CN1701179A - Hermetic compressor - Google Patents

Hermetic compressor Download PDF

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Publication number
CN1701179A
CN1701179A CNA2004800007240A CN200480000724A CN1701179A CN 1701179 A CN1701179 A CN 1701179A CN A2004800007240 A CNA2004800007240 A CN A2004800007240A CN 200480000724 A CN200480000724 A CN 200480000724A CN 1701179 A CN1701179 A CN 1701179A
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CN
China
Prior art keywords
sound
opening
communication passage
sound insulation
wall
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.)
Pending
Application number
CNA2004800007240A
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Chinese (zh)
Inventor
中野明
稻垣耕
石田贵规
杉本修平
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Panasonic Holdings Corp
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Matsushita Electric Industrial Co Ltd
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Filing date
Publication date
Application filed by Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of CN1701179A publication Critical patent/CN1701179A/en
Pending legal-status Critical Current

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    • 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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • 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
    • 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
    • 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
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/08—Compressors specially adapted for separate outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/08—Compressors specially adapted for separate outdoor units
    • F24F1/12—Vibration or noise prevention thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2280/00—Materials; Properties thereof
    • F05B2280/60—Properties or characteristics given to material by treatment or manufacturing
    • F05B2280/6015—Resin
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/13—Vibrations

Abstract

A compressing unit of a hermetic compressor includes a suction valve placed at an opening of a compressing room and a suction muffler. The muffler includes a suction muffler body which forms a sound-deadening space, a first communicating path which communicates with the suction valve and with the sound-deadening space, and a second communicating path which communicates with a hermetic container and with the sound-deadening space. An opening, situated in the sound-deadening space, of the first communicating path, and an opening, situated in the sound-deadening space, of the second communicating path are both open in the same direction. In addition, a sound-insulating wall is disposed on the wall of the muffler body at a place at least confronting both of the openings. This structure achieves low noise and high efficiency.

Description

Hermetic compressor
Technical field
The present invention relates to be used for the hermetic compressor of refrigerator, air-conditioning and chiller plant.
Background technique
Use the hermetic compressor in chiller plant and other equipment need reduce running noises and more effectively utilize the energy in recent years.The publication number of Japanese unexamined is that the patent application of 2003-42064 discloses a kind of traditional hermetic compressor.This hermetic compressor (being designated hereinafter simply as compressor) has improved the soundproof effect of its absorbing silencer (suction muffler), and utilizes this soundproof effect to increase the interior refrigeration cycle amount of pressing chamber, obtains higher energy efficiency thus.The publication number of Japanese unexamined is that the patent application of H11-303739 discloses another kind of traditional hermetic compressor.This compressor makes the refrigerant gas that returns from refrigeration cycle keep low temperature and high density, and refrigerant gas is inhaled in the pressing chamber then, obtains higher energy efficiency thus.
Below with reference to Fig. 6-Fig. 8 above-mentioned traditional compressor is described.Fig. 6 has shown the sectional view of traditional compressor, and Fig. 7 has shown the sectional view of the absorbing silencer of traditional compressor, and Fig. 8 has shown the flow-rate vectors of the refrigerant gas running in the absorbing silencer of explanation in traditional compressor.
In Fig. 6, compression unit 6 and oil wherein 8 that closed container 1 comprises by rotor 4 and has motor unit 5 that the stator 3 of coil 2 constitutes, driven by motor unit 5.
The following describes the rough structure of compression unit 6.Bent axle 10 comprises main shaft 11 that rotor 4 extruding cooperates and with respect to the eccentric part 12 of main shaft 11.Oil pump 13 is arranged in main shaft 11 and opens at oil 8.The cylinder block 20 that is positioned at the top of motor unit 5 has cylinder pressing chamber 22 and rotates the bearing 23 of supports main shaft 11.Piston 30 is inserted in the pressing chamber 22 so that its to-and-fro motion in pressing chamber 22, and it is connected on the eccentric part 12 via coupling piece 31.
