CN101012831A - Rotor type twin cylinder compressor taking air-breathing through partition board - Google Patents
Rotor type twin cylinder compressor taking air-breathing through partition board Download PDFInfo
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- CN101012831A CN101012831A CN 200710003003 CN200710003003A CN101012831A CN 101012831 A CN101012831 A CN 101012831A CN 200710003003 CN200710003003 CN 200710003003 CN 200710003003 A CN200710003003 A CN 200710003003A CN 101012831 A CN101012831 A CN 101012831A
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Abstract
A rotor dual-cylinder compressor uses the middle baffle plate to absorb air. The middle baffle plate is arranged with a radial adsorption through hole. The upper and lower cylinders are arranged with incline adsorption holes communicated with the adsorption through hole on the middle baffle plate. And the incline adsorption holes are arranged with axial semi-round through hole near the inner side of cylinder and communicated with the incline cuts. The air outlet tube of liquid cylinder of compressor is one-way air outlet tube. Since the thickness of middle baffle plate is not limited by the flux and the invention have adsorption holes on the upper and lower cylinders, the increased thickness of middle baffle plate can increase the section of adsorption chamber, reduce the adsorption resistance, and improve the efficiency.
Description
Technical field
The present invention relates to a kind of rotor type twin cylinder compressor, the upper and lower cylinder that particularly relates to a kind of float amount rotor type twin cylinder compressor central diaphragm and match with it.
Background technique
Present conventional rotor type twin cylinder compressor is to be made of a seal container, middle motor by the pump housing that plays compression and the driving pump housing.The groundwork process of conventional rotor type twin cylinder compressor (as shown in Figure 1) is: central diaphragm (12) is separated into two active chambers with upper cylinder (8), lower cylinder (9), upper and lower slide plate (11) closely contacts with upper rotor part (13), lower rotor part (14) under the effect of spring respectively, and respectively the active chamber of upper cylinder (8), (9) two cylinders of lower cylinder is separated into hyperbaric chamber and low-pressure cavity, in cylinder, do off-centre by rotor and rotatablely move.Low-temp low-pressure working medium enters compressor by the suction port on upper cylinder (8), lower cylinder (9) right side, and in compressor pump, be compressed to High Temperature High Pressure working medium and discharge the pump housing, after the outlet pipe on the seal container (23) is drained into the air conditioner associated components, constitute a complete circulatory system.
The air-breathing mode of above-mentioned conventional rotor type twin cylinder compressor is, two active chambers that central diaphragm (12) is separated into upper cylinder (8), lower cylinder (9), the radial suction hole of upper cylinder (8), lower cylinder (9) is communicated with outside seal container air-breathingly with the two steam outlet pipes (30) of compressor stock solution tube respectively, and central diaphragm (12) (as shown in Figure 4) only plays the effect that upper cylinder (8), lower cylinder (9) is separated into two active chambers.When design float amount duplex cylinder compressor (as with R410A or CO
2Duplex cylinder compressor for working medium), after the throw of eccentric of determining reasonable cylinder bore diameter and eccentric shaft, the height of upper cylinder (8), lower cylinder (9) can be less, if again at the radial design suction port of upper cylinder (8), lower cylinder (9) as air intake passage, can the suction port diameter be restricted because of the cylinder height is less in the pump housing of compressor, increase thereby cause inhalation resistance.The loss of inhalation resistance reduces the gas pressure and the density that enter cylinder, reduces effective gettering quantity of compressor, and then the volume flow of compressor is lowered, so the increase of gas inhalation resistance directly causes the fluid resistance losses of compressor to increase.Simultaneously since gas flow drag losses and flow velocity square be directly proportional also significantly increase of the loss of flow resistance when the rotating speed of compressor improves.In general, the aerodynamic loss of high speed rotating compressor will play certain adverse effect to compressor efficiency, so concerning conventional float amount duplex cylinder compressor, the radial diameter of upper cylinder (8), lower cylinder (9) design suction port is limited, cause the inhalation resistance of compressor to increase, the compressor overall efficiency reduces.Meanwhile, this design makes compressor that two suction tude must be arranged, and causes the cost of compressor also higher relatively.
It was head it off in the past, also there is the scheme that suction port is arranged on loam cake shown in Figure 7 (6) and the lower cover (17) to be used, but can make the structure on loam cake (6) and the lower cover (17) become very complicated like this, and two suction tude must be arranged, thereby cost also compares higher.
Summary of the invention
For solving the problem of above-mentioned existence, the invention provides a kind ofly through the air-breathing rotor type twin cylinder compressor of central diaphragm, this rotor type twin cylinder compressor can effectively reduce inhalation resistance, improve compressor efficiency, reduces the cost of production of compressor.
