CN100470056C - Secondary screw type compressor - Google Patents
Secondary screw type compressor Download PDFInfo
- Publication number
- CN100470056C CN100470056C CNB2006101281012A CN200610128101A CN100470056C CN 100470056 C CN100470056 C CN 100470056C CN B2006101281012 A CNB2006101281012 A CN B2006101281012A CN 200610128101 A CN200610128101 A CN 200610128101A CN 100470056 C CN100470056 C CN 100470056C
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- pressure stage
- space portion
- stage side
- compression mechanical
- side compression
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Abstract
The invention provides a twice-grade screw compressor capable of reducing the peak value of the frequency number of the noise caused by rotor engagement from the twice-grade screw compressor, so that noise reduction can be effectively achieved. The twice-grade screw compressor is equipped with a low pressure stage compression mechanism, a high pressure stage compression mechanism, a motor 7, and a housing 1-4 for integrally accommodating the mentioned mechanisms. The housing is arranged between the low pressure stage compression mechanism and the high pressure stage compression mechanism, and has a central housing 2-4 for forming a space section as passages 38, 39 for the compressed gas from the low pressure stage compression mechanism. And a close space section 49 is connected to space section 38, 39 through an opening 49a being arranged at the peripheral of the central housing.
Description
Technical field
The present invention relates to be used for the secondary screw type compressor of refrigerator.
Background technique
The noise spectrum that screw compressor produces, (male ロ-number of teeth ) and the product of gyro frequency number be as the fundamental frequency number, and the peak value of fundamental frequency number and higher harmonics composition thereof (below, be referred to as the meshing frequency number) becomes greatly with male rotor.As the means that reduce this noise, taked: pasting sound absorbing material on the housing, housing is made the countermeasure that double-layer structural improves sound insulation value, additional rib improves the rigidity etc. of housing on housing.And then, as other countermeasure, as TOHKEMY 2002-235525 communique record, also considered with pipe arrangement that screw compressor is connected on the countermeasure of resonance type baffler etc. is set.
Patent documentation 1: TOHKEMY 2002-235525 communique (Fig. 6)
Patent documentation 2: Japanese kokai publication hei 11-117879 communique (Fig. 3)
Pasting sound absorbing material on the housing, add rib with the housing bilayerization, on housing, the resonance type baffler being set to the first-class means of pipe arrangement, can obtain certain noise reduction by above-mentioned.But in these prior aries, the words of pasting sound absorbing material must cover the integral body of mo(u)lding housing with sound absorbing material, are difficult to carry out under a lot of situations for the screw compressor with complicated mo(u)lding shape.And with the housing bilayerization, there is the problem that makes that complex-shapedization of mo(u)lding and mo(u)lding weight increase in perhaps additional rib.And then, for the countermeasure that the resonance type baffler is set on pipe arrangement, even for example use and open the secondary screw type compressor of putting down in writing among Fig. 3 of flat 11-117879 communique the spy, also can't reduce from compressor housing propagating into outside noise, can not effectively reduce the noise of secondary screw type compressor.
Summary of the invention
The objective of the invention is to, a kind of secondary screw type compressor is provided, it can reduce the peak value of the frequency noise number that the engagement by rotor that secondary screw type compressor sends produces, and effectively seeks low noiseization.
In order to reach above-mentioned purpose, secondary screw type compressor of the present invention is provided with low pressure stage side compression mechanical part, high pressure stage side compression mechanical part, motor, and housing; Described low pressure stage side compression mechanical part has a pair of male rotor and female rotor (female ロ-), reach the bearing part of these rotors of supporting; Described high pressure stage side compression mechanical part is made of a pair of male rotor and female rotor and the bearing part that supports these rotors; Described motoring described low pressure stage side compression mechanical part and high pressure stage side compression mechanical part; Described housing holds these low pressure stage side compression mechanical parts, high pressure stage side compression mechanical part and motor integratedly; It is characterized in that, described housing is between described low pressure stage side compression mechanical part and high pressure stage side compression mechanical part, have the middle casing part that is used to form as from the space portion of the path of the compressed fluid of low pressure stage side compression mechanical part, be provided with the peripheral part side of the inner face that is formed on described middle casing part and close space portion by what opening portion was communicated with described space portion.
At this, the described space portion that closes can constitute compactly with the words that the mode in the heavy section that is built in described middle casing part forms.And, describedly close the outside that space portion also can be arranged on the peripheral part of described middle casing part, like this also go for existing compressor.
