CN1766340A - Eccentric bushing brake for vortex compressor - Google Patents
Eccentric bushing brake for vortex compressor Download PDFInfo
- Publication number
- CN1766340A CN1766340A CN 200410072394 CN200410072394A CN1766340A CN 1766340 A CN1766340 A CN 1766340A CN 200410072394 CN200410072394 CN 200410072394 CN 200410072394 A CN200410072394 A CN 200410072394A CN 1766340 A CN1766340 A CN 1766340A
- Authority
- CN
- China
- Prior art keywords
- eccentric bush
- break
- eccentric
- scroll compressor
- joining hole
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Landscapes
- Rotary Pumps (AREA)
Abstract
The invention discloses an eccentric liner stop device of vortex-type compressor, which consists of cylinder-shape hollow stopper host and incision part at the vertical direction of stopper host. When the eccentric force of rotary vortex disk is less than the gas pressure in the compression chamber and the eccentric liner rotates toward radius direction, it will apply the elastic force to the eccentric liner of inversion direction, which shortens the normal position restoring time of eccentric liner. Hence, the device reduces the coolant leakage of rotary eccentric liner, which improves the compression efficiency and property and reduces the preparing cost.
Description
Technical field
The present invention relates to the eccentric bush of scroll compressor, particularly shorten the normal position Recovery time of eccentric bush, thus the eccentric bushing brake of the scroll compressor of the leakage of the cold media air that causes by the rotation of eccentric bush of early cut-off about rotary compressor.
Background technique
Generally, scroll compressor as shown in Figure 1, the mainframe 2 and the auxiliary framework 3 that comprise the inboard upper and lower part setting of shell 1, between mainframe 2 and auxiliary framework 3, be pressed into the inside of shell 1 by stator 4, the power supply that the inside of stator 4 is provided with by input comes rotor rotated 5, the central part of rotor 5 inserts to be fixed with the vertical crankshaft 6 of 5 rotations of rotor and constitutes, and the upper and lower part of crankshaft 6 is rotatably being supported by mainframe 2 and auxiliary framework 3.
And, the upper-end surface of mainframe 2 is provided with lower side and crankshaft 6 is formed with the rotation scrollwork 7a of involute shape in conjunction with, upper side rotation whirlpool dish 7, the upper side of rotation whirlpool dish 7 is fixed on the inside of shell 1 by the fixed eddy plate 8 that has and rotate the fixed scroll 8a of scrollwork 7a correspondence, and dish 7 rotations by crankshaft 6 of rotation whirlpool are rotated motion and compress and flow into the cold media air that rotates pressing chamber 22 inside that form between scrollwork 7a and the fixed scroll 8a.
In addition, the combination of crankshaft 6 and rotation whirlpool dish 7 is, mind-set in the upper-end surface of crankshaft 6 be separated by institute set a distance position above the outstanding crank pin 10 that forms be inserted among the outstanding wheel hub 7b that forms of lower side central part of rotation whirlpool dish 7 and constitute, force to be pressed into bearing 11 in the inside of wheel hub 7b, the outside of crank pin 10 rotatably is combined with eccentric bush 12 in several angle.
In addition, the anti-locking mechanism cross guide ring of rotation is set between mainframe 2 and the auxiliary framework 3, crankshaft 6 inner upper and lower perforations are formed with to oil circuit 6a, and rotor 5 upper and lower is formed with the rotation imbalance that top counterweight 13 and bottom counterweight 14 prevent the crankshaft 6 that caused by crank pin 10 separately.
Here, undeclared symbol 15 and 16 is suction pipe and discharge tube, and 17 and 18 is to discharge port and discharge the chamber, the 1st, and check valve, the 20th, oil, the 21st, oily propeller cavitation.
The scroll compressor of Gou Chenging is imported power supply as mentioned above, and rotor 5 is in stator 4 inner rotations, and crankshaft is by above-mentioned rotor 5 rotations, and the rim, rotation whirlpool that is combined in crank pin 10 crankshaft 6 centers and rotates the turning radius of coiling between 7 centers in the whirlpool and is rotated motion.
