CN201288669Y - High-pressure exhaust structure of rotary compressor and rotary compressor with same - Google Patents
High-pressure exhaust structure of rotary compressor and rotary compressor with same Download PDFInfo
- Publication number
- CN201288669Y CN201288669Y CNU2008201765250U CN200820176525U CN201288669Y CN 201288669 Y CN201288669 Y CN 201288669Y CN U2008201765250 U CNU2008201765250 U CN U2008201765250U CN 200820176525 U CN200820176525 U CN 200820176525U CN 201288669 Y CN201288669 Y CN 201288669Y
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- outlet valve
- high pressure
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- 238000004891 communication Methods 0.000 claims description 3
- 229910000831 Steel Inorganic materials 0.000 claims description 2
- 230000000694 effects Effects 0.000 claims description 2
- 239000010959 steel Substances 0.000 claims description 2
- 239000003507 refrigerant Substances 0.000 abstract description 6
- 230000006835 compression Effects 0.000 abstract 1
- 238000007906 compression Methods 0.000 abstract 1
- 238000000034 method Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000007599 discharging Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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Abstract
The utility model provides a rotary compressor that is used for rotary compressor's high-pressure exhaust structure and has this exhaust structure. The high-pressure exhaust structure comprises a first exhaust valve and is arranged on a flange of the compressor and corresponds to a high-pressure cavity of the compressor. Due to the fact that the second exhaust valve is arranged, when the working condition is severe and the exhaust pressure is high, the second exhaust valve plate is opened, part of high-pressure refrigerants in the high-pressure cavity are discharged in advance, load is reduced, the phenomenon that the compressor cannot work normally is prevented, and the compression resistance and the working reliability of the compressor are improved.
Description
Technical field
The utility model relates to compressor field, particularly, relates to a kind of high pressure gas structure of rotary compressor and rotary compressor with this structure of being used for.
Background technique
In the prior art, the part corresponding with hyperbaric chamber cylinder on the rotary compressor on the lower flange is provided with exhaust port, is used for the pressurized gas in the compressor cylinder hyperbaric chamber are ejected compressor pump from this exhaust port.Rotary compressor has certain scope of bearing pressure, can the life-span of compressor be impacted when the pressure of hyperbaric chamber surpasses this scope.It is about 2.9Mpa that the maximum of common rotary compressor can be born pressure, under general operating mode, can keep proper functioning, but abominable in operating mode, when exhaust pressure is higher, the resisting moment of rotary compressor motor is bigger, might cause compressor to crash or other quality problems.
The model utility content
The utility model is intended to solve the aforementioned problems in the prior, and therefore, the utility model proposes a kind of novel high-pressure exhaust structure of rotary compressor and rotary compressor with this high pressure gas structure of being used for.
Comprise first outlet valve according to high pressure gas structure of the present utility model, it is arranged on the flange of described compressor and corresponding to the hyperbaric chamber of described compressor, wherein, this high pressure gas structure also comprises second outlet valve, and described second outlet valve also is arranged on the flange of described compressor and corresponding to the hyperbaric chamber of described compressor.
Preferably, described second outlet valve comprises: exhaust port is communicated with described hyperbaric chamber; Elastic valve plate is subjected to the pressure effect of described hyperbaric chamber optionally to open or seal described exhaust port; Baffle plate is fixed in described flange and is positioned at the described elastic valve plate outside, limits the distortion of described elastic valve plate.
Preferably, the exhaust port of described second outlet valve comprises: first portion, and the one end is in communication with the outside; Second portion, the one end is communicated with described hyperbaric chamber; And connecting passage, between described first portion and described second portion, extend and the other end of described first portion is connected with the other end of described second portion.
Preferably, described connecting passage extends to the side margin of described flange.
Preferably, the aperture of described second portion and described connecting passage is 2-4mm, and the aperture of described first portion is 2-6mm.
Preferably, the line of the exhaust port of second outlet valve and flange center becomes 20-30 ° angle with respect to substantially horizontal.
