CN101560982A - Annular balancing piston - Google Patents
Annular balancing piston Download PDFInfo
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- CN101560982A CN101560982A CNA2009100279752A CN200910027975A CN101560982A CN 101560982 A CN101560982 A CN 101560982A CN A2009100279752 A CNA2009100279752 A CN A2009100279752A CN 200910027975 A CN200910027975 A CN 200910027975A CN 101560982 A CN101560982 A CN 101560982A
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- piston
- piston ring
- annular groove
- annular
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Abstract
The invention relates to an annular balancing piston used in a bearing base at an exhaust end of an oil-jet screw compressor, an annular groove is formed on the outer circumference of the piston, a movable device in the annular groove is provided with a piston ring, and the outer diameter of the piston ring is larger than the outer diameter of the piston. As the annular groove is formed on the outer circumference of the piston and the movable device in the annular groove is provided with the piston ring, gap is existed between the annular groove and the piston ring; when in use, the piston ring and an inner cavity of the bearing base of a rotor are in close fit, the radial gap between the piston and the bearing base can be eliminated, pressure oil flows out through the gap between the annular groove and the piston ring, and the pressure in a pressure cavity of the bearing base is easy to ensure.
Description
(1) technical field
The present invention relates to a kind of annular balancing piston, be specially a kind of equalizing piston that is used in the fuel injection helical lobe compressor exhaust end bearing support.
(2) background technique
Fuel injection helical lobe compressor because of the structural feature of rotor helical-screw shape, in the process of engagement compression, axially can produce thrust at rotor when load operation.In order to reduce of the influence of this end thrust to bearing, improve the working life of bearing, generally in the exhaust end bearing support of compressor, add equalizing piston.
The equalizing piston structure of existing fuel injection helical lobe compressor is made up of the pressure oil cavity A and the low pressure bearing bore B on rotor shaft bearing 4, equalizing piston 3 and equalizing piston 3 both sides as shown in Figure 1.Among the figure, 1 is angular contact ball bearing, and 2 is roller bearing, and 5 is compressor drum.Form certain pressure when time among the pressure oil injection pressure oil pocket A, pressure oil flows into low pressure bearing bore B by the gap between equalizing piston 3 and the rotor shaft bearing 4 then.Owing between two chambeies of A, B certain pressure difference is arranged, has formed the equilibrant opposite, thereby reduced the stressed of compressor shaft axial thrust bearing, the life-span of having improved thrust-bearing with the rotor axial thrust direction.
There is following problem in above-mentioned equalizing piston structure:
1, the radial clearance between equalizing piston 3 and the rotor shaft bearing 4 is bigger, and a large amount of pressure oil runs off by this gap, and it is not high that the pressure reduction on equalizing piston 3 both sides is carried, and equilibrant is little.
2, the manufacturing tolerances of the cylindrical of the endoporus of rotor shaft bearing 4 and equalizing piston 3 is bigger to the area effect of the annular that forms between them, makes the oil mass that flows through bearing change greatly, and is difficult to control.
(3) summary of the invention
The present invention is directed to the problems referred to above, a kind of annular balancing piston is provided, this piston can increase its equilibrant after being used for the exhaust end bearing support of fuel injection helical lobe compressor.
Technological scheme of the present invention is such: a kind of annular balancing piston is characterized in that: the excircle of described piston is provided with annular groove, and head has piston ring in the annular groove, and the external diameter of piston ring is greater than the external diameter of piston.
The further technological scheme of the present invention is: the piston external diameter of described annular groove both sides is unequal, is stepped shape; Described piston ring is provided with opening; The plane of described piston ring both sides is provided with the contract groove; The position of the contract groove of described piston ring both sides is corresponding; The quantity of the contract groove of described each side of piston ring is four; Described contract groove is uniform on the plane of piston ring both sides; The cross section of described contract groove is a V-arrangement.
The outer peripheral surface of the present invention's piston is provided with annular groove, head has piston ring in the annular groove, therefore there is the gap between annular groove and the piston ring, drive fit between piston ring and rotor shaft bearing inner chamber during use, can eliminate the radial clearance between piston and the bearing support, pressure oil flows out by the gap between annular groove and the piston ring, and the pressure in the bearing support pressure chamber guarantees that easily equilibrant is bigger than equilibrium structure of the prior art.