In addition, be formed between rotation scrollwork 7a and the fixed scroll 8a pressing chamber 22 by rotation whirlpool dish 7 continue rotatablely move, reduce volume and further compress the cold media air that sucks, the cold media air of compressed like this high pressure is discharged to discharge chamber 18 by discharging port 17, discharges the cold media air of 18 inside, chamber and discharges to the outside by discharge tube 16 again.
In addition, no matter the time compression failure, the radius variable formula scroll compressors that rotation whirlpool dish 7 is rotated to radial direction of not risen for each scrollwork 7a, 8a that the variation that scroll compressor is divided into rotation whirlpool dish 7 contractive conditions again is rotated along same track that the fixation radius formula scroll compressor that moves and liquid coolant and oil or foreign substances flow into that pressing chamber 22 makes that pressure in the pressing chamber rises all the time improperly.
For the turning radius of variable rotation whirlpool dish 7, as above be combined with eccentric bush 12 on the crank pin 10, eccentric bush 12 usefulness realize sealing function to pressing chamber 22 together according to the centrifugal force of the rotation whirlpool dish 7 of offset between the center of the center of crank pin 10 and eccentric bush 12 in the radius variable formula scroll compressor.
Fig. 2 is the exploded perspective view of the eccentric lining structure of Fig. 1.
Keep the state of being separated by on the normal position of the eccentric bush 12 of such break 23 shown in Fig. 3 a from break hook face 10a, eccentric bush 12 when radial direction rotates shown in Fig. 3 b break 23 and eccentric bush 12 rotate together, and be connected on the break hook face 10a, so can limit the rotating amount of eccentric bush 12.
And, when rising except the pressure of eccentric bush 12 in pressing chamber improperly, the centrifugal force of rotation whirlpool dish 7 is than the little compressor start initial stage of gas force of compression chamber interior, shown in Fig. 3 b, also to the radial direction rotation, arrive the time marquis that centrifugal force is bigger than gas force, compressor normally moves, eccentric bush 12 is kept its rotational position, before eccentric bush 12 returns to the normal position, continue to leak the cold media air of pressing chamber inside by the gap between scrollwork 7a, the 8a.
Therefore, it is short more that eccentric bush 12 returns to the entopic time from rotational position, can improve the compression efficiency and the performance of scroll compressor more.
But, scroll compressor in the past is only when the normal operation of the centrifugal force that rotatablely moves that continues that is coiled 7 by the rotation whirlpool compressor bigger than gas pressure effect, could return to the normal position to the eccentric bush 12 of compressor start initial stage rotation, so need the long time and the leakage of lasting cold media air arranged in its time, cause the compression efficiency that reduces recompression and the performance of machine.
Summary of the invention
In order to solve the shortcoming of above-mentioned prior art, the eccentric bushing brake that the purpose of this invention is to provide scroll compressor, the centrifugal force that coils when the rotation whirlpool is littler than the gas pressure of compression chamber interior, when so eccentric bush rotates to radial direction, elastic force acts on the eccentric bush to its opposite direction, so shorten the normal position Recovery time of eccentric bush, thus the leakage of the cold media air that causes by the rotation of eccentric bush of early cut-off.
Another object of the present invention is to provide the structure of elastic force of the eccentric bush of rotational position more to oversimplify.
Another object of the present invention is to break that circular elastic structure forms and prevent its rotation by the rotary pressure of eccentric bush.
In order to achieve the above object, the technical solution used in the present invention provides a kind of eccentric bush braking device of scroll compressor, in scroll compressor, rotatably be combined with crankpin on the crankpin joining hole of eccentric bush, on the break joining hole of eccentric bush, be inserted with break, and when eccentric bush rotates the break contact of the rotating amount of restriction eccentric bush on the break hook face that a side of crankpin is provided with, wherein: in break, be provided with according to the rotation of described eccentric bush and compress and its device that recovers to the normal position direction of resilient support.
The device that described resilient support eccentric bush recovers comprises the cut that the cylindrical body with hollow forms the break main body and forms to a side Vertical direction of described break main body.
Described break main body is fixed on the inner side surface of eccentric bush.
Break joining hole inner side surface bottom at eccentric bush is provided with fixed projection, is provided with the fixed groove that inserts to lower side from the top of fixed lobe in the break lower body part.