Preferably, described first outlet valve and described second outlet valve all by screw on described flange.
According to high pressure gas structure of the present utility model, owing to be provided with second outlet valve, thereby abominable in operating mode, when exhaust pressure is higher, second exhaust valve plate is opened, in advance the part high pressure refrigerant in the hyperbaric chamber is discharged, reduce load, prevent the phenomenon of compressor cisco unity malfunction, the anti-pressure ability and the functional reliability of compressor have been improved, and because the unique texture of second outlet valve, make elastic valve plate and baffle plate be hit and reduce, thereby prolonged working life and reduced manufacture cost.
Description of drawings
Fig. 1 schematically shows the high pressure gas structure according to the utility model first embodiment's rotary compressor;
Fig. 2 schematically shows the sectional view of Fig. 1 along the A-A direction;
Fig. 3 a-Fig. 3 c schematically shows the workflow of second outlet valve of Fig. 1 mesohigh exhaust structure;
Fig. 4 schematically shows the high pressure gas structure according to the utility model second embodiment's rotary compressor;
Fig. 5 schematically shows among Fig. 4 the sectional view along the B-B direction.
Embodiment
Reach specific embodiment below with reference to accompanying drawings to doing detailed description according to the high pressure gas structure that is used for rotary compressor of the present utility model.
Fig. 1 schematically shows the high pressure gas structure according to the utility model first embodiment's rotary compressor.This high pressure gas structure comprises: first outlet valve 3, such as by screw on the flange 1 of compressor (not shown) and corresponding to the hyperbaric chamber of compressor, wherein this structure also comprises second outlet valve 2, and this second outlet valve 2 is fixed on the flange 1 and corresponding to hyperbaric chamber.Fig. 2 shows along the partial sectional view of A-A intercepting among Fig. 1, as shown in Figure 2, second outlet valve 2 comprises: penetrate the exhaust port 7 that flange 1 is connected with hyperbaric chamber, optionally open or seal the elastic valve plate 6 of this exhaust port 7, and be positioned at the baffle plate 5 of the elastic valve plate outside with control elastic valve plate 6 resiliently deformable distances away from flange.Second outlet valve 2 is fixed on the flange 1 by screw 4.Preferably, first outlet valve 3 can have the structure similar to this second outlet valve, and the aperture of exhaust port 7 is 2-6mm.Preferably, as shown in Figure 1, the exhaust port 7 of this second outlet valve 2 and the line of flange center are 20-30 ° with respect to the angle C of substantially horizontal.
Fig. 3 a to Fig. 3 c shows the workflow of second outlet valve 2.Particularly, when rotary compressor in common operating mode following time, first outlet valve 3 is opened, second outlet valve 2 is closed (shown in Fig. 3 a), pressurized gas are discharged the compressor proper functioning by first outlet valve 3; When operating mode more abominable, when exhaust pressure is higher, because the pressure of cylinder interior is excessive, cause the resisting moment of motor bigger, thereby possible stall is crashed or other quality problems occurred, for this reason in according to high pressure gas structure of the present utility model, under the abominable situation of operating mode, shown in Fig. 3 b, the elastic valve plate 6 of second outlet valve 2 is opened, thereby in advance the part high pressure refrigerant in the hyperbaric chamber is discharged along the direction of arrow, reduced load, reduce the motor resisting moment, gas in the hyperbaric chamber is discharged by first outlet valve 3 subsequently, when the pressure recovery normal level in the hyperbaric chamber, elastic valve plate 6 returns back to original position, is about to exhaust port 7 sealings.
Fig. 4 shows the high pressure gas structure according to the utility model second embodiment, and Fig. 5 is the sectional view along B-B line intercepting among Fig. 4.As shown in Figure 4, high pressure gas structure according to this second embodiment comprises: first outlet valve 3, such as by screw on the flange 1 of compressor (not shown) and corresponding to the hyperbaric chamber of compressor, wherein this structure also comprises second outlet valve 2, and this second outlet valve 2 also is fixed on the flange 1 and corresponding to hyperbaric chamber.
