CN1093605C - Noise reducing structure for hermetically sealed compressor - Google Patents
Noise reducing structure for hermetically sealed compressor Download PDFInfo
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- CN1093605C CN1093605C CN97122196A CN97122196A CN1093605C CN 1093605 C CN1093605 C CN 1093605C CN 97122196 A CN97122196 A CN 97122196A CN 97122196 A CN97122196 A CN 97122196A CN 1093605 C CN1093605 C CN 1093605C
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- reduction noise
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Abstract
The present invention provides a noise reducing structure for hermetically sealed compressor, which can effectively reduce noise in this frequency band caused by the vibrancy of the compressing chamber because of pressure impact effective in the compressing stroke in the cylinder, and can prevent reduction of volumetric efficiency of chamber for reducing noise. The structure has a chamber for reducing noise having predetermined capacity and formed in said cylinder; and a connection passage for connecting said structure for reducing noise and said cylinder.
Description
Technical field
The present invention relates to a kind of structure of reduction noise of closed compressor, in particular, relate to a kind of can reduce effectively since in the press cycles of cylinder because of the pressure collision effect in the cylinder, the noise of the frequency band that makes compression chamber vibration and cause, and can prevent to reduce the structure of the reduction noise that noise chamber internal volume efficient reduces.
Background technique
As illustrated in fig. 1 and 2, existing closed compressor has a motor with stator 2 and rotor 3 etc. in the seal container 1 of a predetermined volume.
One has the bent axle 4 of eccentric part 4a to be installed in the rotor 3 in its lower end, upper and lower bearing 5 and 6 is connected round the cylinder block 8 of bent axle 4 bottoms with eccentric part 4a with bolt 7 respectively.
A rolling piston 9 links to each other with the eccentric part 4a of bent axle 4, and by internal surface 15 rollings of its driving along cylinder, one compressing mechanism has a hyperbaric chamber 15a and a low-pressure cavity 15b, in rolling piston 9 rotating process, above-mentioned two by one radially the volume that surrounded of valve block 10 change, reciprocating in the radial groove that this valve block 10 forms in the wall of cylinder 15, and pressed to rolling piston 9 by the pressure of spring 13.
A relief opening 8a is arranged on the part of cylinder block 8, be used for compressed refrigerant gas eliminating between hyperbaric chamber 15a and valve block 10 is gone.An exhaust passage 5a is arranged on the suitable part of upper bearing (metal) 5, and 8a is communicated with relief opening.
Also have one to be used to the suction port 8b that allows refrigerant gas flow on cylinder block 8, this suction port is communicated with refrigerant gas suction tude 12 on being connected gas holder 11, and gas holder then is installed on the seal container 1.
In the accompanying drawings, label 14 expressions are contained in the outlet pipe on seal container 1 top, and the refrigerant gas that is used for being compressed in seal container 1 is discharged to the external world and goes.
Below, the working procedure of existing closed compressor is described.
When the motor of common closed compressor was switched on, rotor 3 just rotated.So the bent axle 4 that is driven by rotor 3 also rotates, make rolling piston 9 along the central axis rotation of the internal surface of cylinder 15 with respect to bent axle 4.
At this moment, in the groove that in cylinder block 8, forms,, thereby the hyperbaric chamber 15a and the low-pressure cavity 15b of volume-variation have been formed in of the external peripheral surface sliding contact of the reciprocating valve block 10 of Vertical direction with rolling piston 9.
Because the rotation of bent axle 4 is rotated rolling piston 9, is collected in the low-temp low-pressure refrigerant gas in the gas holder 11 that is installed on the seal container 1, just by being connected refrigerant gas suction tude 12 and the intakeport 8b on the gas holder 11, is inhaled in the cylinder 15.One end of above-mentioned intakeport is communicated with refrigerant gas suction tude 12, and its other end then communicates with the compression chamber of cylinder 15.
Low-temp low-pressure refrigerant gas in the suction cylinder 15 are compressed into the refrigerant gas of High Temperature High Pressure, and this refrigerant gas sequential flow through overcompression is crossed relief opening 8a and exhaust passage 5a, and then is discharged to the outside of cylinder 15.Be discharged to the High Temperature High Pressure refrigerant gas of cylinder 15 outsides, be discharged to the outside of compressor again by the outlet pipe 14 that forms on seal container 1 top.
