CN102182677B - A kind of four line engagement inner pressuring sealing new pump - Google Patents
A kind of four line engagement inner pressuring sealing new pump Download PDFInfo
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- CN102182677B CN102182677B CN201110156779.2A CN201110156779A CN102182677B CN 102182677 B CN102182677 B CN 102182677B CN 201110156779 A CN201110156779 A CN 201110156779A CN 102182677 B CN102182677 B CN 102182677B
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- compensating disc
- rotor shaft
- decile
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Abstract
A kind of four line engagement inner pressuring sealing new pump, comprise the pump housing 4 and be arranged on rotor shaft on the central through bore 41 of the pump housing 41 and be arranged in the eccentric half bore 42 of the pump housing 4 from rotor 2, the work inner end of two rotors againsts the bottom plane 40 of eccentric half bore 42, the work exterior edge face of two rotors also againsts the horizontal frontal plane of compensating disc 6, and have the locating stud 7 be fixed on eccentric end cap 5 to limit compensating disc 6 can only to slide axially, eccentric end cap 5 uses the airtight exterior edge face, working area being fixed on eccentric half bore 42 of screw 8 of at least three, the back side of described compensating disc 6 communicates with the interior runner 9 that pushes back with the space between eccentric end cap 5, and rotor shaft 1 and engaging each other rotation from rotor 2, form A, B, C and D tetra-working spaces.This structure has accomplished to possess end wear sealing compensation and gauge wear sealing compensation simultaneously, realizes being in good dynamic isolation sealing state between hyperbaric chamber and low-pressure cavity for a long time.
Description
Technical field
The invention belongs to mechanical engineering field, International Classification of Patents is F04D non-varactor pump, relates to a kind of transformation of energy displacement pump mechanical energy being converted to fluid pressure energy, refers to a kind of four lines engagement inner pressuring sealing new pump especially.
Background technique
Known displacement pump main structure form has: plunger pump, screw pump, Roots pump and sliding vane pump.Have the high advantage of efficiency as displacement pump, but after all there are long-time running wearing and tearing, its efficiency obviously reduces, the end face dynamic isolation between hyperbaric chamber and low-pressure cavity could not play effective sealing to cause the main cause of above-mentioned defect to be.The undersized easy heat expansion of end face fit tolerance is stuck firmly, end face fit tolerance is oversize, could not play effective sealing, and sealing effect is poorer after long-time running wearing and tearing, the production line replacing pumping unit that stops of having to, causes very large direct waste and indirect loss.
Plunger pump is applicable to high pressure but pulse is large, does not possess self-compensating after wearing and tearing; Screw pump be applicable to high viscosity but on unit volume manufacture cost high, also do not possess self-compensating after wearing and tearing; Roots pump is applicable to liquids and gases but its radial direction exists gap, and does not possess self-compensating after radial direction and end wear; Sliding vane pump can accomplish self-compensating after gauge wear, but does not still possess self-compensating after end wear, and slide plate stuck phenomenon happens occasionally.So far could not see a kind of effective displacement pump both at home and abroad, the structure function of end wear sealing compensation and gauge wear sealing compensation can be possessed simultaneously.(its English full name of " SCI " U.S. " science citation index " is ScienceCitationIndex to the U.S. three large-engineering science and technology magazine, is called for short SCI; " EI " U.S. its English full name of Engineering Index is TheEngineeringIndex, is called for short EI; ISTP " U.S.'s " scientific and technical conference record index " its English full name is IndextoScientific & TechnicalProceedings, is called for short ISTP.) storage global project technical paper, do not see there is a kind of displacement pump that simultaneously can possess end wear sealing compensation and gauge wear sealing compensation yet.