The described space portion that closes is provided with a plurality ofly, can reduce the noise peak in a plurality of meshing frequency numbers.The described space portion that closes constitutes in the mode that can change its volume, can suitably reduce the noise peak of certain meshing frequency number targetedly.At this moment, for example with described close space portion with cylinder portion and in this cylinder portion pistons reciprocating constitute, can change the volume of cylinder portion by making this reciprocating motion of the pistons.
And then, the described space portion that closes is configured in described middle casing upper side partly, this foot that closes space portion is opened in described middle casing part inner face via opening portion, can prevent from that oil, liquid coolant are trapped in to close space portion, can obtain the effect of stable reduction noise.
According to the present invention, between low pressure stage side compression mechanical part and high pressure stage side compression mechanical part, have the middle casing part of the conduct of being used to form from the space portion of the path of the compressed fluid of low pressure stage side compression mechanical part, be provided with by what opening portion was communicated with the described space portion of the peripheral part side of the inner face that is formed on described middle casing part and close space portion, therefore, can reduce the peak value of the frequency number of the noise that the engagement because of rotor of sending from secondary screw type compressor produces, have the effect that effectively to seek low noiseization.
Description of drawings
Fig. 1 is an embodiment's of an expression secondary screw type compressor of the present invention longitudinal section.
Fig. 2 is the longitudinal section of another embodiment's of expression major component.
Fig. 3 is the longitudinal section of the major component of expression another embodiment of the present invention.
Fig. 4 is the noise spectrum line chart that is used to illustrate effect of the present invention.
Embodiment
Have the space that forms as the gas passageway in screw compressor inside, under the situation of the consistent wavelength of the distance in this space and meshing frequency number, the peak value of meshing frequency number is excited because of internal resonance, further increases the level of noise.As the means that reduce this noise, such mode is discussed, that is, blank part is set on guiding valve, internal resonance is avoided in the space that forms the gas passageway by expansion.Can expect like this to obtain certain reduction noise result with easy structure.
But, under the situation that blank part is set on the guiding valve,, still can not reduce the peak value of other meshing frequency number even can reduce the peak value of the specific meshing frequency number that is excited by internal resonance.And, output frequency number at the motor that carries on the compressor is under the shared situation of 50Hz/60Hz, even if be designed to when 50Hz turns round, to avoid exciting the peak value of meshing frequency number because of internal resonance, but when 60Hz turns round, the meshing frequency number is changed to high frequency side, and possibility will be consistent with the internal resonance frequency number.
Below, with reference to the accompanying drawings specific embodiments of the invention are described.Fig. 1 is an embodiment's of an expression secondary screw type compressor of the present invention longitudinal section.
Secondary screw type compressor has: have suction port 26 rudimentary side main casing 1, be located at the discharge side of this rudimentary side main casing discharge housing 2, hold the winding terminal 8 of motor 7 electrical machinery cover 3, hold the electric machine casing 4 of motor 7, and have and allot mouthfuls 40 senior side main casing 5, these housings are connecting by the relation with mutual sealing such as the means of bolt etc.
On rudimentary side main casing 1, be formed with cylindric thorax (ボ ア) 31, cold media air is imported the suction port 29 of cylindric thorax 31 and piston chamber 33.In cylindric thorax 31, holding intermeshing low pressure stage side male rotor 6 and the female rotor (not shown) by roller bearing 11,12 and ball bearing 17 rotatably supports.The axle of low pressure stage side male rotor 6 is connected on the axle of high pressure stage side male rotor 9 by gear coupling 45.Holding the piston 21 that drives guiding valve 23 in piston chamber 33, piston 21 is connected on the guiding valve 23 by connecting rod 22.
On the discharge housing 2 that holds roller bearing 12 and ball bearing 17, be formed with the gas passageway 38 that is communicated with cylindric thorax 31 and electrical machinery cover 3.On the electrical machinery cover 3 of the ball bearing 18 that holds rotatably support high pressure stage side male rotor 9, be formed with and discharge the gas passageway 39 that housing 2 and electric machine casing 4 are communicated with.On the electric machine casing 4 of the axial region that holds motor 7 and high pressure stage side male rotor 9, be formed with the suction chamber 28 that cold media air is imported senior side main casing 5.On senior side main casing 5, form cylindric thorax 32, in cylindric thorax 32, holding by roller bearing 13,14 and ball bearing 19 rotatably supports and also intermeshing high pressure stage side male rotor 9 and female rotor (not shown).The axle of high pressure stage side male rotor 9 constitutes with the axle one of motor 7 (directly).
