CN201486859U - Novel double-exhaust rotary compressor - Google Patents
Novel double-exhaust rotary compressor Download PDFInfo
- Publication number
- CN201486859U CN201486859U CN2009201700706U CN200920170070U CN201486859U CN 201486859 U CN201486859 U CN 201486859U CN 2009201700706 U CN2009201700706 U CN 2009201700706U CN 200920170070 U CN200920170070 U CN 200920170070U CN 201486859 U CN201486859 U CN 201486859U
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- valve plate
- exhaust
- exhaust valve
- compressor
- rotary compressor
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- 238000007789 sealing Methods 0.000 claims description 7
- 230000000694 effects Effects 0.000 abstract description 7
- 238000005057 refrigeration Methods 0.000 abstract description 2
- 238000007906 compression Methods 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
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Abstract
The utility model relates to the technical field of refrigeration compressors, in particular to a novel double-exhaust rotary compressor; in the novel double-exhaust rotary compressor of the utility model, one of the two exhaust ports is provided with a Helmholtz resonant cavity; the thickness dimension of the exhaust valve plate of the exhaust port of the Helmholtz resonant cavity is smaller than that of the other exhaust valve plate; in the operation of the compressor, because the exhaust valve plate that sets up the gas vent of helmholtz resonant cavity is thinner than another exhaust valve plate, thin exhaust valve plate opens the exhaust in advance under high-pressure gas's effect, and most high-pressure gas will pass through from the gas vent that sets up the helmholtz resonant cavity, can reduce exhaust airflow noise more effectively to also have certain attenuation to follow-up air current through not setting up helmholtz resonant cavity airflow noise, thereby can effectively reduce compressor airflow noise to lower.
Description
Technical field
The utility model relates to technical field of refrigeration compressors, relates in particular to a kind of novel double gas rotary compressor.
Background technique
Compressor is that compression refrigerant makes it participate in the circuit nucleus equipment in refrigerator, the air-conditioning system, and rotary compressor is a kind of compressor commonly used, and rotary compressor generally comprises rotary compressor and waves compressor; The work of revolution compression refrigerant is to finish in the sealing cylinder chamber of compressor, the housing assembly that constitutes the sealing cylinder chamber includes upper flange, lower flange and cylinder, upper flange, lower flange is arranged on the cylinder two ends and encloses the sealing cylinder chamber, be provided with eccentric rotor in the cylinder chamber, separation and eccentric rotor at slide plate are divided into air aspiration cavity and compression chamber with cylinder chamber under the tangent line effect mutually with cylinder inner wall, air aspiration cavity is the cavity that is communicated with the intakeport of suction end, the driven by motor eccentric rotor moves a week, by the intakeport of suction end air-breathing after, in the compression chamber gas by low pressure to high pressure converted, pressurized gas in cylinder chamber reach under certain high-pressure situations, discharge through the exhaust valve plate that is arranged on the exhaust passage exhaust passage of the connection relief opening of pressurized gas by being arranged on relief opening on the cylinder and upper flange or lower flange again.
In order to reduce the resistance in the compressor air-discharging process, be provided with double air compressor: because on cylinder, be provided with two relief openings and corresponding two exhaust passages, channel cross-sectional area is bigger than single air compressor, so it is little that single air compressor is compared in exhaust resistance, the compressor power consumption is just low, and COP compares single air compressor and obviously rises.In the eccentric rotor rotation compression process of compressor, in the cylinder chamber, can produce very strong noise, noise transmits out by relief opening and exhaust passage with pressurized gas, and the pneumatic noise that pressurized gas produce when discharge the exhaust passage up and down accounts for the major component of compressor total noise of centrifuge.For this part pneumatic noise of control, method commonly used is in the other helmholtz resonance chamber of opening of relief opening, the helmholtz resonance chamber is arranged on a cavity that connects relief opening on the cylinder, can effectively reduce the noise that gas flows out, but offering of helmholtz resonance chamber can reduce the gas discharge capacity, therefore in the compressor of double gas, generally only offer a helmholtz resonance chamber, reach the loss of eliminating certain noise and avoiding excessive air displacement.But wherein have the pressurized gas about half to flow out by relief opening one end of not offering the helmholtz resonance chamber, erasure effect is undesirable.
The model utility content
Of the present utility model is at the not good problem of present double gas rotary compressor erasure effect, and a kind of double gas rotary compressor that overcomes the above problems is provided.