Summary of the invention
A kind of four line engagement inner pressuring sealing new pump, comprise the pump housing and be arranged on rotor shaft on the central through bore of the pump housing and be arranged in the eccentric half bore of the pump housing from rotor, rotor shaft and against the bottom plane of eccentric half bore from the work inner end of rotor, rotor shaft and also against the horizontal frontal plane of compensating disc from the work exterior edge face of rotor, the eccentric end cap screw of at least three comes the airtight exterior edge face, working area being fixed on eccentric half bore, and rotor shaft and engaging each other rotation from rotor;
A "O"-ring groove is with, the central axis O of central through bore in central through bore on the described pump housing
2with the eccentric axis O of eccentric half bore
1between be eccentric distance t, a crescent shape suction inlet UNICOM on bottom plane import, and another the crescent shape Pai Kou UNICOM on bottom plane outlet, and outlet has in a bypass and pushes back runner and lead to the space between the back side of compensating disc and eccentric end cap;
Described rotor shaft comprises four decile cambered surface active sections and without keyway shaft part and shaft with keyway section, the work inner end of four decile cambered surface active sections againsts bottom plane, and the work exterior edge face of four decile cambered surface active sections is against by the horizontal frontal plane of compensating disc;
Describedly comprise five full sections of decile cambered surface from rotor, the width of five decile cambered surface full section both ends of the surface is equal consistent with the size of the both ends of the surface width of four decile cambered surface active sections;
The central axis O of described rotor shaft
2with the eccentric axis O from rotor
1between be eccentric distance t, four decile cambered surface active sections of rotor shaft (1) and engaging each other rotation between five full sections of decile cambered surface of rotor, synchronous generation four point of contact, cross point of contact and form four axially extended sealing strips, in conjunction with the horizontal frontal plane of bottom plane and compensating disc, form A, B, C and D tetra-working spaces; It is characterized in that:
Locating stud is fastened on the inboard face of eccentric end cap, and there is eccentric positioning hole at the back side of described compensating disc, and eccentric positioning hole and locating stud are slidably matched, and described locating stud restriction compensating disc can only slide axially;
The back side of described compensating disc communicates with interior one end pushing back runner with the space between eccentric end cap, and the other end inside pushing back runner leads to outlet;
The central axis O of the band "O"-ring groove through hole on described compensating disc
2with the eccentric axis O of band "O"-ring groove cylindrical
1between be eccentric distance t, the "O"-ring in all "O"-ring grooves plays motive sealing effect at residing position;
By means of the interior outlet pressure pushing back runner and introduce, the front of compensating disc is that half leads to outlet, second half leads to import, and the back side is gross area leads to outlet, making the back side of compensating disc, stressed to be greater than front stressed, the horizontal frontal plane of compensating disc can be close to rotor shaft and the work exterior edge face from rotor all the time, then forces rotor shaft and is also close to bottom plane from the work inner end of rotor, guarantees that the end face of four working spaces slides and is in effective sealing all the time.
The invention has the beneficial effects as follows: rotor shaft and engaging each other rotation between rotor, synchronous generation four axially extended sealing strips, make the back side of compensating disc by means of the interior runner that pushes back stressed to be greater than front stressed, the horizontal frontal plane side of compensating disc is close to rotor shaft and the work exterior edge face from rotor all the time, then force rotor shaft and be also close to bottom plane from the work inner end of rotor, form A, B, C and D tetra-working spaces have possessed end wear sealing compensation and gauge wear sealing compensation simultaneously, realize between hyperbaric chamber and low-pressure cavity, being in good dynamic isolation sealing state for a long time.
Accompanying drawing explanation
Fig. 1 is the overall sectional drawing by axis of the present invention.
Fig. 2 is the sectional drawing in W-W cross section in Fig. 1.
Fig. 3 is that inner rotor shaft 1 is relative to the synchronous relative position relation producing four working spaces that is in operation from rotor 2.
Fig. 4 is relative to Fig. 3, and rotor shaft 1 is rotated counterclockwise 50 degree, is rotated counterclockwise the relative position relation after 40 degree from rotor 2.
Fig. 5 is relative to Fig. 3, and rotor shaft 1 is rotated counterclockwise 100 degree, is rotated counterclockwise the relative position relation after 80 degree from rotor 2.
Fig. 6 is relative to Fig. 3, and rotor shaft 1 is rotated counterclockwise 150 degree, is rotated counterclockwise the relative position relation after 120 degree from rotor 2.
Fig. 7 is relative to Fig. 3, and rotor shaft 1 is rotated counterclockwise 200 degree, is rotated counterclockwise the relative position relation after 160 degree from rotor 2.
Fig. 8 is relative to Fig. 3, and rotor shaft 1 is rotated counterclockwise 250 degree, is rotated counterclockwise the relative position relation after 200 degree from rotor 2.