Valve plate 35 has been sealed the opening of pressing chamber 22, and valve plate 35 comprises sucking hole 38, and when absorbing valve 34 and open, this sucking hole 38 can communicate with pressing chamber 22.Cylinder head 36 is positioned over the opposite of pressing chamber 22 rigidly by valve plate 35.Absorption tube 37 is fixed on the closed container 1 and a lower (not shown) on the pressure side being connected to refrigeration cycle is used to guide the refrigerant gas (not shown) to enter in the container 1.Absorbing silencer 40 is made by the synthetic resin of the polybutylene-terephthalate that for example adds glass fibre, and is clipped in the middle rigidly by valve plate 35 and cylinder head 36.
In Fig. 7, absorbing silencer 40 has first communication passage 45 and second communication passage 46.More particularly, absorbing silencer 40 comprises sound insulation space 43, and has second communication passage 46, and the first opening 46b wherein communicates with closed container 1 and the second opening 46a extends to sound insulation space 43 split sheds.Absorbing silencer 40 also has first communication passage 45, and the first opening 45b wherein communicates with the sucking hole 38 of valve plate 35 and the second opening 45a extends to sound insulation space 43 split sheds.
Fig. 8 has shown the flow-rate vectors 60 of the refrigerant gas running in the explanation absorbing silencer 40.Can obtain flow-rate vectors by computer simulation.Each vector shows that with their length the amplitude of flow velocity and the direction indication of vector flow to.
Last eddy current 61 by the arrow mark indication is made of the refrigerant gas that upwards flows out that absorbs from the opening 46a of second communication passage 46.Constitute by the following turbine 62 of another arrow mark indication refrigerant gas by the downward outflow that from opening 46a, absorbs.
The below operation of the above-mentioned traditional compressor of explanation.Stator 4 rotary crankshafts 10 of motor unit 5, and rotatablely moving of eccentric part 12 be sent on the piston 30 via coupling piece 31, so that piston 30 to-and-fro motion in pressing chamber 22.This mechanism guides enters into closed container 1 from the refrigerant gas of refrigeration system (not shown) through absorption tube 37.The refrigerant gas of introducing in container 1 is sucked from the opening 46b of absorbing silencer 40 and is discharged in the sound insulation space 43 from the opening 46a of second communication passage 46.The refrigerant gas of discharging forms then and goes up eddy current 61 and following eddy current 62 at nearest and wall run into absorbing silencer 40 towards the position of opening 46a, and circulation in sound insulation space 43.The refrigerant gas of going up eddy current 61 then is drawn into first communication passage 45 from opening 45a, and is directed into the sucking hole 38 of punching on valve plate 35.When absorption valve 34 was opened, refrigerant gas was inhaled in the pressing chamber 22, and is compressed by to-and-fro motion, is discharged to refrigeration system then.
When refrigeration agent was absorbed in the pressing chamber 22, refrigeration agent produced pressure pulsation, and this pressure pulsation is propagated on the opposite direction of flow of refrigerant, promptly 43 propagated to the sound insulation space from the opening 45a of first communication passage 45.In this case, first communication passage 45 extends in the sound insulation space 43 with high soundproof effect, and for example opening 45a is positioned on the sound node of the 3-4kHz that can produce noise problem, therefore obtains high soundproof effect in specific frequency band.
If the length and the inner diameter of the size in sound insulation space 43 and second communication passage 46 are adjusted suitably, the pressure pulsation that weakens in the sound insulation space 43 can further be weakened, and this will produce more effective sound insulation.
