CN202391727U - Double-chamber vane pump with combined compensation of large cylinder springs and small cylinder springs - Google Patents
Double-chamber vane pump with combined compensation of large cylinder springs and small cylinder springs Download PDFInfo
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- CN202391727U CN202391727U CN2011205247248U CN201120524724U CN202391727U CN 202391727 U CN202391727 U CN 202391727U CN 2011205247248 U CN2011205247248 U CN 2011205247248U CN 201120524724 U CN201120524724 U CN 201120524724U CN 202391727 U CN202391727 U CN 202391727U
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- main shaft
- enclosing cover
- pump housing
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- 238000005516 engineering process Methods 0.000 abstract description 4
- 230000002301 combined effect Effects 0.000 abstract 1
- 238000007789 sealing Methods 0.000 description 22
- 239000007788 liquid Substances 0.000 description 6
- 238000007599 discharging Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000011089 mechanical engineering Methods 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
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Abstract
A double-chamber vane pump with combined compensation of large cylinder springs and small cylinder springs comprises a spindle drum, small cylinder springs, large cylinder springs, an end-face compensating disc, sliding vanes, a front-end outer cap, end cap screws, a pump body and a back-end outer cap. The end-face compensating disc is arranged between a spindle drum-rotating section and the front-end outer cap; an outer elliptic contour of the end-face compensating disc match with inner an elliptic hole of the pump body in a sliding seal manner; a central hole of the compensating disc match with a section with a key of a spindle in a sliding manner; one ends of the large cylinder springs are fixed at boss positions at the back of the compensating disc; the other ends of the large cylinder springs abut against an inner side of the front-end outer cap in a pressing manner; one ends of the small cylinder springs are fixed on slider bosses; and the other ends of the small cylinder springs support bottoms of vane slots. Technologies of end-face wear compensation seal and radial wear compensation seal can be achieved simultaneously by depending on combined effects of radial bounce of the small cylinder springs and axial bounce of internal pressure channels.
Description
Technical field
The utility model belongs to mechanical engineering field, and International Classification of Patents is the F04D non-varactor pump, relate to a kind of with mechanical energy convert into fluid pressure can the transformation of energy rotary volume pump, be meant a kind of big or small cylindrical spring combined compensation two-chamber vane pump especially.
Background technique
Rotary volume pump has the high advantage of efficient, but all exists its efficient of long-time running wearing and tearing back obviously to reduce, and causes the main cause of above-mentioned defective to be that movable isolation of end face between hyperbaric chamber and the low pressure chamber fail to play effective sealing.The undersized easy heat expansion of end face fit tolerance is stuck firmly; The end face fit tolerance is oversize then fails to play effective sealing; And long-time running wearing and tearing back sealing effect is poorer, and the production line of having to stop is changed pumping unit, causes very big direct waste and indirect loss.
In all rotary volume pumps, vane pump is widely used in each industry and commerce field because of plurality of advantages such as its compact structures.Perplexing its problem that always can not get effectively solving is: behind the long-term high speed operation, must wearing and tearing of its end face can not get effective compensation.China's license notification number: CN1059019C pendulum rotary vane pump; China's license notification number: CN100374725C rotating vane pump; China's license notification number: the arc toothed mesohigh gear pump of CN1316162C asymmetric double; The sliding blade pump of China's license notification number: CN1081750C band plastic shell; China's license notification number: CN101120175B and China's license notification number: CN101403382B gear pump for micro-miniature turbojet engine or the like; All not seeing has practicable effective compensation method and measure, comes to solve simultaneously rotary volume pump end wear compensation sealing and gauge wear compensation sealing problem.
Summary of the invention
The purpose of the utility model provides a kind of big or small cylindrical spring combined compensation two-chamber vane pump; The technology that possesses end wear compensation sealing and gauge wear compensation sealing simultaneously; To realize being in the compensation sealing state all the time between hyperbaric chamber and the low pressure chamber; Remedy the deficiency of existing technology, fill up the technological gap that rotary volume pump possesses sealing of end wear compensation sealing and gauge wear compensation sealing simultaneously.