Fig. 9 is relative to Fig. 3, and rotor shaft 1 is rotated counterclockwise 300 degree, is rotated counterclockwise the relative position relation after 240 degree from rotor 2.
Figure 10 is relative to Fig. 3, and rotor shaft 1 is rotated counterclockwise 350 degree, is rotated counterclockwise the relative position relation after 280 degree from rotor 2.
Figure 11 is the perspective view of rotor shaft 1.
Figure 12 is rotor shaft 1 and the camberline construction drawing from rotor 2.
Embodiment
In conjunction with the accompanying drawings and embodiments, further structure of the present invention and working principle are elaborated.
The object of this invention is to provide a kind of four line engagement inner pressuring sealing new pump, possesses the technology of end wear sealing compensation and gauge wear sealing compensation simultaneously, to realize being in good dynamic isolation sealing state between hyperbaric chamber and low-pressure cavity for a long time, make up the deficiencies in the prior art, fill up the technological gap that displacement pump possesses end wear sealing compensation and gauge wear sealing compensation simultaneously.
To achieve these goals, the invention provides following technological scheme: a kind of four line engagement inner pressuring sealing new pump, comprise the pump housing 4 and be arranged on rotor shaft on the central through bore 41 of the pump housing 41 and be arranged in the eccentric half bore 42 of the pump housing 4 from rotor 2, rotor shaft 1 and against the bottom plane 40 of eccentric half bore 42 from the work inner end of rotor 2, rotor shaft 1 and also against the horizontal frontal plane of compensating disc 6 from the work exterior edge face of rotor 2, and have the locating stud 7 be fixed on eccentric end cap 5 to limit compensating disc 6 can only to slide axially, eccentric end cap 5 uses the airtight exterior edge face, working area being fixed on eccentric half bore 42 of screw 8 of at least three, the back side of described compensating disc 6 communicates with interior one end pushing back runner 9 with the space between eccentric end cap 5, the other end inside pushing back runner 9 leads to outlet 49, and rotor shaft 1 and engaging each other rotation from rotor 2, synchronously produce four axially extended sealing strips, form A, B, C and D tetra-working spaces.Inside push back pressure that runner 9 introduces to make the back side of compensating disc 6 stressed to be greater than front stressed, rotor shaft 1 and the work exterior edge face from rotor 2 can be close in its front, then force rotor shaft 1 and be also close to bottom plane 40 from the work inner end of rotor 2, possess end wear sealing compensation; And rotor shaft 1 and synchronously produce four axially extended sealing strips from rotor 2, form A, B, C and D tetra-working spaces, still can ensure that four axially extended sealing strips are synchronously formed after the uniform wear of experience Long-Time Service, synchronous four the axially extended sealing strips produced ensure that radially sliding of four working spaces is in effective sealing all the time.This structure has accomplished to possess end wear sealing compensation and gauge wear sealing compensation simultaneously, realizes being in good dynamic isolation sealing state between hyperbaric chamber and low-pressure cavity for a long time.
Central through bore on a described pump housing 4 41 li band "O"-ring groove, the central axis O of central through bore 41
2with the eccentric axis O of eccentric half bore 42
1between be eccentric distance t, crescent shape suction inlet 47 UNICOM on bottom plane 40 import 46, another crescent shape Pai Kou 48 UNICOM on bottom plane 40 outlet 49, and outlet 49 has in a bypass and pushes back runner 9 and lead to the space between the back side and eccentric end cap 5 of compensating disc 6.
Described rotor shaft 1 comprises four decile cambered surface active sections 13 and without keyway shaft part 11 and shaft with keyway section 12, the work exterior edge face that the work inner end of four decile cambered surface active sections 13 againsts 40, four the decile cambered surface active sections 13 in bottom plane is close to by the horizontal frontal plane of compensating disc 6.
Describedly comprise five full sections of decile cambered surface from rotor 2, the width of five decile cambered surface full section both ends of the surface is equal consistent with the size of the both ends of the surface width of four decile cambered surface active sections 13.