The following describes flowing of cold media air and oil.
Low temperature, low pressure refrigerant gas that suction port 26 from the main casing 1 of being located at rudimentary side sucks, the suction port 29 that forms from main casing 1 are drawn into the mesh tooth face and main casing 1 formed pressing chamber by the positive and negative turbine rotor of low pressure stage side.Then, cold media air is along with the rotation of the low pressure stage side male rotor 6 that is connected to motor 7, be sealed in the mesh tooth face and main casing 1 formed pressing chamber of positive and negative turbine rotor of low pressure stage side, because of the gas that is compressed into high temperature, high pressure gradually that dwindles of pressing chamber, be imported into electric machine casing 4 by discharging the gas passageway 38,39 that forms respectively on housing 2, the electrical machinery cover 3.Affact radial load in the compression counter-force of positive and negative turbine rotor of low pressure stage side during compression by roller bearing 11,12 supportings, slip load is supported by roller bearing 17.
Be imported into the cold media air of electric machine casing 4, by the air openings between the rotor, from the suction chamber 28 that is formed at electric machine casing 4 is inhaled into main casing 5 formed pressing chambers by the mesh tooth face of the positive and negative turbine rotor of high pressure stage side and electric machine casing 4 and senior side.Then, cold media air is along with the rotation of the high pressure stage side male rotor 9 that is directly connected to motor 7, be sealed in the mesh tooth face and electric machine casing 4 and senior side main casing 5 formed pressing chambers by the positive and negative turbine rotor of high pressure stage side, along with dwindling gradually of pressing chamber is compressed, with compare and become high temperature, pressurized gas before the compression, drain passageway 40 to senior side main casing is discharged. and affact radial load in the compression counter-force of positive and negative turbine rotor of high pressure stage side during compression by roller bearing 13,14 supportings, slip load is supported by roller bearing 19.The lubricant oil that these bearings are lubricated carries out fuel feeding by the oily path that is communicated with bearing portion that is separately positioned on rudimentary side main casing 1, discharge on housing 2, electrical machinery cover 3, electric machine casing 4 and the senior side main casing 5.
The noise spectrum that the whelk rotary compressor produces, as the fundamental frequency number, the peak value of fundamental frequency number and higher harmonics composition thereof becomes greatly with the product of the number of teeth of male rotor and gyro frequency number.In the secondary screw type compressor, need be used to connect middle casing (discharging housing 2, electrical machinery cover 3, the electric machine casing 4) part of the main casing 5 of the main casing 1 of low pressure stage side and high pressure stage side.On the middle casing part, form gas passageway 38,39 as the space.The sound wave of the noise that the positive and negative turbine rotor of low pressure stage side produces 38,39 propagates into compressor integral body from the gas passageway.At this, the space portion 49 that closes that will link to each other with gas passageway 38 is arranged to the interior form of discharging in the housing 2 of ensconcing, and this closes space portion 49 becomes the structure of variable volume by piston 48 is set.
This closes space portion 49 and is communicated to discharge housing 2 formed gas passageways 38 by opening portion 49a.Close space portion 49 and also can constitute with the gas passageway 39 of electrical machinery cover 3 inner faces and be connected, also can be arranged on any one in the parts that constitute described middle casing part.
Because it is very little to close near the acoustic impedance of the resonant frequency number of space portion 49, thereby near the sound wave the resonant frequency number is interdicted to the propagation of compressor integral body.On the other hand, then almost do not interdict effect near the sound wave the resonant frequency number not.At this, change the volume close space portion 49, make the resonant frequency number that closes space portion 49 consistent with certain specific meshing frequency number, just can with at the peak value reduction of meshing frequency number, effectively realize low noiseization.Constitute and to change volume by closing space portion 49,, also can under the situation of compressor not being disintegrated, not carry out inching the resonant frequency number that closes space portion 49 even after compressor operating.
As long as close the consistent effect that just has the reduction noise of the resonant frequency number of space portion 49 with the meshing frequency number, therefore, be not to make the structure of variable volume with closing space portion 49, it is also passable to become the fixing structure of volume.
Because the positive and negative turbine rotor becomes noise source, therefore, by with the nearest discharge housing 2 of turbine rotor on variable volume is set space 49 just can obtain the effect of extra high reduction noise.The sound wave of the noise that sends from the positive and negative turbine rotor is propagated to compressor is whole, therefore, the space portion 49 that closes of this variable volume is arranged on the middle casing that constitutes secondary screw type compressor, promptly, discharge on any one of housing 2, electrical machinery cover 3, electric machine casing 4, can effectively reduce noise.