The break joining hole inner side surface of described eccentric bush is provided with fixed projection, is inserted into the cut of break.
Effect of the present invention be littler when the centrifugal force of rotation whirlpool dish than the gas pressure of compression chamber interior, when eccentric bush rotates to radial direction, apply elastic force to its opposite direction to eccentric bush, shortened the entopic time of returning to of eccentric bush, reduce the leakage that eccentric bush rotates the refrigerant that brings thus, improved the performance of compression efficiency and compressor.
The present invention has so elastic structure, so relax the impact that takes place when eccentric bush rotates, the characteristics of the institutional damage that prevents compressor is in advance arranged thus.
The present invention provides the device of elastic force to be provided with simply for the eccentric bush of rotational position, so can reduce operation and manufacture cost again.
The present invention is at compressor start initial stage during the rotating eccentricity lining, when the break of the present invention that constitutes with round elastic structure is provided with, do not carried out rotation by its rotary pressure, have by prevent in advance by break from then the effect of the break spring function that causes forfeiture.
Description of drawings
Fig. 1 is the sectional arrangement drawing of general scroll compressor structure;
Fig. 2 is the exploded perspective view of the eccentric lining structure of Fig. 1;
Fig. 3 a is the entopic flat sectional drawing of Fig. 2 eccentric bush;
Fig. 3 b is the flat sectional drawing of Fig. 2 eccentric bush rotational position;
Fig. 4 is the exploded perspective view of the eccentric bush of one embodiment of the invention;
Fig. 5 a is the entopic flat sectional drawing of Fig. 4 eccentric bush;
Fig. 5 b is the section plan of Fig. 4 eccentric bush rotational position;
Fig. 6 is the exploded perspective view of the break of another embodiment of the present invention;
Fig. 7 is the assembled state flat sectional drawing of another embodiment of the present invention.
Among the figure:
6: crankshaft 10: crank pin
10a: break hook face 12: eccentric bush
12a: break joining hole 12b: crank pin joining hole
230: break main body 231: cut
232: fixed projection 233: fixed groove
Embodiment
Below, describe structure of the present invention in detail with reference to drawings and Examples.
Fig. 4 is the exploded perspective view of the eccentric bush of one embodiment of the invention.
Generally, eccentric bush 12 is provided with crank pin joining hole 12b and break joining hole 12a and rotatably is combined with the crank pin 10 that is arranged on crankshaft 6 upper-end surfaces on crank pin joining hole 12b, one upper lateral part of crank pin 10 is formed with the break hook face 10a of longitudinal plane form, and when inserting break 23 coming rotating eccentricity lining 12 on the break joining hole 12a of eccentric bush 12, break 23 contacts limit the rotating amount of eccentric bush 12 at break hook face 10a.
In the eccentric bush braking device of scroll compressor, when the present invention is provided with rotating eccentricity lining 12, be compressed and to above-mentioned eccentric bush 12 means of its opposite direction resilient support, and be subjected to centrifugal force and elastic force simultaneously by the eccentric bush 12 of this elastic force means rotational position, can make it return to the entopic characteristics of eccentric bush 12 in advance.
Compressing also round about during eccentric bush 12 rotations, the means of resilient support are, the break 23 that circumference type in the past forms is deformed into elastic structure, break 23 is the break main bodys 230 that are made of the cylindrical body with hollow, the cut 231 that is provided with to a side Vertical direction of break main body 230 promptly constitutes to the leaf spring that a side has a circular section form of opening portion.
Embodiment is not limited to this, so long as during rotating eccentricity lining 12, is compressed and eccentric bush 12 just passable to normal position direction resilient support.Consider structure, embodiments of the invention preferably according to the deformation limit of the eccentric bush 12 that comprises break 23.
When particularly compressor start initial stage eccentric bush 12 rotates rapidly, avoid break 23 to bump the impact of the eccentric bush 12 that takes place at break hook face 10a, more help preventing the institutional damage of compressor.
Fig. 5 a is the entopic flat sectional drawing of Fig. 4 eccentric bush.
