 149 is formed with the opening to L-shaped bent part 145 oriented downward, and thus lubricating oil 103 will not collect in side branch resonator 149.
Therefore, the sound pressure radiated to the inside of hermetic container 101 can be further reduced by side branch resonator 149. In this case, since side branch resonator 149 is partitioned into a plurality of portions having different depths, that is, resonance frequencies by partition wall 165, noises of a plurality of high-pass resonance frequencies of hermetic container 101 can be reduced.
Furthermore, in the refrigerant compressor according to embodiment 1 of the present invention, tail tube 147 includes Lr shaped bent part 145, and side branch resonator 149 is extended and formed on one axis line of
L-shaped bent part 145. Therefore, L-shaped bent part 145 and side branch resonator 149 can be not only integrally molded by a die, but the die can be easily removed, since the stroke in the molding process is small. Resonance frequency' f of side branch resonator 149 does not change since leakage of the refrigerant gas at the communicating portion of L-shaped bent part 145 and side branch resonator 149 does not occur due to the integral molding.
Furthermore, side branch resonator 149 is formed with the opening to Lrshaped bent part 145 oriented downward. Therefore, lubricating oil 103 will not collect in side branch resonator 149, the length of side branch resonator 149 does not change, and resonance frequency f of side branch resonator 149 does not change.
Accordingly, during the operation of the refrigerant compressor, suction muffler 137 stably maintains the sound deadening characteristics of the frequency that substantially matches the high-pass resonance frequency (e.g., about 2000 Hz and about 2500 Hz) of hermetic container 101.
Fig. 5 is a characteristic chart showing sound deadening characteristics of the suction muffler according to embodiment 1 of the present invention and the suction muffler according to the prior art.
In Fig. 5, characteristic curve a indicates a level of sound deadening characteristic of suction muffler 137 according to the technique of the present invention and characteristic curve b indicates a level of sound deadening characteristic of the suction muffler according to the technique of the prior art. It is apparent that the sound deadening effect from 2000 Hz to 3000 Hz is greatly improved in characteristic curve a compared to characteristic curve b. This is because the positions of opening 161 of tail tube 147 and opening 163 of communication tube 155 are at the middle of space lengths L1, L2 of sound deadening space 139, and side branch resonator 149 partitioned into a plurality of portions having different resonance frequencies by partition wall 165 is arranged on Lrshaped bent part 145. Fig. 6 is a characteristic chart showing a resonance characteristic of the hermetic container in embodiment 1 of the present invention. In Fig. 6, characteristic curve c indicates a level of resonance characteristics of hermetic container 101. It can be recognized that a plurality of resonance frequencies exist in a high frequency region at higher than or equal to 2000 Hz.
Fig. 7 is a characteristic chart showing a noise level of the refrigerant compressor according to embodiment 1 of the present invention and the prior art. In Fig. 7, characteristic curve d indicates a noise level of the refrigerant compressor lowered by the sound deadening function of suction muffler 137. Characteristic curve e indicates a noise level of the refrigerant compressor at the suction muffler of the prior art. As apparent from the graph, the noise level at frequency f (about 2000 Hz and about 2500 Hz) around the high-pass resonance frequency of hermetic container 101 is greatly reduced by suction muffler 137 of the present invention. Accordingly, generation of noise by resonance of hermetic container
101 can be stably reduced.
The resonator of side branch type has been illustrated in embodiment 1, but high sound deadening characteristics can be obtained even if a Helmholtz resonator or a perforated tube resonator is arranged in tail tube 147.
INDUSTRIAL APPLICABILITY
The refrigerant compressor according to the present invention thus can reduce generation of noise caused by resonance of the hermetic container, and can be applied to refrigerant compressors of air conditioners, refrigerator-freezers and the like.

Claims

1. A refrigerant compressor comprising a hermetic container, the hermetic container retaining lubricating oil and accommodating a compression element, wherein the compression element includes^ a compression chamber in which refrigerant gas is compressed; and a suction muffler communicating to the compression chamber and forming a sound deadening space, and the suction muffler includes a tail tube having a first end opening to an inside the hermetic container and a second end opening to the sound deadening space, a position in an opening direction of the tail tube in the sound deadening space being at a middle of the sound deadening space.
2. The refrigerant compressor according to claim 1, wherein the suction muffler includes a communication tube having a first end opening to an inside the compression chamber and a second end opening to the sound deadening space, and having an opening direction in the sound deadening space orthogonal to the opening direction of the tail tube in the sound deadening space, and a position in the opening direction of the communication tube in the sound deadening space is at a middle of the sound deadening space.
3. The refrigerant compressor according to claim 2, wherein an opening of the tail tube in the sound deadening space is proximate to an opening of the communication tube in the sound deadening space.
4. The refrigerant compressor according to any one of claims 1 to 3, wherein the tail tube includes: a vertical part extending in a vertical direction; and an L-shaped bent part bent into an Lrshape in continuation from the vertical part and having the second end opening to the sound deadening space.
5. The refrigerant compressor according to claim 4, wherein a side branch resonator opening downward is arranged on an extended line of the vertical part of the tail tube.
6. The refrigerant compressor according to claim 5, wherein the side branch resonator is partitioned by a partition wall to have a plurality of resonance frequencies.
EP07850311A 2006-12-06 2007-12-03 Refrigerant compressor Withdrawn EP1971777A1 (en)

Applications Claiming Priority (2)

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JP2006328994 2006-12-06
PCT/JP2007/073737 WO2008069334A1 (en) 2006-12-06 2007-12-03 Refrigerant compressor

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EP1971777A1 true EP1971777A1 (en) 2008-09-24

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JP5338355B2 (en) * 2009-02-13 2013-11-13 パナソニック株式会社 Hermetic compressor and refrigeration system
JP2011144719A (en) * 2010-01-13 2011-07-28 Sanden Corp Compressor
SE535923C2 (en) * 2011-04-29 2013-02-19 Scania Cv Ab Silencer and motor vehicles including such silencer
JP5632334B2 (en) * 2011-06-10 2014-11-26 サンデン株式会社 Compressor suction muffler
JP2013231429A (en) * 2012-04-06 2013-11-14 Panasonic Corp Hermetic compressor
CN108915997A (en) * 2018-08-24 2018-11-30 珠海格力节能环保制冷技术研究中心有限公司 Silencer, compressor assembly and refrigerator

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KR200141490Y1 (en) 1993-04-24 1999-05-15 김광호 Noise-reducing apparatus of a compressor
JPH11311180A (en) * 1998-04-28 1999-11-09 Matsushita Refrig Co Ltd Enclosed type electric compressor
JP4232235B2 (en) * 1998-10-23 2009-03-04 パナソニック株式会社 Scarf
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KR101128155B1 (en) 2012-03-23
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WO2008069334A1 (en) 2008-06-12
CN101196183B (en) 2010-08-04
JP4735718B2 (en) 2011-07-27
CN101196183A (en) 2008-06-11
JP2009523938A (en) 2009-06-25

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