This second embodiment's second outlet valve and first embodiment are basic identical, for the purpose of concise and to the point, omit the description to these same sections below, and only the vent structure that is different from first embodiment's exhaust port 7 of second outlet valve 2 are described.
In this second embodiment, as shown in Figure 5, the exhaust port of second outlet valve 2 comprises: first portion 72, and the one end is in communication with the outside, and the other end stretches in the flange 1; Second portion 74, the one end is connected with hyperbaric chamber, and the other end stretches in the flange 1; Connecting passage 76, it extends in the zone between first portion 72 and the second portion 74 in flange and the corresponding the other end of first portion 72 and second portion 74 is connected.
In first embodiment, exhaust port 7 is formed by straight hole, and is stronger to the impact of valve block and baffle plate because exhaust pressure is bigger when the high pressure refrigerant is directly discharged via straight hole, very high to the toughness and the requirement of strength of its material.And adopt vent structure among second embodiment, when second outlet valve 2 is opened, the high pressure refrigerant enters exhaust port along Fig. 5 direction of arrow, because this exhaust port has been avoided the straight hole form of direct discharging, thereby can reduce surge pressure to elastic valve plate 6 and baffle plate (not shown in Fig. 5), under identical working life, this elastic valve plate uses steel commonly used just can meet the demands, thereby saved fabricating cost, and improved product performance.
Preferably, as shown in Figure 5, this connecting passage 76 extends to the side margin 12 of flange always in flange inside, be for convenient this connecting passage that forms in process for making like this, and then form this vent structure, because after rotary compressor assembles, the side margin of flange 12 is surrounded by housing, does not therefore have refrigerant and overflows.Preferably, in this embodiment, the aperture of second portion and connecting passage is 2-4mm, and the aperture of first portion is 2-6mm.
Through facts have proved, the pressure maximum that adopts the rotary compressor of high pressure gas structure of the present utility model to bear is about 3.4Mpa, has improved about 20 percent than the rotary compressor of prior art.
Although describe embodiment of the present utility model with reference to the accompanying drawings, but should be appreciated that, under the situation that does not break away from scope and spirit of the present utility model, those skilled in the relevant art can make variations and modifications, and all changes and modification all are intended to be comprised by claims.
Claims (10)
1. high pressure gas structure that is used for rotary compressor, comprise first outlet valve (3), the flange (1) that is arranged on described compressor is gone up and corresponding to the hyperbaric chamber of described compressor, it is characterized in that, also comprise second outlet valve (2), the flange (1) that described second outlet valve also is arranged on described compressor is gone up and corresponding to the hyperbaric chamber of described compressor.
2. high pressure gas structure according to claim 1 is characterized in that, described second outlet valve comprises: exhaust port (7) is communicated with described hyperbaric chamber; Elastic valve plate (6) is subjected to the pressure effect of described hyperbaric chamber optionally to open or seal described exhaust port (7); Baffle plate (5) is fixed in described flange (1) and goes up and be positioned at described elastic valve plate (6) outside, limits the distortion of described elastic valve plate (6).
3. high pressure gas structure according to claim 1 is characterized in that, the diameter of the exhaust port (7) of described second outlet valve (2) is 2-6mm.
4. high pressure gas structure according to claim 2 is characterized in that, the exhaust port of described second outlet valve (2) comprising: first portion (72), and the one end is in communication with the outside; Second portion (74), the one end is communicated with described hyperbaric chamber; And connecting passage (76), between described first portion (72) and described second portion (74), extend and the other end of described first portion (72) is connected with the other end of described second portion (74).
5. high pressure gas structure according to claim 4 is characterized in that, described connecting passage (76) extends to the side margin (12) of described flange (1).
6. high pressure gas structure according to claim 4 is characterized in that, the aperture of described second portion (74) and described connecting passage (76) is 2-4mm, and the aperture of described first portion (72) is 2-6mm.