For reaching above purpose, adopt following technological scheme:
Novel double gas rotary compressor, the sealing cylinder chamber is enclosed at the two ends that upper flange, lower flange are arranged on cylinder, cylinder is symmetrical arranged two relief openings at upper-lower position, and upper flange, lower flange relevant position are provided with the exhaust passage, and the outer end of exhaust passage is provided with exhaust valve plate and catch; Described two a relief openings wherein relief opening are provided with the helmholtz resonance chamber; The thickness size of exhaust valve plate of relief opening that the helmholtz resonance chamber is set is littler than the thickness size of another exhaust valve plate.
The thickness difference of the thickness of the exhaust valve plate of the wherein said relief opening that the helmholtz resonance chamber is set and the thickness of another exhaust valve plate is L, and the value range of L is 0.03≤L≤0.08MM.
Wherein said L=0.05MM.
The beneficial effects of the utility model are: novel double gas rotary compressor of the present utility model, the sealing cylinder chamber is enclosed at the two ends that upper flange, lower flange are arranged on cylinder, cylinder is symmetrical arranged two relief openings at upper-lower position, upper flange, lower flange relevant position are provided with the exhaust passage, and the outer end of exhaust passage is provided with exhaust valve plate and catch; Described two a relief openings wherein relief opening are provided with the helmholtz resonance chamber; The thickness size of exhaust valve plate of relief opening that the helmholtz resonance chamber is set is littler than the thickness size of another exhaust valve plate; In the compressor operation, owing to the exhaust valve plate of the relief opening that the helmholtz resonance chamber is set is thinner than another exhaust valve plate, thin exhaust valve plate is opened exhaust in advance under the effect of pressurized gas, most of pressurized gas will pass through from the relief opening that the helmholtz resonance chamber is set, can more effectively reduce the exhaust airstream noise, and follow-up air communication crossed helmholtz resonance chamber pneumatic noise is not set certain attenuation is also arranged, thereby can effectively the compressor airflow noise be reduced to lower.
Description of drawings
Fig. 1 is a cylinder assembly cross-sectional view of the present utility model;
Fig. 2 structural representation of air cylinder of the present utility model.
Embodiment
Below in conjunction with accompanying drawing the utility model is further specified:
As shown in Figure 1, 2, novel double gas rotary compressor, the sealing cylinder chamber is enclosed at the upper flange 1 of formation cylinder assembly, the two ends that lower flange 2 is arranged on cylinder 3, cylinder 3 is symmetrical arranged two relief openings 31 at upper-lower position, upper flange 1, lower flange 2 relevant positions are provided with exhaust passage 32, and the outer end of exhaust passage 32 is provided with exhaust valve plate 33 and catch 34; Two relief openings 31 a wherein relief opening 31 are provided with helmholtz resonance chamber 35 (present embodiment is arranged on the relief opening 31 of the lower end of cylinder 3 and sees Fig. 1), certainly as those of ordinary skills, pass through present embodiment, need not the relief opening 31 that creative work can be arranged on helmholtz resonance chamber 35 cylinder 3 upper ends, do not do too much at this and give unnecessary details; The thickness size of exhaust valve plate 33 of relief opening 31 that helmholtz resonance chamber 35 is set is littler than the thickness size of another exhaust valve plate 33; Sum up and get through the inventor test of many times: the thickness difference that the thickness of the thickness of exhaust valve plate 33 of relief opening 31 in helmholtz resonance chamber 35 and another exhaust valve plate 33 is set is L, the value range of L is that 0.03≤L≤0.08MM effect is better, as preferred embodiments of the present utility model, the L value is 0.05MM.
During the utility model compressor operating, owing to the exhaust valve plate 33 of the relief opening 31 that helmholtz resonance chamber 35 is set is thinner than another exhaust valve plate 33, thin exhaust valve plate 33 is opened and exhaust in advance than another exhaust valve plate 33 under the effect of pressurized gas, most of pressurized gas will pass through from the relief opening 31 that helmholtz resonance chamber 35 is set, can more effectively reduce the exhaust airstream noise, and follow-up air communication crossed helmholtz resonance chamber 35 pneumatic noises are not set certain attenuation is also arranged, thereby can effectively the compressor airflow noise be reduced to lower.
The above embodiment, it is preferred embodiments of the present utility model, be not to limit the utility model practical range,, all should be included in the utility model patent claim so all equivalences of doing according to the described structure of the utility model claim, feature and principle change or modify.
Claims (3)
1. novel double gas rotary compressor, the sealing cylinder chamber is enclosed at the two ends that upper flange (1), lower flange (2) are arranged on cylinder (3), cylinder (3) is symmetrical arranged two relief openings (31) at upper-lower position, upper flange (1), lower flange (2) relevant position are provided with exhaust passage (32), and the outer end of exhaust passage (32) is provided with exhaust valve plate (33) and catch (34); Described two relief openings (a 31) wherein relief opening (31) are provided with helmholtz resonance chamber (35); It is characterized in that the thickness size of exhaust valve plate (33) of relief opening (31) that helmholtz resonance chamber (35) are set is littler than the thickness size of another exhaust valve plate (33).
2. novel double gas rotary compressor according to claim 1, it is characterized in that, the thickness difference of the thickness of the exhaust valve plate (33) of the described relief opening (31) that helmholtz resonance chamber (35) are set and the thickness of another exhaust valve plate (33) is L, and the value range of L is 0.03≤L≤0.08MM.
3. novel double gas rotary compressor according to claim 2 is characterized in that described L=0.05MM.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009201700706U CN201486859U (en) | 2009-08-17 | 2009-08-17 | Novel double-exhaust rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009201700706U CN201486859U (en) | 2009-08-17 | 2009-08-17 | Novel double-exhaust rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201486859U true CN201486859U (en) | 2010-05-26 |
Family
ID=42425736
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009201700706U Expired - Fee Related CN201486859U (en) | 2009-08-17 | 2009-08-17 | Novel double-exhaust rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201486859U (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102168665A (en) * | 2011-05-03 | 2011-08-31 | 芜湖欧宝机电有限公司 | Cylinder seat of piston type refrigerating compressor |
| CN102588284A (en) * | 2012-03-31 | 2012-07-18 | 松下·万宝(广州)压缩机有限公司 | Rotary compressor |
| CN103821726A (en) * | 2014-02-11 | 2014-05-28 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN104989645A (en) * | 2015-07-13 | 2015-10-21 | 同济大学 | Multiple-exhaust-pressure rolling rotor type compressor |
| CN107355385A (en) * | 2017-08-31 | 2017-11-17 | 广东美芝制冷设备有限公司 | Double-exhaust compression assembly and rotary compressor |
| CN110785566A (en) * | 2017-07-19 | 2020-02-11 | 大金工业株式会社 | Rotary compressor |
| CN111043006A (en) * | 2019-12-11 | 2020-04-21 | 安徽美芝精密制造有限公司 | Single-cylinder compressor and heat exchange working equipment |
| CN112145418A (en) * | 2019-06-28 | 2020-12-29 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigeration cycle device |
-
2009
- 2009-08-17 CN CN2009201700706U patent/CN201486859U/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102168665A (en) * | 2011-05-03 | 2011-08-31 | 芜湖欧宝机电有限公司 | Cylinder seat of piston type refrigerating compressor |
| CN102588284A (en) * | 2012-03-31 | 2012-07-18 | 松下·万宝(广州)压缩机有限公司 | Rotary compressor |
| CN102588284B (en) * | 2012-03-31 | 2014-10-29 | 松下·万宝(广州)压缩机有限公司 | Rotary compressor |
| CN103821726A (en) * | 2014-02-11 | 2014-05-28 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN104989645A (en) * | 2015-07-13 | 2015-10-21 | 同济大学 | Multiple-exhaust-pressure rolling rotor type compressor |
| CN104989645B (en) * | 2015-07-13 | 2017-04-12 | 同济大学 | Multiple-exhaust-pressure rolling rotor type compressor |
| CN110785566A (en) * | 2017-07-19 | 2020-02-11 | 大金工业株式会社 | Rotary compressor |
| CN110785566B (en) * | 2017-07-19 | 2022-07-08 | 大金工业株式会社 | Rotary compressor |
| US11585343B2 (en) | 2017-07-19 | 2023-02-21 | Daikin Industries, Ltd. | Muffler for a compression mechanism of a rotary compressor |
| CN107355385A (en) * | 2017-08-31 | 2017-11-17 | 广东美芝制冷设备有限公司 | Double-exhaust compression assembly and rotary compressor |
| CN112145418A (en) * | 2019-06-28 | 2020-12-29 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigeration cycle device |
| CN111043006A (en) * | 2019-12-11 | 2020-04-21 | 安徽美芝精密制造有限公司 | Single-cylinder compressor and heat exchange working equipment |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100526 Termination date: 20180817 |