The initial start stage of the compressor that the centrifugal force of rotation whirlpool dish is littler than the gas pressure of compression chamber interior, eccentric bush 12 is shifted the illustrated rotational position of Fig. 5 b onto from the illustrated normal position of Fig. 5 a, eccentric bush 12 rotation and compression brake main bodys 230, at this moment compression brake main body 230 is compressed and again eccentric bush 12 resilient support round about, so eccentric bush 12 is subjected to centrifugal force and elastic force simultaneously.
Thereupon, increase eccentric bush 12 is returned to entopic power from rotational position, and eccentric bush 12 returned to the normal position in advance, and can be breaking at the leakage that continues the refrigerant that carries out during eccentric bush 12 rotations thus in early days and come, further improve compression efficiency and performance.
In addition and the eccentric bush 12 break main body 230 of rotating together when break hook face 10a conflict, relax it by the elastic structure of break main body 230 and impact, so the advantage of the institutional damage that prevents compressor is in advance arranged.
Fig. 6 is the stereogram of breakaway detents from the eccentric bush.
The upper and lower as described above perforation of this eccentric bush 12 is provided with crank pin joining hole 12b, the side continuous phase earthing of crank pin joining hole 12b is provided with break joining hole 12a, break joining hole 12a is inserted with the break main body 230 of one embodiment of the invention, and the elastic structure that the cylinder type of break main body 230 usefulness hollows forms, also a side Vertical direction is formed with cut 231 constitutes.
As mentioned above, break main body 230 usefulness cylindrical bodys form, the pressure that is subjected to during rotating eccentricity lining 12, institute's amount of holding of carrying out rotation in break joining hole 12a inside is many, the cut 231 of break main body 230 is rotated to sense of rotation thus, and be positioned under the impossible state of compression the forfeiture spring function.
So, the present invention prevents to occur as stating problem in advance, be provided with the means that break main body 230 are fixed to break joining hole 12a inside for this reason, fixing means is to form fixed projection 232 with break joining hole 12a inner side surface bottom, and the fixed groove 233 that the cut 231 rear lower portion sides of break main body 230 form the lower opening type constitutes.
Such fixed projection 232 and fixed groove 233 are arranged on the lower side of break joining hole 12a and break main body 230 separately, are because break main body 230 is inserted to the bottom from the break joining hole 12a top of eccentric bush 12.
Fig. 7 is the assembled state flat sectional drawing of Fig. 6.
As shown in the figure, the break joining hole 12a of eccentric bush 12 goes up and inserts break main body 230, fixed projection 232 combinations of the fixed groove 233 of break main body 230 and break joining hole 12a at this moment among the present invention.So break main body 230 is because the combination of fixed groove 233 and fixed projection 232, eccentric bush 12 rotations come under the applied pressure can not rotation, and such fixed structure also is not limited to this, so long as can realize that its fixed function is just passable.
That is, also can be set to the not shown cut 231 that is inserted into break main body 230 of break joining hole 12a inner side surface formation fixed projection of eccentric bush 12.
Claims (5)
1, a kind of eccentric bush braking device of scroll compressor, in scroll compressor, rotatably be combined with crankpin on the crankpin joining hole of eccentric bush, on the break joining hole of eccentric bush, be inserted with break, and the break contact of the rotating amount of restriction eccentric bush is characterized in that on the break hook face that a side of crankpin is provided with when eccentric bush rotates:
In break (23), be provided with according to the rotation of described eccentric bush (12) and compress and its device that recovers to the normal position direction of resilient support.
2, the eccentric bush braking device of scroll compressor according to claim 1 is characterized in that: the device that described resilient support eccentric bush recovers comprises the cut (231) that the cylindrical body with hollow forms break main body (230) and forms to a side Vertical direction of described break main body (230).
3, the eccentric bush braking device of scroll compressor according to claim 2 is characterized in that: described break main body (230) is fixed on the inner side surface of eccentric bush (12).
4, the eccentric bush braking device of scroll compressor according to claim 3, it is characterized in that: break joining hole (12a) the inner side surface bottom at eccentric bush (12) is provided with fixed projection (232), is provided with the fixed groove (233) that inserts to lower side from the top of fixed lobe (232) in break main body (230) bottom.