Not only will close space portion and be arranged on the middle casing part, also be arranged on rudimentary side main casing 1, the senior side main casing 5, can seek to obtain the effect of further reduction noise closing space portion.
Fig. 2 represents other example of the present invention.
Among this embodiment, variable volume closed space portion 49 by the external communications configuration of connecting pipings 49b with the discharge housing 2 in the downstream side that is configured in rudimentary side main casing 1.The resonant frequency number words consistent with the meshing frequency number of closing space portion 49 just have the effect that reduces noise, therefore, make the resonant frequency number that closes space portion 49 consistent as long as constitute in advance with the meshing frequency number, the fixing structure of volume closes the structure that space portion 49 needn't be a variable volume, even also can.Main noise source is from the engagement of positive and negative turbine rotor, therefore, by the space 49 with variable volume be arranged on the nearest described discharge housing 2 of turbine rotor on, can obtain higher noise reduction.But, because the sound wave that engagement produced of positive and negative turbine rotor is also to the whole propagation of compressor, therefore, the described space portion that closes is arranged on any one of the rudimentary side main casing 1 that constitutes secondary screw type compressor, electrical machinery cover 3, electric machine casing 4, senior side main casing 5 and also can obtains certain reduction noise result.
As present embodiment,,, just can easily reduce the noise of existing compressor by the above-mentioned space portion that closes is arranged on the existing compressor with the outside that space portion 49 is arranged on compressor housing of closing of variable volume.
Fig. 3 represents another embodiment of the present invention.
In the present embodiment, the space portion 49 that closes of a plurality of variable volume is arranged on and discharges housing 2.The setting method of closing space portion 49 of variable volume can be the any-mode of built-in, outer installment formula as shown in Figure 2 as shown in Figure 1.As present embodiment, what a plurality of variable volume were set closes space portion 49, can reduce a plurality of peak values of meshing frequency number, can reduce noise significantly.In addition, the same with Fig. 2, closing space portion 49 also can be the fixing structure of volume.
According to noise spectrum line chart shown in Figure 4 effect of the present invention is described.
Do not possessing under the situation of closing space portion 49 that is provided with opening portion of the present invention, the noise that engagement produced by the positive and negative turbine rotor, with the product of the number of teeth of male rotor and gyro frequency number words as fundamental frequency number (f), the frequency number of fundamental frequency number (f) and higher harmonics composition thereof (2f, 3f, 4f, 5f) becomes peak value, and it is big that noise becomes.Represented such example among Fig. 4: represent 5 compositions (5f) to the meshing frequency number, be provided with two have opening portion close 49, one of space portions be at fundamental frequency number (f), another is at the frequency number of 4 compositions (4f) volume that closes space portion 49 to be set.Under such embodiment's situation, near the acoustic impedance of closing the frequency number (4f) of fundamental frequency number (f) and 4 compositions in the space portion 49 is very little, can significantly reduce the noise of fundamental frequency number (f) and 4 compositions (4f), obtain the effect that reduces noise significantly.
Noise data shown in Figure 4 is an example, can control the frequency number composition (peak value) that noise reduces by the volume and the quantity of closing space portion 49.
Claims (8)
1. a secondary screw type compressor is provided with low pressure stage side compression mechanical part, high pressure stage side compression mechanical part, motor and housing;
Described low pressure stage side compression mechanical part has a pair of male rotor and female rotor and supports the bearing part of these rotors;
Described high pressure stage side compression mechanical part is made of a pair of male rotor and female rotor and the bearing part that supports these rotors;
Described motoring described low pressure stage side compression mechanical part and high pressure stage side compression mechanical part;
Described housing holds these low pressure stage side compression mechanical parts, high pressure stage side compression mechanical part and motor integratedly;
It is characterized in that: described housing is between described low pressure stage side compression mechanical part and high pressure stage side compression mechanical part, have the middle casing part that is used to form as from the space portion of the path of the compressed fluid of low pressure stage side compression mechanical part, be provided with the peripheral part side of the inner face that is formed on described middle casing part and close space portion by what opening portion was communicated with described space portion.
2. secondary screw type compressor as claimed in claim 1 is characterized in that: the described space portion that closes is located on the discharge housing of the discharge side that is configured in low pressure stage side compression mechanical part.