Yet in above-mentioned conventional construction, because the to-and-fro motion of piston 30, refrigerant gas is drawn in the absorbing silencer 40 via container 1 from the refrigeration system (not shown), and gas is discharged in the sound insulation space 43 by second communication passage 46 then.As shown in Figure 8, refrigerant gas does not directly flow in first communication passage 45, but nearest and towards the wall of the position of opening 46a collisional absorption silencing apparatus 40, form then and go up eddy current 61 and following eddy current 62, and circulate in sound insulation space 43.The refrigerant gas that returns from refrigeration system is maintained at low temperature; Yet owing to pass through the nearest wall and the heat exchange of high temperature refrigerant gas in closed container 1, gas is heated greatly.In addition, because the temperature of refrigerant gas rises, the circulating air flow that is made of last eddy current 61 and following eddy current 62 is heated by refrigerant gas residual in the sound insulation space 43.Then, circulating air flow is sucked by the opening 45a from first communication passage 45, and flows in the pressing chamber 22.Therefore, pressing chamber 22 has reduced the mass flow rate ratio of the refrigeration agent that wherein will be inhaled into, and has therefore reduced absorption efficiency.
The refrigerant gas that is discharged to sound insulation space 43 among the opening 46a from second communication passage 46 has formed last eddy current 61 and following eddy current 62.Therefore the fluid inertia force that is inhaled into the refrigerant gas in the sound insulation space 43 passes sound insulation space 43 significantly to be reduced to 45a from opening 46a, and this reduction causes the bigger pressure loss.Therefore, be inhaled into into that the mass flow rate ratio of the refrigerant gas of pressing chamber 22 is further reduced, this has worsened absorption efficiency.
The opening 45a of first communication passage 45 near and place towards the wall of absorbing silencer 40, and pressure pulsation becomes maximum value at opening 45a, and is close like this and be stimulated towards the wall of opening 45a.Therefore, the pulsation sound of refrigeration agent sends from absorbing silencer 40, has increased noise.
Fig. 9 has shown the sectional view of the absorbing silencer 50 that another traditional compressor is described.Below with reference to Fig. 9 described another traditional compressor is described.Except absorbing silencer 50, the structure of this compressor is the same with above-mentioned traditional compressor, therefore the detailed description that will omit this compressor.
In Fig. 9, absorbing silencer 50 comprises around the resonant space 58 that absorbs space 57.First communication passage 55 has towards first end that absorbs space 57 openings with via absorbing second end that valve 34 is communicated with pressing chamber 22.First communication passage 55 communicates with resonant space 58 via intercommunicating pore 59.Second communication passage 56 has first end of connection container 1 and is communicated with second end that absorbs space 57.
The work of above-mentioned compressor hereinafter will be described.The refrigerant gas that keeps low temperature and return from the refrigeration system (not shown) is absorbed in the absorption space 57 of absorbing silencer 50 from second communication passage 56.Then, this gas is absorbed in the pressing chamber 22 from first communication passage 55.At this moment, surrounded by resonant space 58,, absorb space 57 by adiabatic by the wall of refrigerant gas in the resonant space 58 and resonant space 58 because absorb space 57.This structure prevents that the refrigerant gas in absorbing space 57 from directly being heated by the refrigerant gas that is in high temperature and remain in the closed container 1.Therefore, highdensity refrigerant gas can be absorbed in the pressing chamber 22, has therefore improved absorption efficiency.Because resonant space 58 communicates with absorbing the space via intercommunicating pore 59, resonant space 58 also as a resonant space job, has reduced noise thus.
Yet, in conventional construction, surrounded by resonant space 58 as the absorption space 57 of parts of absorbing silencer 50.Therefore, the refrigerant gas that this structure prevents to absorb in the space 57 is directly heated by the refrigerant gas that is in high temperature in the closed container 1, has improved absorption efficiency thus.Yet, the same with aforesaid traditional compressor, from second communication passage 56, absorb the refrigerant gas that absorbs in the space 57 and before arriving first communication passage 55, form huge eddy current, produced a lot of pressure losses like this.Therefore, pressing chamber 22 has reduced the mass flow rate ratio of the refrigerant gas that is inhaled into wherein, has reduced absorption efficiency like this.