The technological scheme that the present invention takes is (as shown in Figure 8): the central diaphragm (12) that conventional rotor type twin cylinder compressor is not had air-breathing function changes the air-breathing central diaphragm (23) (as shown in Figure 5) with air-breathing function into, promptly air-breathing central diaphragm (23) radially do one with its end face on the radial direction through hole (23a) that connects of axial hole (23b), the radial direction through hole on the central diaphragm (23a) is communicated with to play effect air-breathing outside seal container with the stock solution tube list steam outlet pipe (31) of compressor list steam outlet pipe stock solution tube (26).The use that has the air-breathing central diaphragm of air-breathing function (23) for cooperation, among the present invention (as Fig. 6, shown in 7) the air-breathing upper cylinder of angular cut (24) arranged, there is the air-breathing lower cylinder of angular cut (25) separately with on the end face that air-breathing central diaphragm (23) cooperates the air-breathing angular cut of the cylinder that matches (28) being arranged all, and done axial semicolumn through hole (29) and the air-breathing angular cut of cylinder (28) at the air-breathing angular cut of cylinder (28) near cylinder bore diameter one side and connected, the air-breathing angular cut of cylinder (28) is communicated with axial hole (23b) on air-breathing central diaphragm (23) end face, assurance will be had the air-breathing upper cylinder of angular cut (24) through the low-pressure low-temperature working medium that air-breathing central diaphragm (23) sucks, there is the air-breathing lower cylinder of angular cut (25) to suck, and then discharges compressor pump after the boil down to High Temperature High Pressure working medium.
For being the float amount rotor type twin cylinder compressor of working medium with R410 or CO2 etc., concerning conventional float amount rotor type twin cylinder compressor, its air-breathing aperture is subject to the height of cylinder, because the cylinder aspect ratio is lower, therefore the air-breathing aperture of this little capacity compressors is also just little.And compare with cylinder, central diaphragm thickness can be not machine discharge capacity restriction by compression, the present invention guarantees that by increasing central diaphragm thickness compressor air-breathing channel cross-sectional area outside seal casinghousing is enough big.Meanwhile, the air-breathing upper cylinder of angular cut (24) is arranged, have the air-breathing angular cut of the air-breathing lower cylinder of angular cut (25) also can not be subjected to the restriction of cylinder height, can amplify by demand, the present invention is by increasing the inhalation resistance that the air-breathing sectional area of compresser cylinder reduces whole compressor thus.Because the generation of compressor air suction resistance causes compressor to produce drag losses, therefore reduce inhalation resistance, the gas flow drag losses also just obtains reducing.Square being directly proportional of gas flow drag losses and flow velocity is so the loss of flow resistance also significantly reduces when the rotating speed of compressor improves.The aerodynamic loss of high speed rotating compressor has certain adverse effect to compressor efficiency, and the compressor gas power loss reduces, and the efficient of compressor also just obtains improving.Meanwhile, this design makes the steam outlet pipe of duplex cylinder compressor stock solution tube also become one by two, effectively reduces the cost of production of compressor.
The invention has the beneficial effects as follows, effectively reduce the inhalation resistance of the little float amount rotor duplex cylinder compressor of cylinder height, improve compressor efficiency, especially with R410A or CO
2For the ability of refrigeration agent is that effect in the float amount rotor type twin cylinder compressor below the 2HP is obvious.Pass through to reduce the cost of compressor stock solution tube in addition, thereby reduce compressor integral production cost.
The invention will be further described below in conjunction with drawings and Examples.
Description of drawings
Fig. 1 is conventional rotor type twin cylinder compressor sectional drawing.
Fig. 2 is the structural representation of the air-breathing upper cylinder in conventional rotor-type compressor radial suction hole.
Fig. 3 is the structural representation of the air-breathing lower cylinder in conventional rotor-type compressor radial suction hole.
Fig. 4 is the structural representation that conventional rotor type twin cylinder compressor does not have air-breathing function central diaphragm.
Fig. 5 is the structural representation with air-breathing function central diaphragm.
Fig. 6 is the schematic representation of the air-breathing upper cylinder of angular cut.
Fig. 7 is the schematic representation of the air-breathing lower cylinder of angular cut.
Fig. 8 is first embodiment's a rotor type twin cylinder compressor sectional drawing.
