CN102444583B - Birotor compressor - Google Patents
Birotor compressor Download PDFInfo
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- CN102444583B CN102444583B CN201010502033.8A CN201010502033A CN102444583B CN 102444583 B CN102444583 B CN 102444583B CN 201010502033 A CN201010502033 A CN 201010502033A CN 102444583 B CN102444583 B CN 102444583B
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Abstract
The invention discloses a birotor compressor comprising a shell. The inside of the shell is provided with a crankshaft, a low pressure cylinder and a high pressure cylinder. The crankshaft is equipped with a low pressure eccentric part and a high pressure eccentric part that are respectively mated with the low pressure cylinder and the high pressure cylinder. And an included angle exists between the low pressure eccentric part and the high pressure eccentric part. The birotor compressor of the invention can make the high pressure cylinder and low pressure cylinder staggered to a certain angle so as to avoid simultaneous operation of the high pressure cylinder and the low pressure cylinder, change a fluid flow path inside a compressor pump body, make the gas entering from an enthalpy adding port and the gas entering the low pressure cylinder fully mixed, and reduce circulation pulsation, so that the suction and exhaust resistance can be reduced, the high pressure cylinder suction can be fuller, and the performance of the compressor can be improved.
Description
Technical field
The invention belongs to field of air conditioning, be specifically related to a kind of two-spool compressor.
Background technique
During common compressor low-temperature heating, hydraulic performance decline is obvious, therefore needs just can reach the demand of system to heating capacity by auxiliary electrical heater, and such power consumption will increase.The bent axle of existing two-spool compressor has two eccentric parts, and the phase 180 degree of two eccentric parts, high pressure air, low pressure (LP) cylinder phase 0 degree, high-pressure cylinder is upwards vented, and the guiding of the gas of discharge is also upwards discharged by opening to exhaust downwards by low pressure (LP) cylinder again.
Due to high-pressure cylinder, the low pressure (LP) cylinder phase 0 degree of existing two-spool compressor, compressor pump fluid flow inside path difference, fluid pulsation is larger, high-pressure cylinder air-breathing is not full, and when making compressor operating, high-pressure cylinder and low pressure (LP) cylinder work, and the load of compressor is larger simultaneously.
Summary of the invention
The object of the invention is to the defect overcoming prior art, a kind of two-spool compressor is provided, the present invention can make high-pressure cylinder and low pressure (LP) cylinder stagger several angle, change compressor pump fluid flow inside path, the gas that the gas that increasing enthalpy mouth is entered and low pressure (LP) cylinder enter fully mixes, and reduces circulation pulsation, thus reduce suction and discharge resistance, make high-pressure cylinder air-breathing fuller, improve the performance of compressor, avoid high-pressure cylinder, low pressure (LP) cylinder works simultaneously.
Its technological scheme is as follows:
A kind of two-spool compressor, comprise housing, be provided with bent axle, low pressure (LP) cylinder and high-pressure cylinder in housing, bent axle is provided with low pressure eccentric part and high pressure eccentric part, low pressure eccentric part, high pressure eccentric part coordinate with low pressure (LP) cylinder, high-pressure cylinder respectively; Low pressure eccentric part and high pressure eccentric part are that θ staggers and arranges with phase difference, also middle cylinder is provided with between low pressure (LP) cylinder and high-pressure cylinder, low pressure (LP) cylinder communicates with middle cylinder, middle cylinder communicates with high-pressure cylinder, and middle cylinder is between low pressure (LP) cylinder and high-pressure cylinder, between described middle cylinder and high-pressure cylinder, be also provided with pump partition plate, pump partition plate is provided with gas flow groove, described high-pressure cylinder is provided with intakeport of cutting sth. askew, described middle cylinder is provided with intermediate exhaust mouth; Gas flow groove is positioned at immediately below intakeport of cutting sth. askew, and the axial connecting line of gas flow groove and bent axle, becomes angle between intermediate exhaust mouth and the axial connecting line of bent axle, and this angle is equal with the phase difference θ existed between low pressure eccentric part, high pressure eccentric part.