Absorb space 57 and surrounded by resonant space 58 fully, absorbing silencer 50 is made the as a whole large volume that becomes like this, and needs a large amount of parts, perhaps needs complicated casting.
Summary of the invention
Hermetic compressor of the present invention comprises following parts:
A closed container comprises a motor unit and a compression unit that is driven by this motor unit,
Described compression unit has the absorption valve and the absorbing silencer that are positioned at the opening of pressing chamber;
Described absorbing silencer has with lower member:
Form the suction muffler body in sound insulation space;
First communication passage is used to be communicated with described absorption valve and described sound insulation space; With
Second communication passage is used to be communicated with described closed container and described sound insulation space.
The opening that is arranged in the opening of first communication passage in sound insulation space and second communication passage that is arranged in same space is all in identical direction upper shed.The wall of suction muffler body has a sound-proof wall towards the position of two openings that are arranged in described sound insulation space at least.
This structure can suppress the heating of the gas of inspiration absorbing silencer, has increased efficient thus.Sound-proof wall is brought into play its sound-absorbent, has suppressed to propagate into via first communication passage from pressing chamber the reflected wave of the wall of muffler body like this.Therefore, can reduce transfer voice.
Description of drawings
Fig. 1 is the sectional view of the hermetic compressor of first exemplary embodiments according to the present invention;
Fig. 2 is the sectional view of the absorbing silencer of first exemplary embodiments according to the present invention;
Fig. 3 is the perspective exploded view of the absorbing silencer of first exemplary embodiments according to the present invention;
Fig. 4 is the sectional view of the absorbing silencer of second exemplary embodiments according to the present invention;
Fig. 5 is the flow-rate vectors in the absorbing silencer of second exemplary embodiments according to the present invention;
Fig. 6 is the sectional view of conventional hermetic-type compressor;
Fig. 7 is the sectional view of the absorbing silencer of conventional hermetic-type compressor;
Fig. 8 is the flow-rate vectors in the absorbing silencer of conventional hermetic-type compressor;
Fig. 9 is the sectional view of the absorbing silencer of conventional hermetic-type compressor.
Embodiment
Hereinafter with reference description of drawings exemplary embodiments of the present invention.
Exemplary embodiments 1
Fig. 1 is the sectional view of the hermetic compressor (hereinafter referred is a compressor) of first exemplary embodiments according to the present invention.
Fig. 2 is the sectional view according to the absorbing silencer of first embodiment's compressor.Fig. 3 is the perspective exploded view according to the absorbing silencer of first embodiment's compressor.
Among Fig. 1, closed container 101 comprises with lower member:
Have the stator 103 of coil 102 and the motor unit 105 that rotor 104 constitutes;
Compression unit 106 by motor unit 105 drivings; With
Reside in oil 108 wherein.
Next the general structure of compression unit 106 is described.Bent axle 110 comprises the main shaft 111 of extruding cooperation rotor 104 and is eccentric in the eccentric part 112 of main shaft 111.Oil pump 113 is arranged in main shaft 111 and opens at oil 108.The cylinder block 120 that is positioned at the top of motor unit 105 has cylinder pressing chamber 122 and rotates the bearing 123 of supports main shaft 111.Piston 130 is inserted in the pressing chamber 122 so that it can to-and-fro motion in pressing chamber 122, and it is connected on the eccentric part 112 by coupling piece 131.
Valve plate 135 has been sealed the opening of pressing chamber 122, and valve plate 135 comprises sucking hole 138, and when absorbing valve 134 and open, this sucking hole 138 can communicate with pressing chamber 122.Cylinder head 136 is fixed on the opposite of pressing chamber 122 by valve plate 135.Absorption tube 137 is fixed on the closed container 101 and a lower (not shown) on the pressure side being connected to refrigeration cycle is used to guide the refrigerant gas (not shown) in closed container 101.Absorbing silencer 140 is made by the synthetic resin that for example mainly adds the polybutylene-terephthalate of glass fibre, and is clipped in the middle rigidly by valve plate 135 and cylinder head 136.
In Fig. 2 and Fig. 3, absorbing silencer 140 comprises suction muffler body 141, suction muffler lid 142, first communication passage 145 and second communication passage 146.Absorbing silencer 140 portion within it forms sound insulation space 143.In sound insulation space 143, opening 145a and 146a are in identical direction upper shed.Sound-proof wall 151 is positioned at least on the wall of the muffler body 141 of the position of opening 145a and 146a.The outer wall of sound-proof wall 151 and muffler body 141 forms the double-walled that limits blocked space 150.Therefore, sound-proof wall 151 is as the part work of suction muffler body 141 and as the wall that marks off blocked space 150 from sound insulation space 143.
Sound-proof wall 151 is placed about the separation surfaces (opening surface of muffler body) of casting synthetic resin is vertical.After first communication passage 145 was mounted in the muffler body 141, welding projection part 145b was placed among the hole 142b that covers punching on 142.Cover on 142 by muffler body 141 being connected to then, realize absorbing silencer 140 thus with method for ultrasound welding.
The below work of the above-mentioned closed compression device of explanation.In conventional suction muffler 40, the temperature of refrigerant gas about 10K that during moving to opening 45b, raise from opening 46b, this gas finally is sucked in the pressing chamber 22 then.The temperature of this refrigerant gas move to from the opening 46a that gas is discharged to sound insulation space 43 opening 45a during about 4K that also raise.
Yet, in this embodiment, blocked space 150 forms in the part of the wall of absorbing silencer 140, that is to say, effect of heat insulation increases on the wall in this section, therefore uses the space littler than the conventional muffler that is all covered by double-walled can obtain effectively heat isolation.Therefore, refrigerant gas can advantageously be remained on low temperature and high density, has improved the mass flow rate ratio of the gas that sucks thus.
The above-mentioned reduction of heating and cooling gas can suppress the temperature increase and is no more than 2K between opening 146a and 145a, and refrigerating capacity is compared with the refrigerating capacity of conventional muffler like this increases by 1.5%, and efficient (the COP=coefficient of performance) increases and is no less than 1.0%.
On the other hand, the refrigerant gas in absorbing silencer 140 responds the to-and-fro motion of piston 130 and becomes intermittent current.At this moment, pressure pulsation, and produces towards recently and in the face of the reflected wave of the wall of opening 145a propagating with the reverse direction of refrigerant gas stream from the opening 145a of pressing chamber 22 to first communication passage 145.The sound-absorbing effect of the blocked space 150 that is made of sound-proof wall 151 has suppressed the propagation of reflected wave to the outside of absorbing silencer 140.Except this inhibition, sound insulation is from 151 intensity of having strengthened the external frame of absorbing silencer 140 again, prevents that thus the absorbing silencer ripple that is reflected from exciting.This prevention is effective especially for the reduction of the sound transmission of the radio-frequency component in the audio-frequency band.
The vertical placement of the separation surfaces (open surfaces of muffler body) of the moulding of sound-proof wall 151 relative absorbing silencers 140 makes that the direction of traction of mould of muffler body 141 is consistent with the direction of isolates sound wall 151.This structure prevents that mould is complicated and prevents increasing of number of components owing to separate some parts in direction of traction.Therefore, this structure can not cause the extra cost to mould, and makes that making absorbing silencer becomes simple.
In this embodiment, the blocked space 150 that is made of sound-proof wall 151 is isolated from sound insulation space 143 fully; Yet, intercommunicating pore punching on sound-proof wall 151, blocked space 150 can further improve the isolates sound effect thus as echo chamber like this.
