CN2813935Y - Crankshaft of high-rigid double-cylinder rotor type compressor - Google Patents
Crankshaft of high-rigid double-cylinder rotor type compressor Download PDFInfo
- Publication number
- CN2813935Y CN2813935Y CN 200520106251 CN200520106251U CN2813935Y CN 2813935 Y CN2813935 Y CN 2813935Y CN 200520106251 CN200520106251 CN 200520106251 CN 200520106251 U CN200520106251 U CN 200520106251U CN 2813935 Y CN2813935 Y CN 2813935Y
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- China
- Prior art keywords
- shaft
- eccentric shaft
- coupling shaft
- circular arc
- bent axle
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Abstract
The utility model provides a crankshaft of a high-rigidity double-cylinder rotor type compressor. The crankshaft comprises a main shaft journal 1a, a subsidiary shaft journal 1e, an upper eccentric shaft 1b, a lower eccentric shaft 1d and a connecting shaft 1c. The utility model is characterized in that the pattern of the cross section of the connecting shaft 1c is composed of two circular arcs of which the cross section sizes increase gradually from the H surface connected to the upper eccentric shaft 1b or the lower eccentric shaft 1d towards left or right, wherein one circular arc is a circular arc with the same radius as that of the connecting shaft 1c and the other circular arc is a circular arc with the radius larger than that of the connecting shaft 1c. The maximum diameter of the connecting shaft can be equal to the diameter of the eccentric shaft. The rigidity of the connecting shaft of the crankshaft is enhanced obviously by the utility model adopting the structure. Consequently, when the crankshaft bears stressed action, the bending deformation of the connecting shaft can be reduced. Meanwhile, the utility model simplifies the processing technology of the crankshaft.
Description
Affiliated technical field
The utility model relates to a kind of bent axle of twin cylinder rotary compressor, and it can reduce the distortion of twin cylinder rotary compressor bent axle in operation process.
Background technique
Compressor its bent axle in operation process is subjected to the effect of high pressure air muscle power, inertial force and electromagnetic force usually, particularly the compression chamber of compressor is in exhaust moment, bent axle is subjected to the effect of very big gas force, the coupling shaft that connects between two eccentric shafts on the bent axle will occur bending and deformation, cause original end face to be in the rolling piston end slope of the high speed rotating of horizontal plane, the metal (upper and the intermediate clapboard of the edge of rolling piston and pump housing part produce wearing and tearing, and compressor reliability reduces.So, how to improve the rigidity of the coupling shaft between two eccentric shafts on the bent axle, reduce its bending deflection, just become a very important problem that improves the two-cylinder rotary compressor reliability.
In 00249769 Chinese patent, what disclose a kind of twin cylinder rotary compressor has a be rigidly connected bent axle of axle of height, is characterized in that the bent axle shape of cross section of coupling shaft is the horizontal diameter of axle greater than the eye shape or the ellipse of the vertical diameter of axle.Though this patented technology has improved the rigidity of bent axle coupling shaft, reduced the bending deflection of making the time spent coupling shaft that bent axle is subjected to very big gas force, but the shape of the coupling shaft that the utility model proposes part, its rigidity is better than 00249769 patent, and processing is more simple.
Summary of the invention
The utility model is a kind of bent axle of high rigidity twin cylinder rotary compressor, as shown in Figure 1.This bent axle comprises: be located in main journal, countershaft neck on the metal (upper of the pump housing, respectively and the eccentric shaft up and down of described main journal, the adjacent layout of countershaft neck and be bearing on the pump housing intermediate clapboard, the coupling shaft between two eccentric shafts.The technological scheme that the utility model adopted as shown in Figure 2, be characterized in, the cross section figure of coupling shaft 1c is risen by the H face that is connected with eccentric shaft 1b or 1d, to the left or to the right, two-part circular arc that cross sectional area constantly increases is formed, wherein a part is and the identical circular arc of coupling shaft 1c radius, and another part is the circular arc greater than coupling shaft 1c radius.When its cross section changed to the Y cross section, its cross sectional area was maximum, and figure to become with coupling shaft 1c radius be the circle of radius, the maximum diameter of this coupling shaft can equal the diameter of eccentric shaft.
