CN102444583A - Birotor compressor - Google Patents
Birotor compressor Download PDFInfo
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- CN102444583A CN102444583A CN2010105020338A CN201010502033A CN102444583A CN 102444583 A CN102444583 A CN 102444583A CN 2010105020338 A CN2010105020338 A CN 2010105020338A CN 201010502033 A CN201010502033 A CN 201010502033A CN 102444583 A CN102444583 A CN 102444583A
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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
Decreased performance is obvious during the common compressor low-temperature heating, so need just can reach the demand of system to heating capacity through the auxiliary electrical heating, power consumption will increase like this.The bent axle of existing two-spool compressor has two eccentric parts; And phase phase difference 180 degree of two eccentric parts; The exhaust that makes progress of high pressure air, the phase difference of low pressure (LP) cylinder phase 0 degree, high-pressure cylinder, low pressure (LP) cylinder to downward exhaust again through opening with the gas guiding of discharging and upwards discharge.
Since the high-pressure cylinder of existing two-spool compressor, low pressure (LP) cylinder phase phase difference 0 degree, compressor pump fluid flow inside path difference, and fluid pulsation is bigger; High-pressure cylinder is air-breathing not full; And when making compressor operating, high-pressure cylinder and low pressure (LP) cylinder are worked simultaneously, and the load of compressor is bigger.
Summary of the invention
The objective of the invention is to overcome the defective of existing technology, a kind of two-spool compressor is provided, the present invention can make high-pressure cylinder and the low pressure (LP) cylinder several angle that staggers; Change compressor pump fluid flow inside path, make to increase enthalpy mouth gas that gets into and the gas that low pressure (LP) cylinder gets into and fully mix, reduce circulation and pulse; Thereby reduce the suction and discharge resistance; Make high-pressure cylinder air-breathing fuller, improve the performance of compressor, avoid high-pressure cylinder, low pressure (LP) cylinder to work simultaneously.
Its technological scheme is following:
A kind of two-spool compressor comprises housing, in housing, is provided with bent axle, low pressure (LP) cylinder and high-pressure cylinder, on bent axle, is provided with low pressure eccentric part and high pressure eccentric part, and low pressure eccentric part, high pressure eccentric part cooperate with low pressure (LP) cylinder, high-pressure cylinder respectively; Low pressure eccentric part and high pressure eccentric part are the 0 °+θ setting of staggering with phase difference.
The technological scheme of the further refinement of aforementioned techniques scheme can be:
Described high-pressure cylinder and low pressure (LP) cylinder are the 180 °+θ setting of staggering at the phase difference in when assembling.
Said high pressure eccentric part and low pressure eccentric part are eccentric cam, and the high pressure eccentric part is H1 with respect to the height of its gyration center, and the low pressure eccentric part is H2 with respect to the height of its gyration center, H1/H2=0.5 to 0.9.
Between low pressure (LP) cylinder and high-pressure cylinder, also be provided with middle 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.
On middle cylinder, be connected with and increase the enthalpy mouth.
Between said middle cylinder high-pressure cylinder, also be provided with pump housing dividing plate, on pump housing dividing plate, be provided with the gas stream groove, on said high-pressure cylinder, be provided with the intakeport of cutting sth. askew, on said middle cylinder, be provided with the intermediate exhaust mouth; The gas stream groove be positioned at the intakeport of cutting sth. askew under, become angle between the axial connecting line of the axial connecting line of gas stream groove and bent axle, intermediate exhaust mouth and bent axle, and the phase difference θ that exists between this angle and low pressure eccentric part, the high pressure eccentric part equates.
Said middle cylinder comprises cylinder main body, lock screw, baffle plate and valve block, and lock screw is pressed on baffle plate and valve block on the cylinder main body, and valve block is corresponding with the position of said intermediate exhaust mouth.
Below said low pressure (LP) cylinder, be provided with lower flange, above said high-pressure cylinder, be provided with upper flange.
Said angle is preferably 60 degree less than 90 degree.
In sum, advantage of the present invention is:
1, owing to have angle between low pressure eccentric part and the high pressure eccentric part, makes there is certain phase difference between high-pressure cylinder and the low pressure (LP) cylinder load when having reduced compressor operating;
2, between low pressure (LP) cylinder and high-pressure cylinder, be provided with middle cylinder, low pressure (LP) cylinder institute exhaust body gets into high-pressure cylinder through middle cylinder, has reduced the resistance in the process fluid flow, has reduced the air-breathing pulsation of high-pressure cylinder, has improved the performance of compressor;
3, on middle cylinder, be provided with and increase the enthalpy mouth, carry out tonifying Qi, improved the performance of compressor through increasing the enthalpy mouth;
4, owing to the angle between high pressure eccentric part, the low pressure eccentric part is spent less than 80, the ratio H1/H2=0.5 to 0.9 between high pressure eccentric part and the low pressure eccentric part through selecting suitable phase difference and height ratio, can make compressor reach best running state.
Description of drawings
Fig. 1 is the sectional view of the said two-spool compressor of the embodiment of the invention;
Fig. 2 is the stereogram of bent axle;
Fig. 3 is the axial view of bent axle;
Fig. 4 is the wherein disassembly diagram of a side of lower flange, low pressure (LP) cylinder, middle cylinder, pump housing dividing plate, high-pressure cylinder and upper flange;
Fig. 5 is the disassembly diagram of lower flange, low pressure (LP) cylinder, middle cylinder, pump housing dividing 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 housing dividing plate, 7, lower flange, 8, upper flange, 9, the high pressure eccentric part, 10, the low pressure eccentric part; 11, increase the enthalpy mouth, 12, the gas stream groove, 13, the intakeport of cutting sth. askew, 14, the 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 elaborated:
Extremely shown in Figure 7 like Fig. 1; A kind of two-spool compressor comprises housing 1, in housing 1, is provided with bent axle 2, rotor 19, stator 20; Rotor 19 is connected with bent axle 2; Low pressure (LP) cylinder 3 and high-pressure cylinder 4 are provided with low pressure eccentric part 10 and high pressure eccentric part 9 on bent axle 2, low pressure eccentric part 10, high pressure eccentric part 9 cooperate with low pressure (LP) cylinder 3, high-pressure cylinder 4 respectively; There is phase difference (angle θ as shown in Figure 3) between low pressure eccentric part 10 and the high pressure eccentric part 9.
Wherein, high pressure eccentric part 9 and low pressure eccentric part 10 are eccentric cam, and high pressure eccentric part 9 is H1 with respect to the height of its gyration center, and low pressure eccentric part 10 is H2 with respect to the height of its gyration center, H1/H2=0.5 to 0.9 (being preferably 0.6 to 0.8).
Between low pressure (LP) cylinder 3 and high-pressure cylinder 4, also be 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 cylinders 4, also be provided with pump housing dividing plate 6, on pump housing dividing plate 6, be provided with gas stream groove 12, on high-pressure cylinder 4, be provided with the intakeport 13 of cutting sth. askew, on middle cylinder 5, be provided with intermediate exhaust mouth 14; Gas stream groove 12 be positioned at the intakeport 13 of cutting sth. askew under; Become angle between the axial connecting line of the axial connecting line of gas stream groove 12 and bent axle 2, intermediate exhaust mouth 14 and bent axle 2, and exist phase difference θ to equate between this angle and low pressure eccentric part 10, the high pressure eccentric part 9.On middle cylinder 5, be connected with and increase enthalpy mouth 11, said middle cylinder 5 comprises cylinder main body 15, lock screw 16, baffle plate 17 and valve block 18, and lock screw 16 is pressed on baffle plate 17 and valve block 18 on the cylinder main body 15, and valve block 18 is corresponding with the position of intermediate exhaust mouth 14.Below low pressure (LP) cylinder 3, be provided with lower flange 7, above high-pressure cylinder 4, be provided with upper flange 8.
In sum, advantage of the present invention is:
1, owing to have angle between low pressure eccentric part 10 and the high pressure eccentric part 9, makes to have certain phase difference between high-pressure cylinder 4 and the low pressure (LP) cylinder 3, the load when having reduced compressor operating;
2, between low pressure (LP) cylinder 3 and high-pressure cylinder 4, be provided with middle cylinder 5,3 exhaust bodies of low pressure (LP) cylinder get into high-pressure cylinder 4 through middle cylinder 5, have reduced the resistance in the process fluid flow, have reduced the air-breathing pulsation of high-pressure cylinder 4, have improved the performance of compressor;
3, on middle cylinder 5, be provided with and increase enthalpy mouth 11, carry out tonifying Qi, through the phase difference that exists between high-pressure cylinder 4 and the low pressure (LP) cylinder 3 through increasing enthalpy mouth 11; Change compressor pump fluid flow inside path; Make to increase enthalpy mouth 11 gas that gets into and the gas that low pressure (LP) cylinder 3 gets into and fully mix, reduce the circulation pulsation, thus reduction suction and discharge resistance; Make high-pressure cylinder air-breathing fuller, improved the performance of compressor;
4, through selecting phase difference suitable between high pressure eccentric part 9, the low pressure eccentric part 10 and height ratio, can make compressor reach best running state.
More than be merely specific embodiment of the present invention, do not limit protection scope of the present invention with this; Any replacement and the improvement on the basis of not violating the present invention's design, done all belong to protection scope of the present invention.
Claims (10)
1. a two-spool compressor comprises housing, in housing, is provided with bent axle, low pressure (LP) cylinder and high-pressure cylinder, on bent axle, is provided with low pressure eccentric part and high pressure eccentric part, and low pressure eccentric part, high pressure eccentric part cooperate with low pressure (LP) cylinder, high-pressure cylinder respectively; It is characterized in that low pressure eccentric part and high pressure eccentric part are the 0 °+θ setting of staggering with phase difference.
2. two-spool compressor as claimed in claim 1 is characterized in that, described high-pressure cylinder and low pressure (LP) cylinder are the 180 °+θ setting of staggering at the phase difference in when assembling.
3. two-spool compressor according to claim 1; It is characterized in that said high pressure eccentric part and low pressure eccentric part are eccentric cam, the high pressure eccentric part is H1 with respect to the height of its gyration center; The low pressure eccentric part is H2 with respect to the height of its gyration center, H1/H2=0.5 to 0.9.
4. two-spool compressor according to claim 1 is characterized in that between low pressure (LP) cylinder and high-pressure cylinder, also be provided with middle 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.
5. like the said two-spool compressor of claim 4, it is characterized in that, on middle cylinder, be connected with and increase the enthalpy mouth.
6. like the said two-spool compressor of claim 4; It is characterized in that, between said middle cylinder high-pressure cylinder, also be provided with pump housing dividing plate, on pump housing dividing plate, be provided with the gas stream groove; On said high-pressure cylinder, be provided with the intakeport of cutting sth. askew, on said middle cylinder, be provided with the intermediate exhaust mouth; The gas stream groove be positioned at the intakeport of cutting sth. askew under, become angle between the axial connecting line of the axial connecting line of gas stream groove and bent axle, intermediate exhaust mouth and bent axle, and the phase difference θ that exists between this angle and low pressure eccentric part, the high pressure eccentric part equates.
7. like the said two-spool compressor of claim 6, it is characterized in that said middle cylinder comprises cylinder main body, lock screw, baffle plate and valve block, lock screw is pressed on baffle plate and valve block on the cylinder main body, and valve block is corresponding with the position of said intermediate exhaust mouth.
8. like the said two-spool compressor of claim 6, it is characterized in that, below said low pressure (LP) cylinder, be provided with lower flange, above said high-pressure cylinder, be provided with upper flange.
9. like each said two-spool compressor in the claim 1 to 8, it is characterized in that said θ is less than 90 °.
10. two-spool compressor as claimed in claim 9 is characterized in that, said 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 |
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| Publication Number | Publication Date |
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| CN102444583A true CN102444583A (en) | 2012-05-09 |
| CN102444583B CN102444583B (en) | 2015-01-21 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201010502033.8A Expired - Fee Related CN102444583B (en) | 2010-09-30 | 2010-09-30 | Birotor compressor |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103866400A (en) * | 2014-03-10 | 2014-06-18 | 陈勇 | Sapphire production system |
| CN104632624A (en) * | 2013-12-25 | 2015-05-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Double-cylinder double-stage compressor |
| 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 |
| 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 |
| WO2023103874A1 (en) * | 2021-12-07 | 2023-06-15 | 珠海格力电器股份有限公司 | Fluid machinery, heat exchange apparatus, and operation method for fluid machinery |
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| 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 |
| CN1299011A (en) * | 2000-09-30 | 2001-06-13 | 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 |
-
2010
- 2010-09-30 CN CN201010502033.8A patent/CN102444583B/en not_active Expired - Fee Related
Patent Citations (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 |
| CN1299011A (en) * | 2000-09-30 | 2001-06-13 | 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 |
Cited By (6)
| 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 |
| CN104632624A (en) * | 2013-12-25 | 2015-05-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Double-cylinder double-stage compressor |
| CN103866400A (en) * | 2014-03-10 | 2014-06-18 | 陈勇 | Sapphire production system |
| 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 |
| WO2023103874A1 (en) * | 2021-12-07 | 2023-06-15 | 珠海格力电器股份有限公司 | Fluid machinery, heat exchange apparatus, and operation method for fluid machinery |
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| Publication number | Publication date |
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| CN102444583B (en) | 2015-01-21 |
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