In this embodiment, sound-proof wall 151 is arranged in absorbing silencer 140 and is used to limit blocked space 150; Yet isolated structure is positioned at the outside of silencing apparatus from silencing apparatus, can form blocked space like this, obtains the similar advantage for present embodiment thus.
Second communication passage 146 can integrally be cast with muffler body 141; Yet, also can transform and cover 142 cast inblocks into, the influence of the heat that receives from the motor unit 105 that is arranged in muffler body 141 back can be lowered like this.
Exemplary embodiments 2
Fig. 4 is the sectional view of the absorbing silencer of second exemplary embodiments according to the present invention.Fig. 5 is the flow-rate vectors that shows according to the running of the refrigerant gas in second embodiment's the absorbing silencer.According to the structure of second kind of embodiment's hermetic compressor (being designated hereinafter simply as compressor) except adsorber with shown in Figure 1 the same, the explanation to this embodiment will concentrate on the absorbing silencer like this.
In Fig. 4, absorbing silencer 140 comprises suction muffler body 141, suction muffler lid (not shown), first communication passage 145 and second communication passage 146, and in the absorbing silencer 140 inner sound insulation spaces 143 that form.In this embodiment, guiding wall 152 is used as sound-proof wall.The gas that shape is sucked by second communication passage 146 as guiding wall 152 guiding of letter U, i.e. refrigerant gas, from opening 146a to opening 145a.
In Fig. 5, flow-rate vectors 160 shows the running of refrigerant gas in the absorbing silencer 140 that obtains by computer simulation, and each vectorial length is represented the flow direction of the direction pilot block system cold air of the flow velocity amplitude of refrigerant gas and vector.Arrow mark is represented the overdraught 161 that formed by the refrigerant gas of discharging from the opening 146a of second communication passage 146.
The below work of the above-mentioned hermetic compressor of explanation.In this embodiment, place guiding wall 152 (sound-proof wall), be used to guide the refrigerant gas of discharging opening 145a to first communication passage 145 at opening 146a.This structure allows nearly all refrigerant gas of discharging at opening 146a to form eddy current 161, and eddy current 161 is inhaled into first communication passage 145 then on this.At this moment, the wall of absorbing silencer 140 is closed the refrigerant gas heating that keeps high temperature in the container 101, and the wall that is heated heating remains in the refrigerant gas in the sound insulation space 143.The temperature of this heated gas is higher than the temperature that just flows to the refrigerant gas the sound insulation space 143 from second communication passage 146.
Therefore, as quickly as possible nearly all refrigerant gas of discharging at opening 146a is sucked in first communication passage 145, this will make gas and be heated to high temperature and refrigerant gas that remain in the sound insulation space 143 is isolated.This structure allows to keep refrigerant gas low temperature and that represented by last eddy current 161 to receive less heat, and refrigerant gas can be maintained at low density like this, and the mass flow rate ratio of the refrigeration agent that will be inhaled into can be increased.
Guiding wall 152 shapes are as letter U rather than pipe path, and the pressure loss advantageously diminishes like this.Guiding wall 152 is adjusted the refrigerant gas that sucks from opening 146a so that gas can smooth flow, and guiding gas directly arrives opening 145a.Therefore, can reduce the pressure loss, increase COP thus.Guiding wall 152 also guides the gas that is inhaled into pressing chamber 122, and this gas is not included in circuit refrigerant gas in the sound insulation space 143 but adopts the fluid inertia force that sucks gas, and the mass flow rate ratio of the gas of Xi Ruing has been enhanced like this.
The heat that the mechanism of above-mentioned discussion has reduced refrigerant gas receives loss and has improved the flow that is inhaled into gas, and absorption efficiency can improve like this, and refrigerating capacity has improved 2.5% with traditional comparing, and COP has improved and is no less than 2.0%.