The beneficial effects of the utility model are, the rigidity of coupling shaft significantly improves on the bent axle, thereby reduced bent axle and be subjected to the bending deflection that very big gas force is made the time spent coupling shaft, the wearing and tearing that produce between the metal (upper of the edge of rolling piston and pump housing part and the intermediate clapboard have been avoided, improve compressor reliability, simplified the processing technology of bent axle simultaneously.
Below in conjunction with drawings and Examples the utility model is further specified.
Description of drawings
Fig. 1 is that bent axle is used for the concrete structural representation of implementing.
Fig. 2 is the parts drawing of the utility model bent axle.
Fig. 3 is the left view of Fig. 2
Among the figure: 6 times cylinder cap 1a of 4 times rolling pistons of rolling piston, 5 pump housing intermediate clapboards main journal 1e countershaft neck 1b goes up eccentric shaft 1c coupling shaft under the eccentric shaft 1d on 1 bent axle, 2 upper cylinder covers 3
Embodiment
As Fig. 1, bent axle 1 of the present utility model comprises: be located in up and down main journal 1a and the countershaft neck 1e on the cylinder cap 2 and 6 of the pump housing respectively; Respectively with the upper and lower eccentric shaft 1b and the 1d on pump housing scroll-up/down piston 3 and 4 of being located in of major and minor axle journal 1a and the adjacent layout of 1e; With upper and lower eccentric shaft 1b link to each other with 1d and and be bearing in the coupling shaft 1c that pump housing intermediate clapboard 5 cooperates.As shown in Figure 2, be characterized in, the cross section figure of coupling shaft 1c is risen by the H face that is connected with last eccentric shaft 1b or following eccentric shaft 1d, to the left or to the right, two-part circular arc that cross sectional area constantly increases is formed, wherein a part is and the identical circular arc of coupling shaft 1c radius, and another part is the circular arc greater than coupling shaft 1c radius.When its cross section changes to the Y cross section, its cross sectional area is maximum, and it is the circle of radius that figure becomes with coupling shaft 1c radius, and the maximum diameter of this coupling shaft 1c can equal the diameter (it is identical with the diameter of following eccentric shaft 1d to go up eccentric shaft 1b) of eccentric shaft 1b or following eccentric shaft 1d.
The Changing Pattern of the vertical diameter of axle dimension D of the cross section figure of coupling shaft 1c is:
D＝φ-(B-L)*tgα
φ in the formula: the diameter of coupling shaft 1c
B: with eccentric shaft 1b or 1d axis is rotating center, and during at a certain angle lathe tool turning, the intersection point of blade and coupling shaft 1c periphery bus is apart from the ultimate range (being the distance of adjacent Y face to the H face) of H face.This ultimate range appeared on the longitudinal section of coupling shaft.
L: on the longitudinal section of crossing coupling shaft 1c, any any distance on the G line segment that lathe tool turning at a certain angle forms to the H face.
α: the angle of working surface G and Q and last eccentric shaft 1b axis.
Identical when the actual processing of bent axle of the present utility model is circular with cross section, be used profile cutter difference, be that the actual processing of oval-shaped bent axle is compared with cross section, the operation process is simplified.The bent axle of this structure, the maximum diameter φ of its coupling shaft can reach and equal its eccentric shaft diameter phi 1, have improved the local stiffness of the bent axle of twin cylinder rotary compressor, have reduced the bending deflection degree of coupling shaft.When gas load acts on upper and lower eccentric wheel 1b and 1d position, because coupling shaft 1c rigidity is bigger, counter-bending deformation ability improves, therefore, tilt to reduce greatly at the rolling piston 3 of horizontal plane rotation and 4 plane of rotation, thereby reduce the cylinder cap up and down 2,6 of rolling piston 3 and 4 edges and pump housing part and the wearing and tearing of 5 of intermediate plates, avoided the inordinate wear of pump housing part, improved the reliability of the compressor that uses this model utility bent axle.