The central axis O of the band "O"-ring groove through hole 61 on described compensating disc 6
2with the eccentric axis O of band "O"-ring groove cylindrical 62
1between be eccentric distance t, the eccentric positioning hole of compensating disc 6 67 and locating stud 7 are slidably matched.By means of the interior outlet pressure pushing back runner 9 and introduce, the front of compensating disc 6 is caused to be that half leads to outlet, second half leads to import, and the back side is gross area leads to outlet, making the back side of compensating disc 6, stressed to be greater than front stressed, the horizontal frontal plane of compensating disc 6 can be close to rotor shaft 1 and the work exterior edge face from rotor 2 all the time, then forces rotor shaft 1 and is also close to bottom plane 40 from the work inner end of rotor 2, guarantees that the end face of four working spaces slides and is in effective sealing all the time.
The central axis O of described rotor shaft 1
2with the eccentric axis O from rotor 2
1between be eccentric distance t, four decile cambered surface active sections 13 of rotor shaft 1 and engaging each other rotation between five full sections of decile cambered surface of rotor 2, synchronous generation four point of contact, cross point of contact and form four axially extended sealing strips, in conjunction with the horizontal frontal plane of bottom plane 40 and compensating disc 6, form A, B, C and D tetra-working spaces, still can ensure that four axially extended sealing strips are synchronously formed after the uniform wear of experience Long-Time Service, synchronous four the axially extended sealing strips produced guarantee that radially sliding of four working spaces is in effective sealing all the time.
Possess while end wear sealing compensation and gauge wear sealing compensation, realize between hyperbaric chamber and low-pressure cavity, being in good dynamic isolation sealing state for a long time.
Installation steps and working principle:
The shaft with keyway section 12 of rotor shaft 1, from side, bottom plane 40, is slidably matched with it through central through bore 41, and the work inner end of four decile cambered surface active sections 13 againsts bottom plane 40.Be placed in eccentric half bore 42 from rotor 2 and be slidably matched, also against bottom plane 40 from the work inner end of rotor 2.The central axis O of rotor shaft 1
2with the eccentric axis O from rotor 2
1between be eccentric distance t, four decile cambered surface active sections 13 of rotor shaft 1 and engaging each other rotation between five full sections of decile cambered surface of rotor 2, synchronous generation four point of contact, cross point of contact and form four axially extended sealing strips, in conjunction with the horizontal frontal plane of bottom plane 40 and compensating disc 6, form A, B, C and D tetra-working spaces, still can ensure that four axially extended sealing strips are synchronously formed after the uniform wear of experience Long-Time Service, guarantee the radial direction effective sealing all the time of four working spaces.
The central axis O of the band "O"-ring groove through hole 61 on compensating disc 6
2with the eccentric axis O of band "O"-ring groove cylindrical 62
1between be eccentric distance t, the eccentric positioning hole of compensating disc 6 67 and locating stud 7 are slidably matched.Inwardly, band "O"-ring groove through hole 61 is slidably matched from being inserted in without keyway shaft part 11 one end of rotor shaft 1 horizontal frontal plane of compensating disc 6, and band "O"-ring groove cylindrical 62 is slidably matched with eccentric half bore 42.
Band "O"-ring groove through hole 51 on eccentric end cap 5 is slidably matched from being inserted in without keyway shaft part 11 one end of rotor shaft 1, and locating stud 7 is fastened on the eccentric inboard face of end cap 5.To after eccentric end cap 5 shimming 54, use the screw 8 of at least three along on the airtight exterior edge face, working area being fixed on the eccentric half bore 42 of the pump housing 4 of outer circular edge of eccentric end cap 5.
The back side of compensating disc 6 has eccentric positioning hole 67 to be slidably matched with locating stud 7, and locating stud 7 is fixedly connected with eccentric end cap 5, and thus compensating disc 6 can only make axial slip relative to eccentric end cap 5."O"-ring in all "O"-ring grooves plays motive sealing effect at residing position.