Also has a problem that propagates into the reflected wave of nearest and wall that face absorbing silencer 140 from opening 145a; Yet guiding wall 152 covers opening 145a, and the inhibitory reflex ripple is by the propagation of the wall of absorbing silencer 140 thus.Guiding wall 152 prevents that also reflected wave from activating the wall of absorbing silencer 140.This prevention is effective especially for the sound transmission that reduces the high fdrequency component in the audio-frequency band.
In this embodiment, the space of preparing about 5mm between opening 145a and guiding wall 152 is used to keep the attenuating to the reflected wave that produces from opening 145a.Yet opening 145a can further reduce the flow resistance of refrigerant gas to the connection of the outer surface of guiding wall 152, and has improved absorption efficiency.
In this embodiment, omitted the explanation of this specification of the part identical with first embodiment; Yet second embodiment can obtain with respect to the advantage on the placement direction of the guiding wall of separation surfaces (opening surface of suction muffler body) in the casting synthetic resin.
Commercial Application
The compression unit of hermetic compressor of the present invention comprises an opening part that is positioned at discharge chambe Absorption valve and absorbing silencer. Described silencer comprises the absorbing silencer that forms the sound insulation space Body, be used for to be communicated with absorb first communication passage in valve and sound insulation space and be used for being communicated with sealing and hold Second communication passage in device and sound insulation space. Be arranged in the sound insulation space first communication passage one An opening of individual opening and second communication passage that is arranged in the sound insulation space is in identical side Upward opening. In addition, sound-proof wall be positioned on the wall of muffler body at least in the face of two openings On the position. The application of this compressor in refrigerator, air-conditioning and refrigeration plant will reduce makes an uproar Sound and improve the efficient of these equipment.

Claims (6)

1, a kind of hermetic compressor comprises:
A motor unit;
A compression unit that drives by described motor unit;
A closed container that holds described motor unit and described compression unit; With
Described compression unit comprises:
Be positioned at the absorption valve of an opening of pressing chamber; With
An absorbing silencer, it has:
Form the suction muffler body in sound insulation space;
Be used to be communicated with first communication passage in described absorption valve and described sound insulation space; With
Be used to be communicated with second communication passage in described closed container and described sound insulation space;
Wherein, be arranged in opening of described first communication passage in described sound insulation space and the opening of described second communication passage that is arranged in described sound insulation space in substantially the same direction upper shed, and
Wherein, described muffler body wall on the position in the face of two openings being arranged in described sound insulation space at least, have a sound insulation from.
2, hermetic compressor according to claim 1, wherein said sound-proof wall is made of the part of described suction muffler body.
3, hermetic compressor according to claim 2, the described wall of wherein said sound-proof wall and described suction muffler body forms a blocked space.
4, hermetic compressor according to claim 2,
Wherein said absorbing silencer is made by synthetic resin and is made of at least two compositions, and
Wherein said sound-proof wall is placed vertically with respect to the open surfaces of described suction muffler body.
5, hermetic compressor according to claim 1, wherein said sound-proof wall is used as guiding wall, is used to guide the gas that sucks from described second communication passage to arrive described first communication passage smoothly.
6, hermetic compressor according to claim 5, the cross section of wherein said guiding wall shows as letter U.