In existing closed compressor, refrigerant gas flows under the low-temp low-pressure state, is compressed into high-temperature high-pressure state then.In the air-breathing and compression process of above refrigerant gas, can produce very big noise.Below, the structure commonly used that reduces the noise that is produced is described.
Shown in Fig. 2 and 3, in the structure of existing reduction noise, a relief opening 8a is arranged, and the refrigerant gas through overcompression will flow through this relief opening owing to the collaborative work of valve plate 10 in hyperbaric chamber 15a, and also has a chamber 8c who reduces noise to communicate with this relief opening 8a.
The chamber 8c of above-mentioned reduction noise has predetermined volume, and it is shaped as cylindrical shape.
In the structure of existing reduction noise, because the chamber of the reduction noise of the structure of this reduction noise is to be used for being communicated with the lateral parts of relief opening 8a, and the refrigerant gas of compression discharges by above-mentioned relief opening in cylinder 15, so can only be reduced in the interior noise of frequency range of 100Hz-2KHz, and can not reduce noise in the frequency range of 3KHz-5KHz, the noise of a kind of frequency range in back is in the compressor compresses stroke because the vibration in the compression chamber that the compression shock effect in the cylinder is caused is caused.
The frequency range of above-mentioned high frequency band is 300Hz-5KHz, just in time in the frequency range of the 20Hz-20KHz that the people can hear.
Owing to reduce the chamber 8c of noise is to form in 340 ° to 350 ° angular range of valve plate 10 beginnings, and the inside of cylinder 15 is divided into hyperbaric chamber 15a and low-pressure cavity 15b by valve plate 10, so in compression stroke, the high pressure refrigerant gas that remains among the chamber 8c that reduces noise will be re-inflated, flow back to again in the low-pressure cavity 15b then, thereby reduced air-breathing volumetric efficiency.
Summary of the invention
Therefore, an object of the present invention is to provide a kind of structure of reduction noise of closed compressor, it has solved problem above-mentioned in the prior art.
Another object of the present invention provides a kind of structure of reduction noise of improved closed compressor, it can reduce the noise of this section frequency band that the vibration of the compression chamber that is caused owing to the compression shock effect in the cylinder in the compression stroke of cylinder causes effectively, and can prevent to reduce the reduction of the cavity volume efficient of noise.
In order to achieve the above object, a kind of structure of reduction noise of closed compressor is provided, it comprises: the chamber of the reduction noise with predetermined volume that forms in a cylinder block, and the contact channel that the compression chamber of a cylinder in the chamber of above-mentioned reduction noise and the cylinder block is communicated with.Its improvements are, the chamber of above-mentioned reduction noise and the position of contact channel are in from valve plate radially cylinder interior is separated in 210 °-270 ° the angular range that the position of hyperbaric chamber and low-pressure cavity begins.The structure of this improved reduction noise compared with prior art, can reduce the noise in the wider frequency range, has also improved gettering efficiency simultaneously.
The following description will make other advantages of the present invention, purpose and characteristics become more clear.
Description of drawings
Below, describe embodiments of the invention in detail with reference to accompanying drawing, but these embodiments are just in order to illustrate the present invention rather than in order to limit the present invention.In the accompanying drawing:
Fig. 1 is the vertical section figure of closed compressor that has equipped the structure of existing reduction noise;
Fig. 2 is the horizontal sectional view along the I-I ' line of Fig. 1;
Fig. 3 is the part sectional view of compressing mechanism of the closed compressor of the explanation structure of having equipped existing reduction noise;
Fig. 4 is the vertical section figure of closed compressor of structure that has equipped the reduction noise of the first embodiment of the present invention;
Fig. 5 is the horizontal sectional view along the V-V ' line of Fig. 4;
Fig. 6 is the schematic partial sectional view of compressing mechanism of closed compressor of structure of having equipped the reduction noise of the first embodiment of the present invention;
Fig. 7 is the vertical section figure of closed compressor of structure that has equipped the reduction noise of the second embodiment of the present invention;
Fig. 8 is the schematic partial sectional view of compressing mechanism of closed compressor of structure of having equipped the reduction noise of the second embodiment of the present invention; And
Fig. 9 is the planimetric map of compressing mechanism of closed compressor of structure of having equipped the reduction noise of the first embodiment of the present invention.
Embodiment
The structure of reduction noise of the closed compressor of the first embodiment of the present invention is described with reference to the accompanying drawings.