3. secondary screw type compressor as claimed in claim 1 is characterized in that: the described space portion that closes forms in the mode in the heavy section that is built in described middle casing part.
4. secondary screw type compressor as claimed in claim 1 is characterized in that: describedly close the outside that space portion is arranged on the peripheral part of described middle casing part.
5. secondary screw type compressor as claimed in claim 1 is characterized in that: the described space portion that closes is provided with a plurality of.
6. as each the described secondary screw type compressor in the claim 1～5, it is characterized in that: the described space portion that closes constitutes can change described mode of closing the volume of space portion.
7. secondary screw type compressor as claimed in claim 6 is characterized in that: described close space portion by cylinder portion and in this cylinder portion pistons reciprocating constitute, constitute by making this reciprocating motion of the pistons change the volume of cylinder portion.
8. as each the described secondary screw type compressor in the claim 1～5, it is characterized in that: the described space portion that closes is configured in described middle casing upper side partly, and this foot that closes space portion is opened in described middle casing part inner face via described opening portion.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005371300 | 2005-12-26 | ||
| JP2005371300A JP4301569B2 (en) | 2005-12-26 | 2005-12-26 | Two stage screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1991177A CN1991177A (en) | 2007-07-04 |
| CN100470056C true CN100470056C (en) | 2009-03-18 |
Family
ID=38213632
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006101281012A Expired - Fee Related CN100470056C (en) | 2005-12-26 | 2006-09-04 | Secondary screw type compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4301569B2 (en) |
| CN (1) | CN100470056C (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5313860B2 (en) * | 2009-12-22 | 2013-10-09 | 株式会社神戸製鋼所 | Screw compressor |
| CN102996451A (en) * | 2011-09-08 | 2013-03-27 | 上海汉钟精机股份有限公司 | Open type double-screw compressor |
| CN102996450A (en) * | 2011-09-08 | 2013-03-27 | 上海汉钟精机股份有限公司 | Semi-enclosed double-screw compressor |
| CN106989027B (en) | 2017-06-05 | 2019-05-24 | 珠海格力电器股份有限公司 | Compound compressor |
| JP2020007982A (en) * | 2018-07-10 | 2020-01-16 | 日立ジョンソンコントロールズ空調株式会社 | Two-stage screw fluid machine |
| CN108757449B (en) * | 2018-07-24 | 2024-06-07 | 凤阳汇通压缩机制造股份有限公司 | Curve rotary piston pump |
| CN110388320A (en) * | 2019-08-26 | 2019-10-29 | 珠海格力电器股份有限公司 | Two-stage screw compressor and air-conditioner set with balancing axial thrust function |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6264443B1 (en) * | 1997-12-15 | 2001-07-24 | Scroll Technologies | Scroll compressor with integral outer housing and fixed scroll member |
| CN2561966Y (en) * | 2002-07-30 | 2003-07-23 | 梁少明 | Air-inlet filtering silencer for air compressor |
| WO2005057014A1 (en) * | 2003-12-15 | 2005-06-23 | Bitzer Kühlmaschinenbau Gmbh | Worm compressor provided with a sound absorber |
-
2005
- 2005-12-26 JP JP2005371300A patent/JP4301569B2/en not_active Expired - Fee Related
-
2006
- 2006-09-04 CN CNB2006101281012A patent/CN100470056C/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6264443B1 (en) * | 1997-12-15 | 2001-07-24 | Scroll Technologies | Scroll compressor with integral outer housing and fixed scroll member |
| CN2561966Y (en) * | 2002-07-30 | 2003-07-23 | 梁少明 | Air-inlet filtering silencer for air compressor |
| WO2005057014A1 (en) * | 2003-12-15 | 2005-06-23 | Bitzer Kühlmaschinenbau Gmbh | Worm compressor provided with a sound absorber |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4301569B2 (en) | 2009-07-22 |
| JP2007170318A (en) | 2007-07-05 |
| CN1991177A (en) | 2007-07-04 |
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| TR01 | Transfer of patent right |
Effective date of registration: 20160810 Address after: Hongkong, China Patentee after: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. Address before: Tokyo, Japan Patentee before: Hitachi Appliances, Inc. |
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| TR01 | Transfer of patent right |
Effective date of registration: 20180710 Address after: Tokyo, Japan Patentee after: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, Inc. Address before: Hongkong, China Patentee before: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. |
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| TR01 | Transfer of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090318 |
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