To achieve these goals; The utility model provides following technological scheme: a kind of big or small cylindrical spring combined compensation two-chamber vane pump; Comprise main shaft drum, small column spring, big column spring, end-face compensate dish, sliding blade, front end enclosing cover, bolts, the pump housing, rear end enclosing cover; The both ends of the surface of the described pump housing are vertical each other with the oval endoporus of the pump housing, and front end enclosing cover that is stamped respectively on the both ends of the surface and rear end enclosing cover use bolts fastening respectively; The oval endoporus of the band seal groove protecgulum hole of described front end enclosing cover and the band seal groove bonnet hole of rear end enclosing cover and the pump housing is on the same central axis; Main shaft is drawn together in described main shaft bulge has key section, main shaft rotary drum section and main shaft not to have the key section; Main shaft has key section and band seal groove protecgulum hole to be slidingly matched; Main shaft does not have the key section and is slidingly matched with band seal groove bonnet hole; Have two blade flutings on the main shaft rotary drum section at least, in every blade fluting a slice sliding blade is housed, the slide plate outer rim is being pasted the oval endoporus of the pump housing; Described main shaft rotary drum section is located in the oval endoporus of the pump housing between front end enclosing cover and the rear end enclosing cover together with sliding blade one; As improvement: between described main shaft rotary drum section and the front end enclosing cover end-face compensate dish is arranged; And the outer elliptic contour of described end-face compensate dish has slipper seal with the oval endoporus of the pump housing and cooperates; Compensating disc center hole and main shaft have the key section to be slidingly matched, and boss place, the compensating disc back side is fixed with an end of big column spring, and the other end of big column spring is pressed against the inboard face of front end enclosing cover; And an end of described small column spring is fixedly on the slide plate boss, and the other end of small column spring is supported on the bottom surface of blade fluting.
As further improvement: be stamped two suction tanks outside the described rear end and be communicated with a port that sucks runner respectively, be connected with suction port again after two another port that suck runners merge; There are two drain tanks being communicated with a port of discharging runner respectively, are connected with exhaust port again after the another port of two discharge runners merges.
Structural principle:
External force is through the input of main shaft keyway; Drive the rotation of whole main shaft drum; Relatedly order about the sliding blade that each slip is inserted in the blade fluting and rotate synchronously; Rely on centrifugal force and the radially acting in conjunction of rebounding force of small column spring, make the slide plate outer rim of sliding blade be close to all the time on the oval endoporus of the pump housing, constitute the radial compensation sealing.
Sliding blade one sideslip sheet end face is pasting the inboard face of rear end enclosing cover; Opposite side slide plate end face is pasting end-face compensate dish horizontal frontal plane; The big column spring of using boss place, the compensating disc back side is pressed against the axial rebounding force of the inboard face generation of front end enclosing cover; The both sides slide plate end face of guaranteeing each sliding blade all is in the compensation sealing state, constitutes the nose balance sealing.
The dynamic confined space that is constituted with main shaft rotary drum section cylindrical and the oval endoporus of the pump housing between each sliding blade is in combination wear compensation sealing state all the time.
The minor axis diameter of the oval endoporus of the pump housing equals the outside diameter of main shaft rotary drum section, but slidably; The oval endoporus major diameter of the pump housing is greater than the outside diameter of main shaft rotary drum section and certain space length is arranged.The space of both sides is isolated the formation two-chamber by sliding blade works simultaneously, all can lead to suction tank and drain tank respectively on each active chamber.There is sliding blade to isolate between suction tank on the same active chamber and the drain tank.
Each dynamic confined space progressively diminishes when being rotated in each drain tank one side, from the pump housing to outside drain medium; Progressively become big when being rotated in each suction tank one side, from outside inhalant liquid body medium to the pump housing.Go round and begin again, realize continuously merging the back from suction port inhalant liquid body medium through sucking runner by two suction tanks, after the supercharging by drain tank after discharging the runner merging from exhaust port drain medium.