The present invention's piston ring is provided with contract groove and opening, and the size of contract groove and opening is control easily all, therefore controls easily by the oil mass of bearing.
(4) description of drawings
Fig. 1 is the schematic representation of existing equalizing piston structure;
Fig. 2 is for using the partial structurtes sectional view of compressor of the present invention;
Fig. 3 is the sectional view of the piston among the present invention;
Fig. 4 is the plan view of the piston ring among the present invention;
Fig. 5 is the C-C sectional view among Fig. 4;
Fig. 6 is the D place enlarged view among Fig. 5.
(5) embodiment
See Fig. 2, be to use the partial structurtes of a kind of fuel injection helical lobe compressor of the present invention.Compressor drum 5 is assemblied on the rotor shaft bearing 4, is equipped with the roller bearing 2 of bearing radial force and the angular contact ball bearing 1 of bearing axial pushing force on the spindle nose of compressor drum 5 side by side.On the axle body of the compressor drum 5 between roller bearing 2 and rotor shaft bearing 4 sidewalls, be equipped with equalizing piston 3.Equalizing piston 3 is divided into two chambeies with the space between roller bearing 2 and rotor shaft bearing 4 sidewalls, is respectively pressure oil cavity A and low pressure bearing bore B.
The present invention is the improvement to the structure of above-mentioned equalizing piston 3.The excircle of piston 3 is provided with annular groove 8, and head has piston ring 6 in the annular groove 8, that is to say between annular groove 8 and the piston ring 6 to have the gap between piston ring 6 and the piston 3 slide relative is arranged.The external diameter of piston ring 6 is greater than the external diameter of piston 3, and during work, piston ring 6 is fitted with rotor shaft bearing 4 inner chambers under the effect of elastic force and frictional force and do not changeed.Piston ring 6 has been filled the radial clearance between piston 3 and the bearing support 4, and pressure oil flows out by the gap between annular groove 8 and the piston ring 6, and the pressure in the bearing support pressure chamber A guarantees that easily equilibrant is bigger than equilibrium structure of the prior art.
As shown in Figure 3, piston 3 external diameters of annular groove 8 both sides can be arranged to unequal, are stepped shape.During installation, big external diameter 7 is close to low pressure bearing bore B in low voltage side, can increase the area of contact of piston 3 and piston ring 6, reduces the specific contact pressure of piston 3 and piston ring 6; Little external diameter 9 is in the high pressure side, and contiguous pressure oil cavity A helps the installation of piston ring 6, and piston ring 6 is as long as very little amount of deformation just can be enclosed within on the piston 3.
As Fig. 4～shown in Figure 6, piston ring 6 is provided with opening 11; The corresponding section, position is provided with contract groove 10 on the plane of piston ring 6 both sides.Contract groove 10 is uniform on the plane of piston ring 6 both sides; The quantity of the contract groove 10 of each side is four or other quantity; The sectional shape of contract groove 10 can be circular arc, U-shaped, but is preferably V-arrangement.Owing to have V-arrangement contract groove 10 on piston ring 6, the contract oil groove of similar plain thrust bearing makes between piston 3 and the piston ring 6 and forms oil film, and the pressure oil in the pressure oil cavity A can only flow to low pressure bearing bore B by contract groove 10 on the piston ring 6 and opening 11.Therefore the size of contract groove 10 and opening 11 is control easily all, and the oil mass that enters low pressure bearing bore B from pressure oil cavity A is controlled easily.
Working principle of the present invention is: the pressure difference of pressure oil cavity A and low pressure bearing bore B acts on piston 3 and the piston ring 6, the direction of the axial force F 2 that the direction of the axial force F 1 that forms and rotor 5 are suffered is opposite, and axial force F 1 has played the effect of balance portion axial force F 2.
Claims (8)
1, a kind of annular balancing piston is characterized in that: the excircle of described piston is provided with annular groove, and head has piston ring in the annular groove, and the external diameter of piston ring is greater than the external diameter of piston.