Shown in Fig. 4,5 and 6, formed the contact channel 108d of the compression chamber of the chamber 108c of a reduction noise that makes progress with predetermined volume and chamber 108c who is communicated with above-mentioned reduction noise and cylinder 115 in the casing wall inside in lower bearing 106 of the cylinder 115 of cylinder block 108 central authorities.
The chamber 108c and the contact channel 108d of the above-mentioned reduction noise that upwards forms are in when mounted from valve plate 110 radially the inside of cylinder 115 are separated in 210 °-270 ° the angular range that the position of hyperbaric chamber 115a and low-pressure cavity 115b begins.
The chamber 108c of the above-mentioned reduction noise that upwards forms is cylindrical, and its diameter D is 1 with the ratio (D/L) of length L: 5-1: 6.The transverse shape of above-mentioned contact channel 108d is square.
The chamber 108c of above-mentioned reduction noise and contact channel 108d make respectively cylindrical shape and square be for the ease of making.And the ratio of above-mentioned D/L is determined according to practical experience.
Below, with reference to the working procedure of accompanying drawing detailed description according to the structure of the reduction noise of the closed compressor of the first embodiment of the present invention.
At first, when closed compressor was connected power supply, rotor 103 just rotated.When the bent axle 104 in being installed in rotor 103 rotated, rolling piston 109 just rolled along the inner circumferential surface of cylinder 115.Be collected in the low-temp low-pressure refrigerant gas in the gas holder that is installed in seal container 101 outsides, flow through the refrigerant suction tude 112 and the suction port 108 that are communicated with gas holder 111, be inhaled in the cylinder 115 inner low-pressure cavity 115b that form.One end of above-mentioned suction port 108 is communicated with the suction tude 112 of refrigerant gas, and its other end is communicated with the compression chamber of cylinder 115.The refrigerant gas that flows into compresses in the cylinder 115 inner hyperbaric chamber 115a that form.
Flow through the relief opening 108a that in cylinder block 108, forms through the refrigerant gas of overcompression, by with upper bearing (metal) 105 that relief opening 108a is communicated with in the exhaust passage 105a that forms, outside the discharge cylinder block 108.
Vibration in the compression chamber that compression shock effect when being compressed in cylinder 115 by refrigerant gas is caused is caused, high frequency band is the noise of 300Hz-5KHz, has been reduced widely by the chamber 108c of the reduction noise of the contact channel 108d and the formation that makes progress.
In addition, because the position of the chamber 108c of the above-mentioned reduction noise that upwards forms, be in 210 °-270 ° the angular range that begins from the mounting point that the inside of cylinder 115 is separated into the valve plate 110 of hyperbaric chamber 115a and low-pressure cavity 115b, so just can prevent the reduction of aspirated volume efficient.In the existing structure of Fig. 1-3, in the compression stroke of compressor, the interior high pressure refrigerant gas of chamber that remains in the reduction noise that upwards forms can be re-inflated, and is back in the low-pressure cavity, thereby has reduced air-breathing volumetric efficiency.
Below, with reference to the structure of description of drawings according to the reduction noise of the closed compressor of the second embodiment of the present invention.
Shown in Fig. 7,8 and 9, on the part of the cylinder block 108 that contacts with upper bearing (metal) 205, the chamber 208c of the reduction noise of the downward formation with predetermined volume is arranged, and a contact channel 208d then makes the chamber 208c of the reduction noise of above-mentioned downward formation be communicated with the compression chamber of cylinder 215.
The chamber 208c of the reduction noise of above-mentioned downward formation and the position of contact channel 208d are in 210 °-270 ° the angular range that begins from the mounting point that the inside of cylinder 215 is separated into the valve plate 210 of hyperbaric chamber 215a and low-pressure cavity 215b.
The chamber 208c of the reduction noise of above-mentioned downward formation is cylindrical, and its diameter D is 1 with the ratio (D/L) of length L: 5-1: 6.The transverse shape of above-mentioned contact channel 208d is square usually.
Cylindrical with the square respectively reason of the chamber 208c of the reduction noise of above-mentioned downward formation and the transverse shape of above-mentioned contact channel 208d is identical with the first embodiment of the present invention.In addition, the diameter D of the chamber 208c of the reduction noise of above-mentioned downward formation is 1 with the ratio of length L: 5-1: 6 also is rule of thumb to determine.