5, the eccentric bush braking device of scroll compressor according to claim 2 is characterized in that: break joining hole (12a) inner side surface of described eccentric bush (12) is provided with fixed projection (232), is inserted into the cut (231) of break.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100723948A CN100455809C (en) | 2004-10-27 | 2004-10-27 | Eccentric bushing brake for vortex compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100723948A CN100455809C (en) | 2004-10-27 | 2004-10-27 | Eccentric bushing brake for vortex compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1766340A true CN1766340A (en) | 2006-05-03 |
| CN100455809C CN100455809C (en) | 2009-01-28 |
Family
ID=36742406
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100723948A Expired - Fee Related CN100455809C (en) | 2004-10-27 | 2004-10-27 | Eccentric bushing brake for vortex compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100455809C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103958897A (en) * | 2012-01-11 | 2014-07-30 | 三菱电机株式会社 | Vane-type compressor |
| CN109578409A (en) * | 2019-01-31 | 2019-04-05 | 广西玉柴机器股份有限公司 | A kind of positioning pin eccentric bush |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06185476A (en) * | 1992-12-18 | 1994-07-05 | Fujitsu General Ltd | Scroll compressor |
| US5378129A (en) * | 1993-12-06 | 1995-01-03 | Copeland Corporation | Elastic unloader for scroll machines |
| US5496158A (en) * | 1994-12-22 | 1996-03-05 | Carrier Corporation | Drive for scroll compressor |
| JPH11280674A (en) * | 1998-03-31 | 1999-10-15 | Fujitsu General Ltd | Scroll compressor |
| KR100371171B1 (en) * | 2000-06-30 | 2003-02-05 | 엘지전자 주식회사 | Radial adaptation structure for scroll compressor |
-
2004
- 2004-10-27 CN CNB2004100723948A patent/CN100455809C/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103958897A (en) * | 2012-01-11 | 2014-07-30 | 三菱电机株式会社 | Vane-type compressor |
| CN103958897B (en) * | 2012-01-11 | 2016-10-05 | 三菱电机株式会社 | Blade-tape compressor |
| CN109578409A (en) * | 2019-01-31 | 2019-04-05 | 广西玉柴机器股份有限公司 | A kind of positioning pin eccentric bush |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100455809C (en) | 2009-01-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1249350C (en) | Vacuum-protective device for vortex compressor | |
| KR100434399B1 (en) | Oil leakage reducing apparatus for enclosed compressor | |
| CN1807897A (en) | Multi-stage rotary compressor | |
| CN1611788A (en) | Hermetic compressor | |
| KR100432115B1 (en) | Plural cylinder rotary compressor | |
| CN1766340A (en) | Eccentric bushing brake for vortex compressor | |
| CN1538070A (en) | Device for preventing reverse rotationof scroll compressor | |
| CN1401908A (en) | Transmission pin structure of swirl compressor | |
| CN1018374B (en) | Fluid compressor | |
| JP5167829B2 (en) | Compressor | |
| CN1896531A (en) | Blade spring arrangement of rotary compressor | |
| JP2003301784A (en) | Rotation preventing mechanism of scroll fluid machine | |
| WO2004038225A1 (en) | Compressor | |
| CN1363777A (en) | Silencer of exhaust valve for sealed rotary compressor | |
| KR100674656B1 (en) | Inclined Board Structure for Oil Hydraulic Pump | |
| KR100641239B1 (en) | Hermetic rotary compressor | |
| CN1201085C (en) | Antifriction device of compressor | |
| CN1888433A (en) | Rotation type compressor | |
| KR20220148004A (en) | Scroll compressor | |
| KR100309289B1 (en) | Wankel compressor without discharge valve | |
| CN1566682A (en) | Multiple compression type compressor | |
| CN1704605A (en) | Thrust surface friction diminishing device for vane type compressor | |
| CN1566672A (en) | Device for decreasing thrust surface friction for hermetic compressor | |
| CN1888434A (en) | Spindle combine structure for gear compressor | |
| KR20030041578A (en) | Swash plate structure for enclosed compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090128 Termination date: 20161027 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |