CN202370823U - Disc spring compensated three-line meshing rotor pump - Google Patents
Disc spring compensated three-line meshing rotor pump Download PDFInfo
- Publication number
- CN202370823U CN202370823U CN2011204838471U CN201120483847U CN202370823U CN 202370823 U CN202370823 U CN 202370823U CN 2011204838471 U CN2011204838471 U CN 2011204838471U CN 201120483847 U CN201120483847 U CN 201120483847U CN 202370823 U CN202370823 U CN 202370823U
- Authority
- CN
- China
- Prior art keywords
- eccentric
- rotor
- half hole
- compensating disc
- compensating
- 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.)
- Expired - Fee Related
Links
Images
Abstract
The utility model discloses a disc spring compensated three-line meshing rotor pump. The disc spring compensated three-line meshing rotor pump comprises a pump body, a rotor shaft which passes through and is arranged in a central through hole of the pump body, and a driven rotor which is arranged in an eccentric half hole of the pump body in a sliding way, wherein an eccentric end cover is hermetically fixed at the outer end surface of the eccentric half hole by at least three screws; and a compensating disc is arranged in the eccentric half hole in a sliding way between the eccentric end cover and the outer end surface of the driven rotor. Three contact lines are synchronously produced between three equal cambered surface working sections of the rotor shaft and four equal inner arc working surfaces of the driven rotor, and are combined with the bottom surface of the eccentric half hole and a frontal plane of the compensating disc to form three dynamic spaces, namely A, B and c, and the synchronous formation of three sealing belts which extend axially can still be ensured even if the pump is used for a long time and is uniformly worn, so that radial directions of the three dynamic spaces are always effectively sealed; and disc springs are arranged between the back of the compensating disc and the eccentric end cover, and push the compensating disc to achieve the effect of compensating the wear of end surfaces of the three dynamic spaces, namely the A, the B and the c.
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 displacement pump, be meant that especially a kind of belleville spring compensates three-way engagement rotor pump.
Background technique
Known displacement pump main structure form has: plunger pump, screw pump, Roots pump and sliding vane pump.Displacement 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.
Plunger pump is fit to high pressure but pulse is big, does not possess self-compensating after the wearing and tearing; Screw pump be fit to high viscosity but on unit volume manufacture cost high, do not possess self-compensating after the wearing and tearing yet; Roots pump is fit to liquids and gases but radially there is the gap in it, and radially with behind the end wear does not possess self-compensating; Sliding vane pump can be accomplished self-compensating after the gauge wear, but does not still possess self-compensating behind the end wear, and the slide plate stuck phenomenon happens occasionally.So far fail to see a kind of effective displacement pump both at home and abroad, can possess the structure function of end wear sealing compensation and gauge wear sealing compensation simultaneously.(its English full name of " SCI " U.S. " science citation index " is that ta is tion Index for Science Ci to the U.S.'s three large-engineerings science and technology magazine, is called for short SCI; " EI " U.S. its English full name of EI is the Engineering Index, is called for short EI; Its English full name of " IS is tP " U.S. " scientific and technical conference record index " is that Index is technical Proceedings for to Scien for tific &, and abbreviation IS is tP.) take in global engineering science and technology paper, also not seen has a kind of displacement pump that can possess end wear sealing compensation and gauge wear sealing compensation rotator type simultaneously.
Summary of the invention
The purpose of the utility model provides a kind of belleville spring and compensates three-way engagement rotor pump; The technology that possesses end wear sealing compensation and gauge wear sealing compensation simultaneously; To realize being in good movable isolating seal state for a long time between hyperbaric chamber and the low pressure chamber; Remedy the deficiency of existing technology, fill up the technological gap that displacement pump possesses end wear sealing compensation and gauge wear sealing compensation simultaneously.
To achieve these goals; The utility model provides following technological scheme: a kind of belleville spring compensates three-way engagement rotor pump; Comprise the pump housing and pass through in the central through bore that is installed in the pump housing rotor shaft be slidingly mounted in off-centre half hole of the pump housing from rotor; Eccentric end cap is by on the airtight exterior edge face that is fixed on eccentric half hole of at least three screws; Eccentric end cap and from there being compensating disc to be slidingly mounted in eccentric half hole central axis O of the central through bore on the described pump housing between the exterior edge face of rotor
2Eccentric axis O with off-centre half hole
1Between eccentric distance be t, a crescent shape suction inlet UNICOM on the bottom surface, described off-centre half hole import, another crescent shape row mouthful UNICOM outlet; Described rotor shaft comprises three five equilibrium cambered surface active sections and do not have the keyway shaft part and the shaft with keyway section, and the inner end of three five equilibrium cambered surface active sections is pasting bottom surface, eccentric half hole, and the exterior edge face of three five equilibrium cambered surface active sections is being pasted by the horizontal frontal plane of compensating disc; Described have the both ends of the surface of four five equilibrium inner arc working surfaces also pasting the horizontal frontal plane of eccentric bottom surface, half hole and compensating disc respectively from rotor; As improvement: described rotor shaft and between the inboard face of rotor rotary drum and front end enclosing cover, compensating disc is arranged; The eccentric distance of compensating disc cylindrical and compensating disc eccentric opening also is t; And disk is pasting the fixing big nose circle of belleville spring in the compensating disc back side; The spring foot of belleville spring is pressed against the inboard face of protecgulum of front end enclosing cover, and also has locating stud to be fixed on the back side of eccentric end cap and the eccentric positioning hole at the compensating disc back side is slidingly matched.
Structural principle:
The central axis O of rotor shaft
2With eccentric axis O from rotor 2
1Between eccentric distance be t; Three five equilibrium cambered surface active sections of rotor shaft and from three Line of contact of synchronized generation between four five equilibrium inner arc working surfaces of rotor; Horizontal frontal plane in conjunction with eccentric bottom surface, half hole and compensating disc; Constitute A, B and three dynamic spaces of C,, guarantee the radially effectively sealing all the time of three dynamic spaces even can guarantee that still three axially extended sealing strips form synchronously after using uniform wear for a long time.
The back side of compensating disc has positioning hole and locating stud to be slidingly matched, and locating stud is fixedly connected with eccentric end cap, thereby compensating disc can only be made axial slip with respect to eccentric end cap.Belleville spring promotes compensating disc and plays compensating action for the end wear of A, B and three dynamic spaces of C.
Possess in the time of end wear sealing compensation and gauge wear sealing compensation, realize being in good movable isolating seal state for a long time between hyperbaric chamber and the low pressure chamber.
The beneficial effect of the utility model is: rotor shaft and from three axially extended sealing strips of rotor synchronized generation; Support rebounding force by means of belleville spring; Horizontal frontal plane one side of compensating disc is close to the exterior edge face of two rotors all the time, forces the inner end of two rotors also to be close to bottom surface, eccentric half hole.Constitute A, B and three dynamic spaces of C and possessed end wear sealing compensation and gauge wear sealing compensation simultaneously, realize being in good movable isolating seal state for a long time between hyperbaric chamber and the low pressure chamber.
Description of drawings
Fig. 1 is the sectional drawing of the utility model integral body through axis;
Fig. 2 is the sectional drawing in W-W cross section among Fig. 1;
Fig. 3 is the relative position relation of inner rotor shaft 1 with respect to three dynamic spaces of synchronized generation that are in operation from rotor 2;
Fig. 4 is with respect to Fig. 3, and rotor shaft 1 is around central axis O
2Be rotated counterclockwise 40 the degree, from rotor 2 around eccentric axis O
1Be rotated counterclockwise 30 the degree after relative position relation;
Fig. 5 is with respect to Fig. 3, and rotor shaft 1 is around central axis O
2Be rotated counterclockwise 80 the degree, from rotor 2 around eccentric axis O
1Be rotated counterclockwise 60 the degree after relative position relation;
Fig. 6 is with respect to Fig. 3, and rotor shaft 1 is around central axis O
2Be rotated counterclockwise 120 the degree, from rotor 2 around eccentric axis O
1Be rotated counterclockwise 90 the degree after relative position relation;
Fig. 7 is with respect to Fig. 3, and rotor shaft 1 is around central axis O
2Be rotated counterclockwise 180 the degree, from rotor 2 around eccentric axis O
1Be rotated counterclockwise 135 the degree after relative position relation;
Fig. 8 is with respect to Fig. 3, and rotor shaft 1 is around central axis O
2Be rotated counterclockwise 240 the degree, from rotor 2 around eccentric axis O
1Be rotated counterclockwise 180 the degree after relative position relation;
Fig. 9 is with respect to Fig. 3, and rotor shaft 1 is around central axis O
2Be rotated counterclockwise 360 the degree, from rotor 2 around eccentric axis O
1Be rotated counterclockwise 270 the degree after relative position relation;
Figure 10 is with respect to Fig. 3, and rotor shaft 1 is around central axis O
2Be rotated counterclockwise 480 the degree, from rotor 2 around eccentric axis O
1Be rotated counterclockwise 360 the degree after relative position relation;
Figure 11 is the stereogram of rotor shaft 1;
Figure 12 is a rotor shaft 1 and from the camberline construction drawing of rotor 2.
Figure 13 is the sectional drawing of belleville spring 9;
Figure 14 is the plan view of belleville spring 9.
Embodiment
In conjunction with the accompanying drawings and embodiments, further the structure and the operation principle of the utility model elaborated.
A kind of belleville spring compensates three-way engagement rotor pump; Comprise the pump housing 4 and pass through in rotor shaft 1 and the off-centre that is slidingly mounted on the pump housing 4 half hole 42 in the central through bore 41 that is installed in the pump housing 4 from rotor 2; Eccentric end cap 5 is by on the airtight exterior edge face that is fixed on eccentric half hole 42 of at least three screw 8; Eccentric end cap 5 and from there being compensating disc 6 to be slidingly mounted in eccentric half hole 42 the central axis O of the central through bore 41 on the described pump housing 4 between the exterior edge face of rotor 2
2Eccentric axis O with off-centre half hole 42
1Between eccentric distance be t, crescent shape suction inlet 47 UNICOMs on the bottom surface, described off-centre half hole 40 import 46, another crescent shape row mouthful 48 UNICOMs outlet 49; Described rotor shaft 1 comprises three five equilibrium cambered surface active sections 13 and does not have keyway shaft part 11 and shaft with keyway section 12; The inner end of three five equilibrium cambered surface active sections 13 is pasting the exterior edge face of bottom surface, eccentric half hole 40, three five equilibrium cambered surfaces active section 13 and is being pasted by the horizontal frontal plane of compensating disc 6; Described have the both ends of the surface of four five equilibrium inner arc working surfaces also pasting the horizontal frontal plane of bottom surface, eccentric half hole 40 and compensating disc 6 respectively from rotor 2; As improvement: described rotor shaft 1 and between the inboard face of rotor 2 rotary drums and front end enclosing cover, compensating disc is arranged; Compensating disc cylindrical 62 also is t with the eccentric distance of compensating disc eccentric opening 61; And disk 69 is pasting the fixing big nose circle 96 of belleville spring 9 in the compensating disc back side; The spring foot 36 of belleville spring 9 is pressed against the inboard face 59 of protecgulum of front end enclosing cover 5, and also has locating stud 7 to be fixed on the back side of eccentric end cap 5 and the eccentric positioning hole 67 at compensating disc 6 back sides is slidingly matched.
Installation steps and working procedure:
In Fig. 1 and Fig. 2, earlier with the shaft with keyway section 12 of rotor shaft 1 from bottom surface, off-centre half hole 40 1 sides, pass central through bore 41 and be slidingly matched with it, the inner end of three five equilibrium cambered surface active sections 13 is pasting bottom surface, eccentric half hole 40.To be placed in eccentric half hole 42 from rotor 2 and be slidingly matched, also paste bottom surface, eccentric half hole 40, make the central axis O of rotor shaft 1 from the inner end of rotor 2
2With eccentric axis O from rotor 2
1Between eccentric distance be t.
Three five equilibrium cambered surface active sections 13 of rotor shaft 1 and from three point of contact of synchronized generation between four five equilibrium inner arc working surfaces of rotor 2; Cross point of contact and form three axially extended sealing strips; Horizontal frontal plane in conjunction with bottom surface, eccentric half hole 40 and compensating disc 6 constitutes A, B and three dynamic spaces of C.Even can guarantee that still three axially extended sealing strips form synchronously after using uniform wear for a long time, guarantee the radially effectively sealing all the time of three dynamic spaces;
From no keyway shaft part 11 1 ends, load onto compensating disc 6 successively again; The fixing big nose circle 96 of locating stud 7 and belleville spring 9 is fixed on the back side of eccentric end cap 5; At last with eccentric end cap 5 shimmings 54, on the outside end face of four screws 8 with airtight off-centre half hole 42 that is fixed on the pump housing 4 of eccentric end cap 5.
Locating stud 7 is fastened on the eccentric end cap 5 inboard faces, and the spring foot 36 of belleville spring 9 is pressed against the inboard face 59 of protecgulum of front end enclosing cover 5, and band " O " the type ring recess through hole 51 on the eccentric end cap 5 is inserted in from no keyway shaft part 11 1 ends of rotor shaft 1 and is slidingly matched.
The back side of compensating disc 6 has positioning hole 67 and locating stud 7 to be slidingly matched, and locating stud 7 is fixedly connected with eccentric end cap 5, thereby compensating disc 6 can only be made axial slip with respect to eccentric end cap 5.Belleville spring 9 promotes compensating disc 6 and plays compensating action for the end wear of A, B and three dynamic spaces of C.
Possess in the time of end wear sealing compensation and gauge wear sealing compensation, realize being in good movable isolating seal state for a long time between hyperbaric chamber and the low pressure chamber.
" O " type circle in all " O " type ring recess plays the motive sealing effect at position of living in.
In Fig. 3 to Figure 10; During work, external force drives rotor shaft 1 rotation through shaft with keyway section 12, stirs then from rotor 2 rotations; From both rotating center deviation distances of rotor 2 and rotor shaft 1 is t; Three five equilibrium cambered surface active sections 13 of rotor shaft 1 and from three axially extended sealing strips of synchronized generation between four five equilibrium inner arc working surfaces of rotor 2, the horizontal frontal plane in conjunction with bottom surface, eccentric half hole 40 and compensating disc 6 constitutes A, B and three dynamic spaces of C.During rotation, A, B and three dynamic spaces of C along with rotation will become a big side gradually and be crescent shape suction inlet 47, lead to import 46; One side that will diminish gradually along with rotation of A, B and three dynamic spaces of C is a crescent shape row mouth 48, leads to outlet 49.Rotor shaft 1 continuously rotation order about A, B and three dynamic spaces of C go round and begin again accomplish inhale, row's work.
Figure 11 is the stereogram of rotor shaft 1.
Figure 13, Figure 14 are reflection belleville springs 9.
Setting-out X of elder generation and vertical with it line Y1 and line Y2, intersection point is respectively O
1, O
2, O
1With O
2Be 6mm apart for eccentric distance t. gets eccentric distance t here;
With O
1Be the center of circle, R1 is that radius is made basic circle R1.Here getting the R1 radius is 60mm;
An intersection point with basic circle R1 and line X is the center of circle, and R2 is that radius is made arc section R2, again with O
1Be the center of circle, with arc section R2 around O
1Trisection annular display.Here getting the R2 radius is 40mm;
The distance that is extended to R3 with the intersection point of arc section R2 and line X is the center of circle, is that the intersection point that radius is crossed arc section R2 and line X is made arc section R3 with R3, again with O
2Be the center of circle, with arc section R3 around O
2Trisection annular display.Here getting the R3 radius is 120mm;
Choose two arc section R3 and an arc section R2 respectively, the three-way tangent arc section R4 that does gets the R4 radius here and is approximately 4.7mm;
With R5 is that radius is made two adjacent arc section R2 of arc section R5 connection respectively, and the R5 radius is 32mm here.
Article three, arc section R4 alternately with three point of contact of three arc section R2 synchronized generation, cross point of contact and form three axially extended sealing strips, constitute A, B and three dynamic spaces of C.Even after using uniform wear for a long time, three point of contact of synchronized generation form three axially extended sealing strips can guarantee that still three axially extended sealing strips form synchronously, and that guarantees three dynamic spaces radially is in effective sealing all the time.
The both ends of the surface width of three five equilibrium cambered surface active sections 13 of rotor shaft 1 and size equal uniform from the both ends of the surface width of rotor 2; Here getting the both ends of the surface width all is 50mm; The inner end of two rotors is all pasting bottom surface, eccentric half hole 40, and the horizontal frontal plane of compensating disc 6 is pasting the exterior edge face of two rotors simultaneously.The support rebounding force that is supported on the inboard face 59 of protecgulum of eccentric end cap 5 by means of belleville spring 9 and is asking the back side of compensating disc 6 to produce; The horizontal frontal plane of compensating disc 6 is close to the exterior edge face of two rotors all the time; Then force the inner end of two rotors also to be close to bottom surface, eccentric half hole 40, guarantee that the end face slip of three dynamic spaces is in effective sealing all the time.
During work, external force drives rotor shaft 1 rotation through shaft with keyway section 12, stirs then from rotor 2 rotations.From both rotating center deviation distances of rotor 2 and rotor shaft 1 is t; Three five equilibrium cambered surface active sections 13 of rotor shaft 1 and from three axially extended sealing strips of synchronized generation between four five equilibrium inner arc working surfaces of rotor 2; Horizontal frontal plane in conjunction with bottom surface, eccentric half hole 40 and compensating disc 6 constitutes A, B and three dynamic spaces of C.During rotation, A, B and three dynamic spaces of C along with rotation will become a big side gradually and be crescent shape suction inlet 47, lead to import 46; One side that will diminish gradually along with rotation of A, B and three dynamic spaces of C is a crescent shape row mouth 48, leads to outlet 49.Rotor shaft 1 continuously rotation order about A, B and three dynamic spaces of C go round and begin again accomplish inhale, row's work.
Claims (1)
1. a belleville spring compensates three-way engagement rotor pump; Comprise the pump housing (4) and pass through the rotor shaft (1) in the central through bore (41) that is installed in the pump housing (4) and be slidingly mounted in off-centre half hole (42) of the pump housing (4) from rotor (2); Eccentric end cap (5) is by on the airtight exterior edge face that is fixed on eccentric half hole (42) of at least three screws (8); Eccentric end cap (5) and from there being compensating disc (6) to be slidingly mounted in eccentric half hole (42) between the exterior edge face of rotor (2), the central axis O of the central through bore (41) on the described pump housing (4)
2Eccentric axis O with off-centre half hole (42)
1Between eccentric distance be t, a crescent shape suction inlet (47) UNICOM on the bottom surface, described off-centre half hole (40) import (46), another crescent shape row mouthful (48) UNICOM outlet (49); Described rotor shaft (1) comprises three five equilibrium cambered surface active sections (13) and does not have keyway shaft part (11) and shaft with keyway section (12); The inner end of three five equilibrium cambered surface active sections (13) is pasting bottom surface, eccentric half hole (40), and the exterior edge face of three five equilibrium cambered surface active sections (13) is being pasted by the horizontal frontal plane of compensating disc (6); Described have the both ends of the surface of four five equilibrium inner arc working surfaces also pasting the horizontal frontal plane of bottom surface, eccentric half hole (40) and compensating disc (6) respectively from rotor (2); It is characterized in that: described rotor shaft (1) and compensating disc (6) is arranged between the inboard face of rotor (2) rotary drum and front end enclosing cover; Compensating disc cylindrical (62) also is t with the eccentric distance of compensating disc eccentric opening (61); And disk in the compensating disc back side (69) is pasting the fixing big nose circle (96) of belleville spring (9); The spring foot (36) of belleville spring (9) is pressed against the inboard face (59) of protecgulum of front end enclosing cover (5), and also has locating stud (7) to be fixed on the back side of eccentric end cap (5) and the eccentric positioning hole (67) at compensating disc (6) back side is slidingly matched.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011204838471U CN202370823U (en) | 2011-11-18 | 2011-11-18 | Disc spring compensated three-line meshing rotor pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011204838471U CN202370823U (en) | 2011-11-18 | 2011-11-18 | Disc spring compensated three-line meshing rotor pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202370823U true CN202370823U (en) | 2012-08-08 |
Family
ID=46594528
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011204838471U Expired - Fee Related CN202370823U (en) | 2011-11-18 | 2011-11-18 | Disc spring compensated three-line meshing rotor pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202370823U (en) |
-
2011
- 2011-11-18 CN CN2011204838471U patent/CN202370823U/en not_active Expired - Fee Related
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102182673A (en) | Four-line synchromesh spring compensation combination pump | |
| CN202370827U (en) | Disc spring compensating five-wire meshed rotor pump | |
| CN102192142B (en) | Annular air bag compensation sealing four-space rotor pump | |
| CN202370825U (en) | Cylindrical spring compensating four-wire meshed rotor pump | |
| CN202370823U (en) | Disc spring compensated three-line meshing rotor pump | |
| CN102182677B (en) | A kind of four line engagement inner pressuring sealing new pump | |
| CN202370826U (en) | Cylindrical spring compensating three-line meshing rotor pump | |
| CN202348655U (en) | Dished spring compensation four-wire meshing rotor pump | |
| CN202370824U (en) | Five-line-meshed rotor pump compensated by cylindrical spring | |
| CN202040076U (en) | Three-line synchromesh spring-compensation combination pump | |
| CN202326204U (en) | Cylinder spring compensation five-space rotor pump | |
| CN202187910U (en) | Novel four-wire meshing internal pressure seal pump | |
| CN202194821U (en) | Novel pump adopting three-line meshing and internal-pressure sealing | |
| CN202250811U (en) | Spring compensating three-dimensional space rotor pump | |
| CN202194822U (en) | Novel pump adopting five-line meshing and internal-pressure sealing | |
| CN202040077U (en) | Four-line synchromesh spring-compensation combination pump | |
| CN202284535U (en) | Three-space rotor pump with cylindrical spring for compensation | |
| CN102182674B (en) | Five-wire synchronous meshing spring compensation combined pump | |
| CN202284536U (en) | Four-space internal-pressure balance sealing rotor pump | |
| CN202326201U (en) | Spring compensating five-space rotor pump | |
| CN202082094U (en) | Annular air bag compensation seal four-space rotor pump | |
| CN202326203U (en) | Cylindrical spring compensation four-space rotor pump | |
| CN102182675B (en) | Three-wire synchronous meshing spring compensation combined pump | |
| CN202228347U (en) | Pressure air bag compensation sealing three-space rotor pump | |
| CN202040075U (en) | Five-wire synchromesh spring compensating unit pump |
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: 20120808 Termination date: 20121118 |