During work, external force is rotated by shaft with keyway section 12 rotor driven axle 1, then stir and rotate from rotor 2, be t from rotor 2 and the rotating center deviation distance of both rotor shafts 1, four decile cambered surface active sections 13 of rotor shaft 1 and engaging each other rotation between five full sections of decile cambered surface of rotor 2, synchronous generation four axially extended sealing strips, in conjunction with the horizontal frontal plane of bottom plane 40 and compensating disc 6, form A, B, C and D tetra-working spaces.During rotation, A, B, C and D tetra-working spaces along with rotation be crescent shape suction inlet 47 by becoming large side gradually, lead to import 46; A, B, C and D tetra-working spaces along with rotation be crescent shape row mouth 48 by the side diminished gradually, lead to outlet 49.Rotor shaft 1 continuous rotation orders about A, B, C and D tetra-working spaces and to have gone round and begun again suction, row's work.
Figure 12 illustrates rotor shaft 1 and the camberline working process from rotor 2 by means of CAD:
First setting-out X and line Y1 vertical with it and line Y2, intersection point is respectively O
1, O
2, O
1with O
2at a distance of getting t distance here for eccentric distance t. for 6mm;
With O
1for the center of circle, R1 is that radius makes basic circle R1.Here getting R1 radius is 60mm;
With an intersection point of basic circle R1 and line X for the center of circle, R2 is that radius makes arc section R2, then with O
1for the center of circle, by arc section R2 around O1 five decile annular array.Here getting R2 radius is 33mm;
Being extended to the distance of R3 for the center of circle with the intersection point of arc section R2 and line X, is that the intersection point that radius crosses arc section R2 and line X makes arc section R3 with R3, then with O
2for the center of circle, by arc section R3 around O
2quartering annular display.Here getting R3 radius is 50mm;
Choose two arc section R3 and arc section R2 respectively, four lines are tangent makes arc section R4, gets R4 radius here and is approximately 4.8mm;
Be that radius is made arc section R5 respectively and connected two adjacent arc section R2 with R5, R5 radius is 40mm here.
Article four, four point of contact alternately synchronously producing with five arc section R2 of arc section R4, cross point of contact and form four axially extended sealing strips, form A, B, C and D tetra-working spaces.Even if after Long-Time Service uniform wear, synchronous four point of contact produced form four axially extended sealing strips and still can ensure that four axially extended sealing strips are synchronously formed, and guarantee that the radial direction of four working spaces is in effective sealing all the time.
The both ends of the surface width of four decile cambered surface active sections 13 of rotor shaft 1 is equal consistent with the size of the both ends of the surface width from rotor 2, here getting both ends of the surface width is all 50mm, the both ends of the surface width of four decile cambered surface active sections 13 of rotor shaft 1 with from rotor 2 the size of both ends of the surface width equal consistent, the work inner end of two rotors againsts bottom plane 40 respectively, and the horizontal frontal plane of compensating disc 6 againsts the work exterior edge face of two rotors respectively.Make the back side of compensating disc 6 by means of the interior runner 9 that pushes back stressed to be greater than front stressed, the horizontal frontal plane of compensating disc 6 is close to rotor shaft 1 and the work exterior edge face from rotor 2 all the time, then force rotor shaft 1 and be also close to bottom plane 40 from the work inner end of rotor 2, guarantee that the end face of four working spaces slides and be in effective sealing all the time."O"-ring in all "O"-ring grooves plays motive sealing effect at residing position.
A kind of four line engagement inner pressuring sealing new pump, comprise the pump housing 4 and be arranged on rotor shaft on the central through bore 41 of the pump housing 41 and be arranged in the eccentric half bore 42 of the pump housing 4 from rotor 2, there is eccentric end cap 5 exterior edge face, working area of eccentric half bore 42, have the horizontal frontal plane of compensating disc 6 to against work exterior edge face from rotor 2 between the described work exterior edge face from rotor 2 and eccentric end cap 5, locating stud 7 slides the circumferential position of fixed compensation dish 6 relative to eccentric end cap 5.
Central through bore on a pump housing 4 41 li band "O"-ring groove, the central axis O of central through bore 41
2with the eccentric axis O of eccentric half bore 42
1between be eccentric distance t, crescent shape suction inlet 47 UNICOM on bottom plane 40 import 46, and another crescent shape Pai Kou 48 UNICOM outlet 49, and outlet 49 has in a bypass and pushes back runner 9 and lead to the space between the back side and eccentric end cap 5 of compensating disc 6.
First by the shaft with keyway section 12 of rotor shaft 1 from side, bottom plane 40, be slidably matched with it through central through bore 41, the work inner end of four decile cambered surface active sections 13 againsts bottom plane 40.To be placed in eccentric half bore 42 from rotor 2 and be slidably matched, also against bottom plane 40 from the work inner end of rotor 2.Make the central axis O of rotor shaft 1
2with the eccentric axis O from rotor 2
1between be eccentric distance t.Compensating disc 6 is loaded onto successively again from without keyway shaft part 11 one end, locating stud 7 is fixed on the back side of eccentric end cap 5, finally by eccentric end cap 5 shimming 54, by the outer circular edge of the screws 8 of four along eccentric end cap 5, on the airtight exterior edge face, working area being fixed on the eccentric half bore 42 of the pump housing 4.
During work, external force is rotated by shaft with keyway section 12 rotor driven axle 1, then stir and rotate from rotor 2, be t from rotor 2 and the rotating center deviation distance of both rotor shafts 1, four decile cambered surface active sections 13 of rotor shaft 1 are synchronous with between five full sections of decile cambered surface from rotor 2 produces four axially extended sealing strips, in conjunction with the horizontal frontal plane of bottom plane 40 and compensating disc 6, form A, B, C and D tetra-working spaces.During rotation, A, B, C and D tetra-working spaces along with rotation be crescent shape suction inlet 47 by becoming large side gradually, lead to import 46; A, B, C and D tetra-working spaces along with rotation be crescent shape row mouth 48 by the side diminished gradually, lead to outlet 49.Push back runner 9 in outlet 49 bypass and pressure is sent to space between the back side of compensating disc 6 and eccentric end cap 5, making the back side of compensating disc 6, stressed to be greater than front stressed, the horizontal frontal plane of compensating disc 6 can be close to rotor shaft 1 and the exterior edge face from rotor 2 all the time, then force rotor shaft 1 and be also close to bottom plane 40 from the inner end of rotor 2, guarantee that the end face of four working spaces slides and be in effective sealing all the time.Rotor shaft 1 continuous rotation orders about A, B, C and D tetra-working spaces and to have gone round and begun again suction, row's work.
Finally, it is also to be noted that what enumerate above is only a specific embodiment of the present invention.Obviously, the invention is not restricted to above embodiment, many distortion can also be had.All distortion that those of ordinary skill in the art can directly derive from content disclosed by the invention or associate, all should regard as protection scope of the present invention.
Claims (1)
1. a line engagement inner pressuring sealing new pump, the rotor shaft (1) comprising the pump housing (4) and be arranged on the central through bore (41) of the pump housing (4) and be arranged in the eccentric half bore (42) of the pump housing (4) from rotor (2), rotor shaft (1) and against the bottom plane (40) of eccentric half bore (42) from the work inner end of rotor (2), rotor shaft (1) and also against the horizontal frontal plane of compensating disc (6) from the work exterior edge face of rotor (2), eccentric end cap (5) comes the airtight exterior edge face, working area being fixed on eccentric half bore (42) with the screw (8) of at least three, and rotor shaft (1) and engaging each other rotation from rotor (2),
Central through bore (41) inner band "O"-ring groove on the described pump housing (4), the central axis O of central through bore (41)
2with the eccentric axis O of eccentric half bore (42)
1between be eccentric distance t, crescent shape suction inlet (47) UNICOM on bottom plane (40) import (46), another crescent shape row mouth (48) UNICOM on bottom plane (40) outlet (49), and outlet (49) has in a bypass and pushes back runner (9) and lead to the space between the back side of compensating disc (6) and eccentric end cap (5);
Described rotor shaft (1) comprises four decile cambered surface active sections (13) and without keyway shaft part (11) and shaft with keyway section (12), the work inner end of four decile cambered surface active sections (13) againsts bottom plane (40), and the work exterior edge face of four decile cambered surface active sections (13) is against by the horizontal frontal plane of compensating disc (6);
Describedly comprise five full sections of decile cambered surface from rotor (2), the width of five decile cambered surface full section both ends of the surface is equal consistent with the size of the both ends of the surface width of four decile cambered surface active sections (13);
The central axis O of described rotor shaft (1)
2with the eccentric axis O from rotor (2)
1between be eccentric distance t, four decile cambered surface active sections (13) of rotor shaft (1) and engaging each other rotation between five full sections of decile cambered surface of rotor (2), synchronous generation four point of contact, cross point of contact and form four axially extended sealing strips, in conjunction with the horizontal frontal plane of bottom plane (40) and compensating disc (6), form A, B, C and D tetra-working spaces; It is characterized in that:
Locating stud (7) is fastened on eccentric end cap (5) inboard face, there is eccentric positioning hole (67) at the back side of described compensating disc (6), eccentric positioning hole (67) is slidably matched with locating stud (7), and described locating stud (7) restriction compensating disc (6) can only slide axially;
The back side of described compensating disc (6) communicates with interior one end pushing back runner (9) with the space between eccentric end cap (5), and the other end inside pushing back runner (9) leads to outlet (49);
The central axis O of band "O"-ring groove through hole (61) on described compensating disc (6)
2with the eccentric axis O of band "O"-ring groove cylindrical (62)
1between be eccentric distance t, the "O"-ring in all "O"-ring grooves plays motive sealing effect at residing position;
By means of the interior outlet pressure pushing back runner (9) and introduce, the front of compensating disc (6) is that half leads to outlet, second half leads to import, and the back side is gross area leads to outlet, making the back side of compensating disc (6), stressed to be greater than front stressed, the horizontal frontal plane of compensating disc (6) can be close to rotor shaft (1) and the work exterior edge face from rotor (2) all the time, then force rotor shaft (1) and be also close to bottom plane (40) from the work inner end of rotor (2), guarantee that the end face of four working spaces slides and be in effective sealing all the time.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110156779.2A CN102182677B (en) | 2011-06-01 | 2011-06-01 | A kind of four line engagement inner pressuring sealing new pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110156779.2A CN102182677B (en) | 2011-06-01 | 2011-06-01 | A kind of four line engagement inner pressuring sealing new pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102182677A CN102182677A (en) | 2011-09-14 |
| CN102182677B true CN102182677B (en) | 2016-04-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110156779.2A Expired - Fee Related CN102182677B (en) | 2011-06-01 | 2011-06-01 | A kind of four line engagement inner pressuring sealing new pump |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102518587B (en) * | 2011-12-06 | 2015-04-01 | 温州市张衡科技服务有限公司 | Compensating internal-external gear pump for internal pressure passage |
| CN102536798B (en) * | 2011-12-23 | 2016-09-21 | 温州市张衡科技服务有限公司 | A kind of compensation gear pump for internal-pressure passage |
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| CN2483585Y (en) * | 2001-05-14 | 2002-03-27 | 殷建英 | Plate spring type lubricating pump |
| CN1412439A (en) * | 2002-09-28 | 2003-04-23 | 宁波华液机器制造有限公司 | Internal meshed gear pump |
| CN101532603A (en) * | 2009-04-15 | 2009-09-16 | 合肥华升泵阀有限责任公司 | Lubricating pump |
| CN202187910U (en) * | 2011-06-01 | 2012-04-11 | 张意立 | Novel four-wire meshing internal pressure seal pump |
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2011
- 2011-06-01 CN CN201110156779.2A patent/CN102182677B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2104325U (en) * | 1991-04-19 | 1992-05-13 | 田昌桃 | New-type cycloidal lubricating pump |
| CN2168098Y (en) * | 1992-04-21 | 1994-06-08 | 周庆耕 | Cam-rotor vane pump using hydraulic floating sideboard |
| CN2420443Y (en) * | 2000-05-08 | 2001-02-21 | 青州液压件厂有限公司 | Double axial seal compensating high pressure gear pump |
| CN2483585Y (en) * | 2001-05-14 | 2002-03-27 | 殷建英 | Plate spring type lubricating pump |
| CN1412439A (en) * | 2002-09-28 | 2003-04-23 | 宁波华液机器制造有限公司 | Internal meshed gear pump |
| CN101532603A (en) * | 2009-04-15 | 2009-09-16 | 合肥华升泵阀有限责任公司 | Lubricating pump |
| CN202187910U (en) * | 2011-06-01 | 2012-04-11 | 张意立 | Novel four-wire meshing internal pressure seal pump |
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| Publication number | Publication date |
|---|---|
| CN102182677A (en) | 2011-09-14 |
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