The claimant is with bent axle of the present utility model and can satisfy the maximum circle of having of same intermediate clapboard matching requirements, maximum oval, the bent axle of maximum eye shape cross section has carried out test relatively, and bent axle of the present utility model is used for two-cylinder rotary compressor has carried out the real-world operation test, the result shows, circular with the maximum that the same intermediate clapboard of assembling should have, maximum oval, the bent axle of maximum eye shape cross section is compared, the be hit ability of power of coupling shaft position strengthens, the performance of counter-bending distortion is obviously improved, and it is circular that the rolling piston end wear is better than adopting cross section, the bent axle of ellipse and eye shape.
Claims (3)
1. the bent axle of a high rigidity twin cylinder rotary compressor, comprise: main journal (1a), countershaft neck (1e), last eccentric shaft (1b), following eccentric shaft (1d) and coupling shaft (1c), it is characterized in that: the cross section figure of coupling shaft (1c) is risen by the H face that is connected with last eccentric shaft (1b) or following eccentric shaft (1d), to the left or to the right, two-part circular arc that cross sectional area constantly increases is formed, wherein a part is and the identical circular arc of coupling shaft (1c) radius, and another part is the circular arc greater than coupling shaft (1c) radius.
2. the bent axle of high rigidity twin cylinder rotary compressor according to claim 1 is characterized in that: the Changing Pattern of the vertical diameter of axle dimension D of the cross section figure of described coupling shaft (1c) is:
D＝φ-(B-L)*tgα
φ in the formula: the diameter of coupling shaft (1c)
B: above eccentric shaft (1b) or down eccentric shaft (1d) axis be rotating center, during at a certain angle lathe tool turning, the intersection point of blade and coupling shaft (1c) periphery bus is apart from the ultimate range of H face.
L: on the longitudinal section of crossing coupling shaft (1c), any any distance on the G line segment that lathe tool turning at a certain angle forms to the H face.
α: the angle of working surface G and Q and last eccentric shaft (1b) axis.
3. the bent axle of high rigidity twin cylinder rotary compressor according to claim 1 is characterized in that: the maximum diameter of described coupling shaft (1c) equals the diameter of eccentric shaft (1b) or following eccentric shaft (1d).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520106251 CN2813935Y (en) | 2005-08-26 | 2005-08-26 | Crankshaft of high-rigid double-cylinder rotor type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520106251 CN2813935Y (en) | 2005-08-26 | 2005-08-26 | Crankshaft of high-rigid double-cylinder rotor type compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2813935Y true CN2813935Y (en) | 2006-09-06 |
Family
ID=36949023
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200520106251 Expired - Lifetime CN2813935Y (en) | 2005-08-26 | 2005-08-26 | Crankshaft of high-rigid double-cylinder rotor type compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2813935Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101688535B (en) * | 2007-08-28 | 2013-03-13 | 东芝开利株式会社 | Multicylinder rotary type compressor, and refrigerating cycle apparatus |
| CN104302924A (en) * | 2012-07-31 | 2015-01-21 | 三菱重工业株式会社 | Rotary fluid machine and method for assembling same |
| CN106286570A (en) * | 2016-09-27 | 2017-01-04 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of bent axle and rotor-type compressor |
-
2005
- 2005-08-26 CN CN 200520106251 patent/CN2813935Y/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101688535B (en) * | 2007-08-28 | 2013-03-13 | 东芝开利株式会社 | Multicylinder rotary type compressor, and refrigerating cycle apparatus |
| CN104302924A (en) * | 2012-07-31 | 2015-01-21 | 三菱重工业株式会社 | Rotary fluid machine and method for assembling same |
| CN106286570A (en) * | 2016-09-27 | 2017-01-04 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of bent axle and rotor-type compressor |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term |
Expiration termination date: 20150826 Granted publication date: 20060906 |
|
| EXPY | Termination of patent right or utility model |