CNA2004800007240A 2003-08-26 2004-07-27 Hermetic compressor Pending CN1701179A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003300869A JP4581354B2 (en) 2003-08-26 2003-08-26 Hermetic compressor
JP300869/2003 2003-08-26

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CN1701179A true CN1701179A (en) 2005-11-23

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US (1) US20060039803A1 (en)
EP (1) EP1697637A1 (en)
JP (1) JP4581354B2 (en)
KR (1) KR100653669B1 (en)
CN (1) CN1701179A (en)
WO (1) WO2005019645A1 (en)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4735084B2 (en) * 2005-07-06 2011-07-27 パナソニック株式会社 Hermetic compressor
KR100778485B1 (en) 2006-04-26 2007-11-21 엘지전자 주식회사 Muffler and compressor having the same
TWI475627B (en) 2007-05-17 2015-03-01 Brooks Automation Inc Substrate carrier, substrate processing apparatus and system, for reducing particle contamination of substrate during processing and method of interfacing a carrier with a processing tool
US8235683B2 (en) * 2007-12-06 2012-08-07 Panasonic Corporation Hermetic compressor
JP5386906B2 (en) * 2008-09-25 2014-01-15 パナソニック株式会社 Refrigerant compressor
JP5560580B2 (en) * 2009-04-10 2014-07-30 パナソニック株式会社 Hermetic compressor
BRPI1105162B1 (en) 2011-12-15 2021-08-24 Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda. ACOUSTIC FILTER FOR ALTERNATIVE COMPRESSOR
WO2014122931A1 (en) * 2013-02-07 2014-08-14 パナソニック株式会社 Sealed compressor and refrigerating apparatus
CN203867817U (en) * 2013-07-30 2014-10-08 惠而浦股份有限公司 Acoustic attenuator device used for compressor
CN106014920A (en) * 2016-06-29 2016-10-12 安徽美芝制冷设备有限公司 Compressor, assembly method for compressor and refrigerator
KR102301459B1 (en) 2017-05-30 2021-09-13 가부시키가이샤 아루박 vacuum pump

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4109751A (en) * 1976-08-26 1978-08-29 Deere & Company Noise silencer
BR8602173A (en) * 1986-05-02 1987-12-22 Brasil Compressores Sa IMPROVEMENT IN A HERMETIC COOLING COMPRESSOR SUCTION SYSTEM
JP3115710B2 (en) * 1992-10-02 2000-12-11 松下冷機株式会社 Hermetic electric compressor
KR200141490Y1 (en) * 1993-04-24 1999-05-15 김광호 Noise-reducing apparatus of a compressor
JP3207032B2 (en) * 1993-11-09 2001-09-10 株式会社豊田自動織機製作所 Scroll compressor
BR9604126A (en) * 1996-08-21 1998-05-26 Brasil Compressores Sa Suction damper for hermetic compressor
JP3725294B2 (en) * 1997-05-21 2005-12-07 松下冷機株式会社 Hermetic compressor
JPH11311179A (en) * 1998-04-28 1999-11-09 Matsushita Refrig Co Ltd Enclosed type electric compressor
JP2001304118A (en) * 2000-04-24 2001-10-31 Matsushita Refrig Co Ltd Hermetic compressor
KR100378803B1 (en) * 2000-06-12 2003-04-07 엘지전자 주식회사 Muffler for compressor
KR100390492B1 (en) * 2000-07-13 2003-07-04 엘지전자 주식회사 Apparatus for reducing noise of suction muffler in compressor
KR100364741B1 (en) * 2000-09-28 2002-12-16 엘지전자 주식회사 Suction muffler of compressor
US6390132B1 (en) * 2000-12-07 2002-05-21 Caterpillar Inc. Fluid stream pulse damper
KR100373455B1 (en) * 2000-12-21 2003-02-25 삼성광주전자 주식회사 Suc-muffler of compressor
KR100386269B1 (en) * 2001-01-11 2003-06-02 엘지전자 주식회사 Muffler of compressor
JP4792675B2 (en) * 2001-07-31 2011-10-12 パナソニック株式会社 Hermetic compressor
KR100504983B1 (en) * 2003-03-12 2005-08-01 삼성광주전자 주식회사 A suction muffler for compressor, A compressor and A apparatus having refrigerant cycle circuit

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JP2005069121A (en) 2005-03-17
US20060039803A1 (en) 2006-02-23
WO2005019645A1 (en) 2005-03-03
EP1697637A1 (en) 2006-09-06
JP4581354B2 (en) 2010-11-17
KR20050084808A (en) 2005-08-29
KR100653669B1 (en) 2006-12-05

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