The beneficial effect of the utility model is: rely on the radially rebounding force of small column spring and the axial rebounding force synergy of interior pressure passageway; Realized possessing simultaneously the technology of end wear compensation sealing and gauge wear compensation sealing, guaranteed that constituting each moving attitude confined space with main shaft rotary drum section cylindrical and the oval endoporus of the pump housing between each sliding blade is in the combined compensation sealing state all the time.
Description of drawings
Fig. 1 is the sectional drawing of the utility model integral body through main axis;
Fig. 2 is the sectional drawing in P-P cross section among Fig. 1;
Fig. 3 be among Fig. 2 main shaft rotary drum section 18 together with sliding blade 50 with turn clockwise 15 the degree after sectional drawing;
Fig. 4 be among Fig. 2 main shaft rotary drum section 18 together with sliding blade 50 with turn clockwise 30 the degree after sectional drawing;
Fig. 5 is the stereogram of sliding blade 50;
Fig. 6 is the stereogram of main shaft drum 10;
Fig. 7 is the stereogram of end-face compensate dish 40.
Embodiment
In conjunction with accompanying drawing and embodiment, further structure and the working principle to the utility model elaborates.
A kind of big or small cylindrical spring combined compensation two-chamber vane pump; Comprise main shaft drum 10, small column spring 20, big column spring 30, end-face compensate dish 40, sliding blade 50, front end enclosing cover 60, bolts 70, the pump housing 80, rear end enclosing cover 90; The both ends of the surface of the described pump housing 80 are vertical each other with pump housing ellipse endoporus 85, and the front end enclosing cover 60 and the rear end enclosing cover 90 that are stamped respectively on the both ends of the surface use bolts 70 fastening respectively; The band seal groove protecgulum hole 61 of described front end enclosing cover 60 is on the same central axis with the band seal groove bonnet hole 91 of rear end enclosing cover 90 and the oval endoporus 85 of the pump housing; Described main shaft drum 10 comprises that main shaft has key section 11, main shaft rotary drum section 18 and main shaft not to have key section 13; Main shaft has key section 11 and band seal groove protecgulum hole 61 to be slidingly matched; Main shaft does not have key section 13 and is slidingly matched with band seal groove bonnet hole 91; Have two blade flutings 15 on the main shaft rotary drum section 18 at least, every blade fluting is equipped with a slice sliding blade 50 for 15 li, and slide plate outer rim 58 is being pasted the oval endoporus 85 of the pump housing; Described main shaft rotary drum section 18 is located in the oval endoporus 85 of the pump housing between front end enclosing cover 60 and the rear end enclosing cover 90 together with sliding blade 50 1; As improvement: between described main shaft rotary drum section 18 and the front end enclosing cover 60 end-face compensate dish 40 is arranged; And the outer elliptic contour 48 of described end-face compensate dish 40 has slipper seal with the oval endoporus 85 of the pump housing and cooperates; Compensating disc center hole 41 has key section 11 to be slidingly matched with main shaft; Boss 44 places, the compensating disc back side are fixed with an end of big column spring 30; The other end of big column spring 30 is pressed against the inboard face of front end enclosing cover 60, and an end of described small column spring 20 is fixedly on the slide plate boss 55, and the other end of small column spring 20 is supported on the bottom surface of blade fluting 15.
As further improvement: described rear end enclosing cover 90 has two suction tanks 56 being communicated with a port that sucks runner 96 respectively, is connected with suction port 86 after two another port that suck runners 96 merge again; There are two drain tanks 54 being communicated with a port of discharging runner 94 respectively, are connected with exhaust port 84 again after the another port of two discharge runners 94 merges.
Embodiment's installation steps and working procedure are following.
Installation steps:
In Fig. 1, Fig. 2, embodiment selects every sliding blade 50 that a slide plate boss 55 is arranged; End cap screw 87 numbers of each side of the pump housing 80 are 4; There is compensating disc back side boss 44 at end-face compensate dish 40 back sides; 6 blade flutings 15 are arranged on the main shaft rotary drum section 18.
Pad is put gasket seal 98 between the end face of rear end enclosing cover 90 and the pump housing 80 1 sides, with 4 bolts 70 rear end enclosing cover 90 is fixed on the pump housing 80 1 side end faces.At 15 li a slice sliding blades 50 of packing into successively of 6 blades fluting, an end of small column spring 20 is fixedly on the slide plate boss 55, and the other end of small column spring 20 is supported on slot 15 bottom surface of blade.Main shaft drum 10 and sliding blade 50 together are placed in the oval endoporus 85 of the pump housing, wherein main shaft does not have key section 13 and penetrates in the band seal groove bonnet hole 91 and be slidingly matched again.
With the slide plate end face 51 of end-face compensate dish 40 horizontal frontal planes towards sliding blade 50, letting compensating disc center hole 41 flip sleeves go into main shaft has key section 11.The outer elliptic contour 48 of end-face compensate dish 40 has slipper seal with the oval endoporus 85 of the pump housing and cooperates, thereby end-face compensate dish 40 has key section 11 can only make axial slip with respect to main shaft.Boss 44 places fix big column spring 30 at the compensating disc back side; Pad is put gasket seal 68 on the opposite side end face of the pump housing 80; Cover front end enclosing cover 60 backs and front end enclosing cover 60 is fixed on the pump housing 80 opposite side end faces, make the big column spring 30 at boss 44 places, the compensating disc back side be pressed against front end enclosing cover 60 inboard faces with 4 bolts 70.
There is preceding seal ring 16 at band 61 places, seal groove protecgulum hole, and there is back seal ring 19 at band 91 places, seal groove bonnet hole.
During the work operation:
External force is through 12 inputs of main shaft keyway; Drive whole main shaft drum 10 rotations; Relatedly order about the sliding blade 50 that each slip is inserted in the blade fluting 15 and rotate synchronously; Rely on centrifugal force and the radially acting in conjunction of rebounding force of small column spring 20, make the blade outer rim 58 of sliding blade 50 be close to all the time on the oval endoporus 85 of the pump housing, constitute the radial compensation sealing state.
Sliding blade 50 1 sideslip sheet end faces 51 are pasting the inboard face of rear end enclosing cover; Opposite side slide plate end face 51 is pasting end-face compensate dish 40 horizontal frontal planes; The inboard face that the big column spring 30 of using boss 44 places, the compensating disc back side is pressed against front end enclosing cover 60 produces axial rebounding force, constitutes the nose balance sealing.The both sides slide plate end face 51 of guaranteeing each sliding blade 50 all is in the compensation sealing state.
The minor axis diameter of the oval endoporus 85 of the pump housing equals the outside diameter of main shaft rotary drum section 18, but slidably; Oval endoporus 85 major diameter of the pump housing are greater than the outside diameter of main shaft rotary drum section 18 and certain space length is arranged.The space of both sides is isolated the formation two-chamber by sliding blade 50 works simultaneously, all can lead to suction tank 56 and drain tank 54 respectively on each active chamber.
Six dynamic confined spaces that six sliding blades 50 and main shaft rotary drum section 18 cylindricals and pump housing ellipse endoporus 85 are constituted are in all the time and have the wear compensation sealing state.There is sliding blade 50 that they are kept apart in turn between suction tank 56 on the same active chamber and the drain tank 54.
Each dynamic confined space progressively diminishes when being rotated in each drain tank 54 1 side, in the pump housing liquid medium by drain tank 54 through discharge runners 94 from exhaust port 84 to outside drain medium;
Each dynamic confined space progressively becomes when being rotated in each suction tank 56 1 side greatly, sucks outside liquid medium to the pump housing in through sucking runner 96 from suction port 86 by suction tank 56.Go round and begin again; Realize continuously merging the back and sucking the outside liquid media in the pump housing through sucking runner 96 from suction port 86 by two suction tanks 56, the liquid medium after the supercharging by drain tank 54 after 94 merging of discharge runner from exhaust port 84 to outside drain medium.