7. high pressure gas structure according to claim 4 is characterized in that, the elastic valve plate (6) of described second outlet valve (2) is made by steel.
8. high pressure gas structure according to claim 1 is characterized in that, the exhaust port of described second outlet valve (2) and the line of flange center become 20-30 ° angle with respect to substantially horizontal.
9. high pressure gas structure according to claim 1 is characterized in that, described first outlet valve (3) and described second outlet valve (2) all are fixed on the described flange (1) by screw (4).
10. a rotary compressor is characterized in that, comprises according to any described high pressure gas structure among the claim 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201765250U CN201288669Y (en) | 2008-11-19 | 2008-11-19 | High-pressure exhaust structure of rotary compressor and rotary compressor with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201765250U CN201288669Y (en) | 2008-11-19 | 2008-11-19 | High-pressure exhaust structure of rotary compressor and rotary compressor with same |
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| Publication Number | Publication Date |
|---|---|
| CN201288669Y true CN201288669Y (en) | 2009-08-12 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNU2008201765250U Expired - Lifetime CN201288669Y (en) | 2008-11-19 | 2008-11-19 | High-pressure exhaust structure of rotary compressor and rotary compressor with same |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103541900A (en) * | 2012-07-12 | 2014-01-29 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary type compressor, refrigerant circulation system and control method thereof |
| CN104976128A (en) * | 2015-07-15 | 2015-10-14 | 广东美芝制冷设备有限公司 | Rotary compressor and compression assembly thereof |
| CN104989645A (en) * | 2015-07-13 | 2015-10-21 | 同济大学 | Multiple-exhaust-pressure rolling rotor type compressor |
| CN105065281A (en) * | 2015-08-05 | 2015-11-18 | 同济大学 | Multi-exhaust-pressure screw type compressor |
| CN106401961A (en) * | 2016-12-08 | 2017-02-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotational compressor and electrical product comprising rotational compressor |
| CN106640645A (en) * | 2015-08-07 | 2017-05-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Fluid flow machine, heat exchange and fluid flow machine operation method |
| 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 |
-
2008
- 2008-11-19 CN CNU2008201765250U patent/CN201288669Y/en not_active Expired - Lifetime
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103541900B (en) * | 2012-07-12 | 2016-11-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary Compressor, refrigerant-cycle systems and control method thereof |
| CN103541900A (en) * | 2012-07-12 | 2014-01-29 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary type compressor, refrigerant circulation system and control method thereof |
| 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 |
| CN104976128B (en) * | 2015-07-15 | 2018-01-23 | 广东美芝制冷设备有限公司 | Rotary compressor and its compression assembly |
| CN104976128A (en) * | 2015-07-15 | 2015-10-14 | 广东美芝制冷设备有限公司 | Rotary compressor and compression assembly thereof |
| CN105065281A (en) * | 2015-08-05 | 2015-11-18 | 同济大学 | Multi-exhaust-pressure screw type compressor |
| CN105065281B (en) * | 2015-08-05 | 2017-05-24 | 同济大学 | Multi-exhaust-pressure screw type compressor |
| CN106640645A (en) * | 2015-08-07 | 2017-05-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Fluid flow machine, heat exchange and fluid flow machine operation method |
| CN106640645B (en) * | 2015-08-07 | 2019-05-31 | 珠海格力电器股份有限公司 | Fluid machine, heat exchange device and operation method of fluid machine |
| US10941771B2 (en) | 2015-08-07 | 2021-03-09 | Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai | Fluid machinery, heat exchange equipment, and operating method for fluid machinery |
| CN106401961A (en) * | 2016-12-08 | 2017-02-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotational compressor and electrical product comprising rotational compressor |
| CN106401961B (en) * | 2016-12-08 | 2018-09-07 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary compressor and electric equipment products including the 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 |
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Legal Events
| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20090812 |