Because identical according to the working procedure of the structure of the reduction noise of the closed compressor of the second embodiment of the present invention and the first embodiment of the present invention is so omitted the description of repetition.
As mentioned above, structure according to the reduction noise of closed compressor of the present invention, can reduce the noise of this section high frequency band that the vibration of the compression chamber that is caused owing to the compression shock effect in the cylinder in the compression stroke of cylinder causes effectively, and can prevent to reduce the reduction of the cavity volume efficient of noise, thereby improve the reliability and the performance of compressor.
Though above the preferred embodiments of the present invention have been described,, those skilled in the art are appreciated that under the prerequisite of scope of the claims that do not break away from the application and aim, can be used for various modifications, increase and replace the present invention.
Claims (4)
1. the structure of the reduction noise of a closed compressor, sealing formula compressor has a cylinder block that forms air cylinder in therein, one rolling piston that can rotate along the wall of above-mentioned cylinder, and one radially be installed in the cylinder, contact with above-mentioned rolling piston, cylinder interior is separated into the valve plate of low-pressure cavity and hyperbaric chamber, it is characterized in that the structure of above-mentioned reduction noise comprises:
The chamber of a reduction noise that in above-mentioned cylinder block, forms; And
Article one, in above-mentioned cylinder wall, form, be used to be communicated with the structure of above-mentioned reduction noise and the contact channel of above-mentioned cylinder;
Wherein, it is benchmark that the structure of above-mentioned reduction noise and contact channel are formed on the mounting point of above-mentioned radially valve plate on cylinder, is 210 °-270 ° angle of circumference place along the sense of rotation of rotor.
2. the structure of reduction noise as claimed in claim 1 is characterized in that, the structure of above-mentioned reduction noise is cylindrical, and the ratio of its diameter and length is 1: 5-1: in 6 the scope.
3. the structure of reduction noise as claimed in claim 1 is characterized in that, the structure of above-mentioned reduction noise is upwards to form from the lower surface that contacts with upper surface lower bearing above-mentioned cylinder block.
4. the structure of reduction noise as claimed in claim 1 is characterized in that, the structure of above-mentioned reduction noise is to form downwards from the upper surface that contacts with lower surface upper bearing (metal) above-mentioned cylinder block.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR32199/97 | 1996-07-11 | ||
| KR61241/96 | 1996-12-03 | ||
| KR19960061241 | 1996-12-03 | ||
| KR1019970032199A KR100214662B1 (en) | 1996-12-03 | 1997-07-11 | A noise lessening structure of a hermetic compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1186177A CN1186177A (en) | 1998-07-01 |
| CN1093605C true CN1093605C (en) | 2002-10-30 |
Family
ID=26632327
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN97122196A Expired - Lifetime CN1093605C (en) | 1996-07-11 | 1997-12-01 | Noise reducing structure for hermetically sealed compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1093605C (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1314898C (en) * | 2002-07-19 | 2007-05-09 | 三星光州电子株式会社 | Reciprocating compressor |
| CN100398835C (en) * | 2003-05-22 | 2008-07-02 | 乐金电子(天津)电器有限公司 | Noise reducing device for rotary compressor |
| CN100458165C (en) * | 2005-10-26 | 2009-02-04 | 日立空调·家用电器株式会社 | Rotary compressor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110318984B (en) * | 2019-07-11 | 2020-11-20 | 珠海格力电器股份有限公司 | Cylinder silencing device, pump body assembly and compressor |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1171496A (en) * | 1996-07-18 | 1998-01-28 | 三洋电机株式会社 | Rotary compressor |
-
1997
- 1997-12-01 CN CN97122196A patent/CN1093605C/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1171496A (en) * | 1996-07-18 | 1998-01-28 | 三洋电机株式会社 | Rotary compressor |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1314898C (en) * | 2002-07-19 | 2007-05-09 | 三星光州电子株式会社 | Reciprocating compressor |
| CN100398835C (en) * | 2003-05-22 | 2008-07-02 | 乐金电子(天津)电器有限公司 | Noise reducing device for rotary compressor |
| CN100458165C (en) * | 2005-10-26 | 2009-02-04 | 日立空调·家用电器株式会社 | Rotary compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1186177A (en) | 1998-07-01 |
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|---|---|---|---|
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
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| C14 | Grant of patent or utility model | ||
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| CX01 | Expiry of patent term |
Granted publication date: 20021030 |
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| CX01 | Expiry of patent term |