2, annular balancing piston according to claim 1 is characterized in that: the piston external diameter of described annular groove both sides is unequal, is stepped shape.
3, annular balancing piston according to claim 1 is characterized in that: described piston ring is provided with opening.
4, annular balancing piston according to claim 1 is characterized in that: the plane of described piston ring both sides is provided with the contract groove.
5, annular balancing piston according to claim 4 is characterized in that: the position of the contract groove of described piston ring both sides is corresponding.
6, annular balancing piston according to claim 5 is characterized in that: the quantity of the contract groove of described each side of piston ring is four.
7, annular balancing piston according to claim 4 is characterized in that: described contract groove is uniform on the plane of piston ring both sides.
8, annular balancing piston according to claim 4 is characterized in that: the cross section of described contract groove is a V-arrangement.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200910027975 CN101560982B (en) | 2009-05-12 | 2009-05-12 | Annular balancing piston |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200910027975 CN101560982B (en) | 2009-05-12 | 2009-05-12 | Annular balancing piston |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101560982A true CN101560982A (en) | 2009-10-21 |
| CN101560982B CN101560982B (en) | 2012-12-19 |
Family
ID=41219917
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200910027975 Active CN101560982B (en) | 2009-05-12 | 2009-05-12 | Annular balancing piston |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101560982B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103334927A (en) * | 2013-07-11 | 2013-10-02 | 烟台冰轮股份有限公司 | Semi-closed oil injection screw supercharger |
| CN108223379A (en) * | 2016-12-12 | 2018-06-29 | 斯凯孚公司 | The bearing group of studdle formula compressor drum and the assembly method of compressor |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1075901B (en) * | 1957-05-09 | 1960-02-18 | Hydraulik Gmbh | Thrust bearing with load compensation for large thrust forces with at least two axial roller bearings |
| US4551072A (en) * | 1984-02-15 | 1985-11-05 | Hibar Systems Limited | Fluid pressure operated actuator |
| AU634731B2 (en) * | 1988-12-02 | 1993-03-04 | Sanden Corporation | Piston ring having a function which is for facilitating supply of lubricating oil into an annular groove of a piston |
| CN2714885Y (en) * | 2004-06-25 | 2005-08-03 | 无锡压缩机股份有限公司 | Bearing soft pretightening and anti-rotating structure |
| CN2918861Y (en) * | 2005-12-31 | 2007-07-04 | 瓦房店轴承集团有限责任公司 | Traveling wheel seal structure |
| JP2008255796A (en) * | 2007-03-30 | 2008-10-23 | Anest Iwata Corp | Shaft seal device of oil-free rotary compressor |
| CN100516534C (en) * | 2007-11-27 | 2009-07-22 | 无锡压缩机股份有限公司 | Dry helical lobe compressor host rotor spindle sealing structure |
| CN101158403B (en) * | 2007-11-27 | 2011-01-12 | 无锡压缩机股份有限公司 | Step-up gear box shaft seal |
| CN201448241U (en) * | 2009-05-12 | 2010-05-05 | 无锡压缩机股份有限公司 | Annular balance piston |
-
2009
- 2009-05-12 CN CN 200910027975 patent/CN101560982B/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103334927A (en) * | 2013-07-11 | 2013-10-02 | 烟台冰轮股份有限公司 | Semi-closed oil injection screw supercharger |
| CN108223379A (en) * | 2016-12-12 | 2018-06-29 | 斯凯孚公司 | The bearing group of studdle formula compressor drum and the assembly method of compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101560982B (en) | 2012-12-19 |
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| C10 | Entry into substantive examination | ||
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| C14 | Grant of patent or utility model | ||
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Address after: 214145 No. 199, xixie Road, Hongshan street, Xinwu District, Wuxi City, Jiangsu Province Patentee after: Shengang Wuxi Compressor Co.,Ltd. Address before: 214145 Jiangsu city of Wuxi Province New Photoelectric Industrial Park Patentee before: WUXI COMPRESSOR Co.,Ltd. |
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| CP03 | Change of name, title or address |