Among the figure on 1. nameplates, 2. rotors, 3. motor stators, 4. cylindrical shells, 5. eccentric shafts, 6. loam cakes 7. on 18. times outer covers of silencer cover 8. upper cylinders, 9. lower cylinder 10. springs, 11. slide plate 12. median septums, 13. upper rotor part 14. lower rotor parts, 15. screws 16. times silencer covers, 17. lower covers, 19. liquid storage cylinders, 20. air inlet pipe, 21. blast pipes 22. the air-breathing median septum axially extending bore 24. of outer cover 23. air-breathing median septum 23a. air-breathing median septum radial direction through hole 23b. have the air-breathing upper cylinder of angular cut 25. that axially two escape pipe 31. liquid storage cylinder list escape pipes 32. lubricating oil of semicolumn through hole 30. liquid storage cylinders are arranged on air-breathing angular cut 29. cylinders of the air-breathing lower cylinder of angular cut 26. single escape pipe liquid storage cylinder 27. cylinder radial suction through holes 28. cylinders
Embodiment
In the embodiment shown in fig. 8, with R410A or CO
2For the rotor type twin cylinder compressor (as shown in Figure 8) of refrigeration working medium is by a seal container, the middle formations such as motor that play the pump housing of compression and drive the pump housing.Whole compressor links to each other with the air-conditioning system miscellaneous part with outlet pipe (21) by suction tude (20), and single steam outlet pipe stock solution tube (26) plays a part air-breathing and gas-liquid separation.Shown in Figure 5 is a kind of structure that the central diaphragm of air-breathing function is arranged, and compares the axial hole (23b) that design has a radial direction through hole (23a) and connects at its end face and this radial direction through hole on it with conventional rotator type double-cylinder compressor central diaphragm shown in Figure 4.Fig. 6 is the structure through the air-breathing upper cylinder of angular cut (24) that a kind of and air-breathing central diaphragm cooperates, compare with the air-breathing upper cylinder in conventional rotor type twin cylinder compressor radial suction hole shown in Figure 2, there is not radial suction hole (27), and design has angular cut (28) on its lower end surface, and design has axial semicolumn through hole (29) and angular cut to connect near cylinder bore diameter one side at angular cut.Shown in Figure 7 be a kind of and air-breathing central diaphragm cooperate through the air-breathing lower cylinder of angular cut (25), compare with the air-breathing lower cylinder in conventional rotator type radial suction hole shown in Figure 3, there is not radial suction hole (27), design has angular cut (28) on its upper-end surface, and design has axial semicolumn through hole (29) and angular cut to connect near cylinder bore diameter one side at angular cut.When concrete the use, the radial direction through hole (23a) of air-breathing central diaphragm (23) is communicated with to play effect air-breathing outside seal container with single steam outlet pipe (31) of compressor stock solution tube, then the air-breathing upper cylinder of angular cut (24) and the air-breathing lower cylinder of angular cut (25) respectively by separately with air-breathing central diaphragm (23) end face on axial hole (23b) discharge compressor pump after two logical air-breathing angular cuts of upper and lower cylinder (28) suck low-pressure low-temperature refrigeration working mediums and boil down to High Temperature High Pressure refrigeration working medium mutually.
In the present embodiment, because the not restriction of machine discharge capacity by compression of air-breathing central diaphragm thickness, the diameter of the radial direction through hole of (23) (23a) can be made enough big by design requirement on the air-breathing central diaphragm, the air-breathing angular cut (28) of the lower cylinder (25) that upper cylinder (24) that the while angular cut is air-breathing and angular cut are air-breathing is not subjected to the restriction of cylinder height yet, also can leave angular cut, and leave the axial semicolumn through hole (29) that connects with the air-breathing angular cut of cylinder (28) with the air-breathing net sectional area of further raising cylinder near cylinder bore diameter one side at the air-breathing angular cut of cylinder (28) by demand.The rotor type twin cylinder compressor that adopts this invention and conventional rotor type twin cylinder compressor relatively, below design 2HP with R410A or CO
2During for the rotary double cylinder compressor of refrigeration agent, effectively reduce the compressor air suction resistance, improved the efficient of compressor.Experiment show adopt of the present invention with R410A be the efficient of 2HP rotor type twin cylinder DC speed regulation compressor of refrigeration agent of the present invention than not adopting be that the efficient of 2HP rotor type twin cylinder DC speed regulation compressor of refrigeration agent is high about 1% with R410A, separate unit saving cost 3 yuans.
Claims (3)
1. one kind through the air-breathing rotor type twin cylinder compressor of central diaphragm, seal container top is installed with the electric machine assembly with running shaft, the bottom is installed with the compressor pump that is being driven by the electric motor assembly running shaft, central diaphragm is separated into two active chambers with upper and lower cylinder in the compressor pump, it is characterized in that: central diaphragm has suction port, and suction port is communicated with the steam outlet pipe of compressor stock solution tube; The upper and lower cylinder that matches with central diaphragm all has the hole of cutting sth. askew that communicates with the central diaphragm suction port; Stock solution tube is single steam outlet pipe.
2. according to claim 1 through the air-breathing rotor type twin cylinder compressor of central diaphragm, it is characterized in that: the suction port on the central diaphragm is a radial direction through hole, and design has the axial hole that connects with radial direction through hole on its end face.