The technological scheme of the further refinement of preceding solution can be:
Described high-pressure cylinder and the low pressure (LP) cylinder phase difference when assembling is that 180 ° of+θ stagger setting.
Described high pressure eccentric part and low pressure eccentric part are eccentric cam, and high pressure eccentric part is H1 relative to the height of its gyration center, and low pressure eccentric part is H2, H1/H2=0.5 to 0.9 relative to the height of its gyration center.
Middle cylinder is connected with and increases enthalpy mouth.
Described middle cylinder comprises cylinder main body, lock screw, baffle plate and valve block, and baffle plate and valve block are pressed in cylinder main body by lock screw, and valve block is corresponding with the position of described intermediate exhaust mouth.
Be provided with lower flange in the below of described low pressure (LP) cylinder, above described high-pressure cylinder, be provided with upper flange.
Described angle is less than 90 degree, is preferably 60 degree.
In sum, advantage of the present invention is:
1, owing to there is angle between low pressure eccentric part and high pressure eccentric part, make between high-pressure cylinder and low pressure (LP) cylinder, to there is certain phase difference, reduce load during compressor operating;
2, between low pressure (LP) cylinder and high-pressure cylinder, be provided with middle cylinder, body that low pressure (LP) cylinder is vented enters high-pressure cylinder through middle cylinder, decreases the resistance in process fluid flow, reduces the air-breathing pulsation of high-pressure cylinder, improves the performance of compressor;
3, on middle cylinder, be provided with increasing enthalpy mouth, carry out tonifying Qi by increasing enthalpy mouth, improve the performance of compressor;
4, because the angle between high pressure eccentric part, low pressure eccentric part is less than 80 degree, the ratio H1/H2=0.5 to 0.9 between high pressure eccentric part and low pressure eccentric part, by selecting suitable phase difference and height ratio, can make the running state that compressor reaches best.
Accompanying drawing explanation
Fig. 1 is the sectional view of two-spool compressor described in the embodiment of the present invention;
Fig. 2 is the stereogram of bent axle;
Fig. 3 is the axial view of bent axle;
Fig. 4 is the disassembly diagram of lower flange, low pressure (LP) cylinder, middle cylinder, pump partition plate, high-pressure cylinder and upper flange wherein side;
Fig. 5 is the disassembly diagram of lower flange, low pressure (LP) cylinder, middle cylinder, pump partition plate, high-pressure cylinder and upper flange opposite side;
Fig. 6 is the plan view of middle cylinder;
Fig. 7 is the B-B sectional view of Fig. 6;
Description of reference numerals:
1, housing, 2, bent axle, 3, low pressure (LP) cylinder, 4, high-pressure cylinder, 5, middle cylinder, 6, pump partition plate, 7, lower flange, 8, upper flange, 9, high pressure eccentric part, 10, low pressure eccentric part, 11, increase enthalpy mouth, 12, gas flow groove, 13, to cut sth. askew intakeport, 14, intermediate exhaust mouth, 15, cylinder main body, 16, lock screw, 17, baffle plate, 18, valve block.
Embodiment
Below in conjunction with accompanying drawing, embodiments of the invention are described in detail:
As shown in Figures 1 to 7, a kind of two-spool compressor, comprise housing 1, bent axle 2, rotor 19, stator 20 is provided with in housing 1, rotor 19 is connected with bent axle 2, low pressure (LP) cylinder 3 and high-pressure cylinder 4, bent axle 2 is provided with low pressure eccentric part 10 and high pressure eccentric part 9, and low pressure eccentric part 10, high pressure eccentric part 9 coordinate with low pressure (LP) cylinder 3, high-pressure cylinder 4 respectively; Phase difference (as shown in Figure 3 angle θ) is there is between low pressure eccentric part 10 and high pressure eccentric part 9.
Wherein, high pressure eccentric part 9 and low pressure eccentric part 10 are eccentric cam, high pressure eccentric part 9 is H1 relative to the height of its gyration center, and low pressure eccentric part 10 is H2, H1/H2=0.5 to 0.9 (being preferably 0.6 to 0.8) relative to the height of its gyration center.
Between low pressure (LP) cylinder 3 and high-pressure cylinder 4, be also provided with middle cylinder 5, low pressure (LP) cylinder 3 communicates with middle cylinder 5, and middle cylinder 5 communicates with high-pressure cylinder 4, and middle cylinder 5 is between low pressure (LP) cylinder 3 and high-pressure cylinder 4.Between middle cylinder 5 high-pressure cylinder 4, be also provided with pump partition plate 6, pump partition plate 6 is provided with gas flow groove 12, high-pressure cylinder 4 is provided with intakeport 13 of cutting sth. askew, middle cylinder 5 is provided with intermediate exhaust mouth 14; Gas flow groove 12 is positioned at immediately below intakeport 13 of cutting sth. askew, the axial connecting line of gas flow groove 12 and bent axle 2, between intermediate exhaust mouth 14 with the axial connecting line of bent axle 2, become angle, and this angle is with to there is phase difference θ between low pressure eccentric part 10, high pressure eccentric part 9 equal.Middle cylinder 5 is connected with and increases enthalpy mouth 11, described middle cylinder 5 comprises cylinder main body 15, lock screw 16, baffle plate 17 and valve block 18, and baffle plate 17 and valve block 18 are pressed in cylinder main body 15 by lock screw 16, and valve block 18 is corresponding with the position of intermediate exhaust mouth 14.Be provided with lower flange 7 in the below of low pressure (LP) cylinder 3, above high-pressure cylinder 4, be provided with upper flange 8.
In sum, advantage of the present invention is:
1, owing to there is angle between low pressure eccentric part 10 and high pressure eccentric part 9, make to there is certain phase difference between high-pressure cylinder 4 and low pressure (LP) cylinder 3, reduce load during compressor operating;
2, between low pressure (LP) cylinder 3 and high-pressure cylinder 4, be provided with middle cylinder 5, low pressure (LP) cylinder 3 be vented body and enter high-pressure cylinder 4 through middle cylinder 5, decrease the resistance in process fluid flow, reduce the air-breathing pulsation of high-pressure cylinder 4, improve the performance of compressor;
3, on middle cylinder 5, be provided with increasing enthalpy mouth 11, tonifying Qi is carried out by increasing enthalpy mouth 11, by the phase difference existed between high-pressure cylinder 4 and low pressure (LP) cylinder 3, change compressor pump fluid flow inside path, the gas that the gas that increasing enthalpy mouth 11 is entered and low pressure (LP) cylinder 3 enter fully mixes, and reduces circulation pulsation, thus reduces suction and discharge resistance, make high-pressure cylinder air-breathing fuller, improve the performance of compressor;
4, by selecting suitable phase difference and height ratio between high pressure eccentric part 9, low pressure eccentric part 10, the running state that compressor reaches best can be made.
These are only specific embodiments of the invention, do not limit protection scope of the present invention with this; Not violating any replacement and improvement that the basis of the present invention's design is done, all belong to protection scope of the present invention.
Claims (8)
1. a two-spool compressor, comprises housing, is provided with bent axle, low pressure (LP) cylinder and high-pressure cylinder in housing, and bent axle is provided with low pressure eccentric part and high pressure eccentric part, and low pressure eccentric part, high pressure eccentric part coordinate with low pressure (LP) cylinder, high-pressure cylinder respectively; It is characterized in that, low pressure eccentric part and high pressure eccentric part are that θ staggers and arranges with phase difference, also middle cylinder is provided with between low pressure (LP) cylinder and high-pressure cylinder, low pressure (LP) cylinder communicates with middle cylinder, and middle cylinder communicates with high-pressure cylinder, and middle cylinder is between low pressure (LP) cylinder and high-pressure cylinder, also pump partition plate is provided with between described middle cylinder and high-pressure cylinder, pump partition plate is provided with gas flow groove, described high-pressure cylinder is provided with intakeport of cutting sth. askew, described middle cylinder is provided with intermediate exhaust mouth; Gas flow groove is positioned at immediately below intakeport of cutting sth. askew, and the axial connecting line of gas flow groove and bent axle, becomes angle between intermediate exhaust mouth and the axial connecting line of bent axle, and this angle is equal with the phase difference θ existed between low pressure eccentric part, high pressure eccentric part.
2. two-spool compressor as claimed in claim 1, is characterized in that, described high-pressure cylinder and the phase difference of low pressure (LP) cylinder when assembling are that 180 ° of+θ stagger setting.
3. two-spool compressor as claimed in claim 1, it is characterized in that, described high pressure eccentric part and low pressure eccentric part are eccentric cam, and high pressure eccentric part is H1 relative to the height of its gyration center, low pressure eccentric part is H2, H1/H2=0.5 to 0.9 relative to the height of its gyration center.
4. two-spool compressor as claimed in claim 1, is characterized in that, middle cylinder is connected with and increases enthalpy mouth.
5. two-spool compressor as claimed in claim 1, it is characterized in that, described middle cylinder comprises cylinder main body, lock screw, baffle plate and valve block, and baffle plate and valve block are pressed in cylinder main body by lock screw, and valve block is corresponding with the position of described intermediate exhaust mouth.
6. two-spool compressor as claimed in claim 1, is characterized in that, be provided with lower flange in the below of described low pressure (LP) cylinder, above described high-pressure cylinder, be provided with upper flange.
7. two-spool compressor according to any one of claim 1 to 6, is characterized in that, described θ is less than 90 °.
8. two-spool compressor as claimed in claim 7, it is characterized in that, described θ is 60 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010502033.8A CN102444583B (en) | 2010-09-30 | 2010-09-30 | Birotor compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010502033.8A CN102444583B (en) | 2010-09-30 | 2010-09-30 | Birotor compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102444583A CN102444583A (en) | 2012-05-09 |
| CN102444583B true CN102444583B (en) | 2015-01-21 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010502033.8A Expired - Fee Related CN102444583B (en) | 2010-09-30 | 2010-09-30 | Birotor compressor |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104632623B (en) * | 2013-12-23 | 2017-02-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Double-stage compressor |
| CN104632624B (en) * | 2013-12-25 | 2016-10-05 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of twin-tub double-stage compressor |
| CN103866400B (en) * | 2014-03-10 | 2016-06-15 | 陈勇 | Sapphire crystal heat-exchanging method growth furnace helium cooling system |
| CN112228338A (en) * | 2019-07-15 | 2021-01-15 | 艾默生环境优化技术(苏州)有限公司 | Compression mechanism and compressor |
| CN116241466A (en) * | 2021-12-07 | 2023-06-09 | 珠海格力电器股份有限公司 | Fluid machine, heat exchange device, and method for operating a fluid machine |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61258988A (en) * | 1985-05-13 | 1986-11-17 | Nippon Air Brake Co Ltd | Rotary piston compressor |
| JPH03237290A (en) * | 1990-02-14 | 1991-10-23 | Matsushita Refrig Co Ltd | Two-cylinder rotary compressor |
| JP2000073974A (en) * | 1998-08-26 | 2000-03-07 | Daikin Ind Ltd | Two stage compressor and air conditioner |
| CN1142368C (en) * | 2000-09-30 | 2004-03-17 | 上海日立电器有限公司 | Multi-cylinder compressor and method for manufacturing accentric shaft |
| CN1978904A (en) * | 2005-12-06 | 2007-06-13 | 上海日立电器有限公司 | Two-stage rolling rotor-type compressor |
| CN201027653Y (en) * | 2006-12-27 | 2008-02-27 | 上海日立电器有限公司 | Unsymmetrical crankshaft structure of two-stage rolling rotor compressor |
| CN201818500U (en) * | 2010-09-30 | 2011-05-04 | 珠海格力节能环保制冷技术研究中心有限公司 | Double-rotor compressor |
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