Claims (2)
1. one kind big or small cylindrical spring combined compensation two-chamber vane pump; Comprise main shaft drum (10), small column spring (20), big column spring (30), end-face compensate dish (40), sliding blade (50), front end enclosing cover (60), bolts (70), the pump housing (80), rear end enclosing cover (90); The both ends of the surface of the described pump housing (80) are vertical each other with the oval endoporus of the pump housing (85), and front end enclosing cover (60) that is stamped respectively on the both ends of the surface and rear end enclosing cover (90) use bolts (70) fastening respectively; The band seal groove protecgulum hole (61) of described front end enclosing cover (60) is on the same central axis with the band seal groove bonnet hole (91) of rear end enclosing cover (90) and the oval endoporus of the pump housing (85); Described main shaft drum (10) comprises that main shaft has key section (11), main shaft rotary drum section (18) and main shaft not to have key section (13); Main shaft has key section (11) and band seal groove protecgulum hole (61) to be slidingly matched; Main shaft does not have key section (13) and is slidingly matched with band seal groove bonnet hole (91); Have two blade flutings (15) on the main shaft rotary drum section (18) at least, a slice sliding blade (50) is equipped with in every blade fluting (15) lining, and slide plate outer rim (58) is being pasted the oval endoporus (85) of the pump housing; Described main shaft rotary drum section (18) is located in the oval endoporus of the pump housing (85) between front end enclosing cover (60) and the rear end enclosing cover (90) together with sliding blade (50); It is characterized in that: between described main shaft rotary drum section (18) and the front end enclosing cover (60) end-face compensate dish (40) is arranged; And the outer elliptic contour (48) of described end-face compensate dish (40) has slipper seal with the oval endoporus of the pump housing (85) and cooperates; Compensating disc center hole (41) has key section (11) to be slidingly matched with main shaft; Compensating disc back side boss (44) locates to be fixed with an end of big column spring (30); The other end of big column spring (30) is pressed against the inboard face of front end enclosing cover (60), and an end of described small column spring (20) is fixedly on the slide plate boss (55), and the other end of small column spring (20) is supported on the bottom surface of blade fluting (15).
2. a kind of big or small cylindrical spring combined compensation two-chamber vane pump according to claim 1; It is characterized in that: described rear end enclosing cover (90) has two suction tanks (56) being communicated with a port of suction runner (96) respectively, and the another port of two suction runners (96) is connected with suction port (86) after merging again; Have two drain tanks (54) being communicated with a port of discharge runner (94) respectively, the another port of two discharge runners (94) is connected with exhaust port (84) after merging again.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011205247248U CN202391727U (en) | 2011-11-30 | 2011-11-30 | Double-chamber vane pump with combined compensation of large cylinder springs and small cylinder springs |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011205247248U CN202391727U (en) | 2011-11-30 | 2011-11-30 | Double-chamber vane pump with combined compensation of large cylinder springs and small cylinder springs |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202391727U true CN202391727U (en) | 2012-08-22 |
Family
ID=46666657
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011205247248U Expired - Fee Related CN202391727U (en) | 2011-11-30 | 2011-11-30 | Double-chamber vane pump with combined compensation of large cylinder springs and small cylinder springs |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202391727U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102425545A (en) * | 2011-11-30 | 2012-04-25 | 张意立 | Large and small cylinder spring combination compensation double-cavity vane pump |
| CN103147977A (en) * | 2013-02-05 | 2013-06-12 | 中国石油天然气股份有限公司 | Torsion spring vane pump for oil well lifting |
-
2011
- 2011-11-30 CN CN2011205247248U patent/CN202391727U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102425545A (en) * | 2011-11-30 | 2012-04-25 | 张意立 | Large and small cylinder spring combination compensation double-cavity vane pump |
| CN102425545B (en) * | 2011-11-30 | 2016-04-06 | 温州市张衡科技服务有限公司 | A kind of size cylinder spring combination compensation double-cavity vane pump |
| CN103147977A (en) * | 2013-02-05 | 2013-06-12 | 中国石油天然气股份有限公司 | Torsion spring vane pump for oil well lifting |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20120822 Termination date: 20121130 |