3. according to claim 1 through the air-breathing rotor type twin cylinder compressor of central diaphragm, it is characterized in that: the angular cut of upper cylinder on its lower end surface has the axial semicolumn through hole that connects with angular cut near cylinder bore diameter one side, and the lower cylinder angular cut on the end face thereon has the axial semicolumn through hole that connects with angular cut near cylinder bore diameter one side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200710003003 CN101012831A (en) | 2007-01-29 | 2007-01-29 | Rotor type twin cylinder compressor taking air-breathing through partition board |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200710003003 CN101012831A (en) | 2007-01-29 | 2007-01-29 | Rotor type twin cylinder compressor taking air-breathing through partition board |
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| Publication Number | Publication Date |
|---|---|
| CN101012831A true CN101012831A (en) | 2007-08-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200710003003 Pending CN101012831A (en) | 2007-01-29 | 2007-01-29 | Rotor type twin cylinder compressor taking air-breathing through partition board |
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Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2009062365A1 (en) * | 2007-11-17 | 2009-05-22 | Guang Dong Mei Zhi Refrigeration Equipment Co., Ltd | A suction device for capacity-controlled rotary compressor |
| CN101387298B (en) * | 2007-08-28 | 2011-03-23 | 东芝开利株式会社 | Double cylinders rotary compressor and freezing cycle device using the same |
| CN102472280A (en) * | 2009-08-06 | 2012-05-23 | 大金工业株式会社 | Compressor |
| CN102538322A (en) * | 2012-01-09 | 2012-07-04 | 西安庆安制冷设备股份有限公司 | Rotor type compressor and gas and liquid separator thereof |
| CN102644593A (en) * | 2011-02-16 | 2012-08-22 | 广东美芝制冷设备有限公司 | Double-cylinder rotary compressor and control method thereof |
| CN102644594A (en) * | 2011-02-16 | 2012-08-22 | 广东美芝制冷设备有限公司 | Double-cylinder type rotary compressor and control method for same |
| CN103821719A (en) * | 2014-02-10 | 2014-05-28 | 广东美芝制冷设备有限公司 | Volume control type rotary compressor and refrigeration circulating device with same |
| CN103850939A (en) * | 2012-11-30 | 2014-06-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and refrigeration system provided with same |
| CN106715913A (en) * | 2014-11-10 | 2017-05-24 | 东芝开利株式会社 | Rotating compressor and refrigeration cycle device |
| CN109058109A (en) * | 2018-10-10 | 2018-12-21 | 珠海凌达压缩机有限公司 | A kind of compressor and air conditioner |
| CN109209885A (en) * | 2018-09-06 | 2019-01-15 | 珠海凌达压缩机有限公司 | Compressor |
-
2007
- 2007-01-29 CN CN 200710003003 patent/CN101012831A/en active Pending
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101387298B (en) * | 2007-08-28 | 2011-03-23 | 东芝开利株式会社 | Double cylinders rotary compressor and freezing cycle device using the same |
| WO2009062365A1 (en) * | 2007-11-17 | 2009-05-22 | Guang Dong Mei Zhi Refrigeration Equipment Co., Ltd | A suction device for capacity-controlled rotary compressor |
| CN102472280B (en) * | 2009-08-06 | 2014-08-20 | 大金工业株式会社 | Compressor |
| CN102472280A (en) * | 2009-08-06 | 2012-05-23 | 大金工业株式会社 | Compressor |
| CN102644593A (en) * | 2011-02-16 | 2012-08-22 | 广东美芝制冷设备有限公司 | Double-cylinder rotary compressor and control method thereof |
| CN102644594A (en) * | 2011-02-16 | 2012-08-22 | 广东美芝制冷设备有限公司 | Double-cylinder type rotary compressor and control method for same |
| CN102538322A (en) * | 2012-01-09 | 2012-07-04 | 西安庆安制冷设备股份有限公司 | Rotor type compressor and gas and liquid separator thereof |
| CN102538322B (en) * | 2012-01-09 | 2014-06-04 | 西安庆安制冷设备股份有限公司 | Rotor type compressor and gas and liquid separator thereof |
| CN103850939A (en) * | 2012-11-30 | 2014-06-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and refrigeration system provided with same |
| CN103821719A (en) * | 2014-02-10 | 2014-05-28 | 广东美芝制冷设备有限公司 | Volume control type rotary compressor and refrigeration circulating device with same |
| CN106715913A (en) * | 2014-11-10 | 2017-05-24 | 东芝开利株式会社 | Rotating compressor and refrigeration cycle device |
| CN109209885A (en) * | 2018-09-06 | 2019-01-15 | 珠海凌达压缩机有限公司 | Compressor |
| CN109058109A (en) * | 2018-10-10 | 2018-12-21 | 珠海凌达压缩机有限公司 | A kind of compressor and air conditioner |
| CN109058109B (en) * | 2018-10-10 | 2024-02-27 | 珠海凌达压缩机有限公司 | Compressor and air conditioner |
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