CN203335870U - Self-pumping fluid-dynamic-pressure-type mechanical seal - Google Patents
Self-pumping fluid-dynamic-pressure-type mechanical seal Download PDFInfo
- Publication number
- CN203335870U CN203335870U CN2013202952931U CN201320295293U CN203335870U CN 203335870 U CN203335870 U CN 203335870U CN 2013202952931 U CN2013202952931 U CN 2013202952931U CN 201320295293 U CN201320295293 U CN 201320295293U CN 203335870 U CN203335870 U CN 203335870U
- Authority
- CN
- China
- Prior art keywords
- groove
- rotating ring
- fluid
- backward bending
- face
- 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
Landscapes
- Mechanical Sealing (AREA)
Abstract
The utility model relates to a self-pumping fluid-dynamic-pressure-type mechanical seal. More than three groups of back-bent-type fluid grooves are formed in the moving ring seal end surface of the self-pumping fluid-dynamic-pressure-type mechanical seal. Each fluid groove is composed of a sloping groove and a flat groove; the outlet of each fluid groove is located outside the moving ring seal end surface; and the inlet of each fluid groove is located in the middle of the moving ring seal end surface and is communicated with a seal cavity through an axial duct or an axial and radial combined duct in a moving ring. When the moving ring rotates, media in the fluid grooves are accelerated to be high-speed fluid; the high-speed fluid flows to the outer diameter side of the moving ring and is pumped into the seal cavity under the action of centrifugal force; and a low-pressure area is formed in the inlet of each back-bent-type fluid groove, and media in the seal cavity flow into the back-bent-type fluid grooves through the axial duct or the axial and radial combined duct, which is arranged in the moving ring and is communicated with the seal cavity, under the action of pressure difference, so that a new self-pumping cycle is formed. In the process that the high-speed fluid is pumped out, the flowing speed is reduced, the pressure is increased, and certain opening force is formed as the circulating sectional area gradually increases. The self-pumping fluid-dynamic-pressure-type mechanical seal has good self-lubricating, self-washing and anti-solid-particle-interference ability and superior sealing performance.
Description
Technical field
The utility model belongs to technical field of sealing technology, particularly a kind of have the hydrodynamic effect from pumping mechanical seal, be applicable to the sealing of the running shaft of the rotating machineries such as various compressors, centrifugal pump, reactor stirrer.
Background technique
At present, be widely used in oil, chemical industry, chemical fibre, papermaking, the centrifugal compressor of electric power and metallurgy industry, blower fan, non-contacting mechanical face seal on the equipment such as centrifugal pump, to offer the type groove on the rotating ring sealing surface, utilize principle of hydrodynamics to form the fluid dynamic wedge, produce face opening power, reach the wearing and tearing purpose that reduces seal face, a kind of single-row spiral fluted fluid active and static pressure combined type non-contact mechanical seal that has as disclosed as U.S. US4212475, China's disclosed single-row fluid type groove upstream pumping mechanical seal of ZL00239203.8 and the disclosed dry gas seal of centrifugal machine of ZL201020106087.8.These patents, no matter be dry gas seals, or upstream pumping mechanical seal, the medium that they form hydrodynamic all pumps in groove, when producing face opening power at type groove root, separate rotating ring and stationary ring, reduce seal face and rub, also increased the leak-down rate between rotating ring and stationary ring, if particularly pumped medium contains particle, also can destroy sealing dam end face, accelerate seal failure.For this reason, some known technology improves, and a kind of Hydrodynamic pressure type double spiral groove face seals as disclosed as U.S. Pat 5201531, the disclosed double-loop spiral-slot end sealing of Chinese patent ZL96108614.9 and the disclosed biserial fluid type of ZL00239202.X groove self-lubricating non-contact mechanical seal etc. all have been in harmonious proportion this contradiction effectively.Under given rotation direction, this seal arrangement utilizes a row spiral chute by fluid-encapsulated pumping downstream, another row spiral chute is by fluid-encapsulated upstream pumping, and the pump produced by this two row spiral chute draw pressure reduction and seal face inside and outside the both sides fluid pressure difference balance each other, thereby realize the zero leakage of screw groove end face sealing.But, the complicated structure of this class sealing, installing space is large, and is only applicable to the little operating mode of seal face both sides fluid pressure difference.
Summary of the invention
The purpose of this utility model be propose a kind of be applicable to seal face both sides fluid pressure differential wide scope have the hydrodynamic effect from pumping mechanical seal, to solve, existing single-row Spiral Groove Mechanical Seal face opening power is little, leak-down rate is large, the particle-resistant interference performance is poor, the seal face complex structure of double spiral groove mechanical seal, the problem that installing space is large, acquisition has larger work elasticity than above-mentioned sealing under identical condition, and the effect of zero leakage.
The technical solution of the utility model is:
A kind of from the mechanical seal of pumping Hydrodynamic pressure type, be arranged between the casing 2 and axle 10 or axle sleeve 8 of rotating machinery, for rotating ring 3, rotating ring O shape circle 12, stationary ring 11, stationary ring with O shape enclose 5, spring 7, stationary seat 14 etc. form; Rotating ring 3 end faces that coordinate with stationary ring 11 are divided into the groove district and seal the external lateral portion that Ba37，Cao Qu is distributed in end face, and sealing dam 37 is distributed in the external lateral portion of end face; The groove district offers 3 groups of above backward bending type fluid type grooves 39, and the sealing surface between backward bending type fluid type groove 39 forms the sealing weir;
Described backward bending type fluid type groove 39 comprises slope groove 32 and 33 two parts of rising as high as the banks, the large radius position of slope groove 32 in rotating ring 3 end faces, the 33 minor radius positions in rotating ring 3 end faces of rising as high as the banks;
The outlet of described backward bending type fluid type groove 39 is positioned at the outer radius of rotating ring 3 sealing surfaces, import 31 is positioned at the middle part of rotating ring 3 sealing surfaces, and the import 31 of described backward bending type fluid type groove 39 is communicated with Seal cage 1 by the axial channel on rotating ring 3 or axial-radial combination duct 30;
The both sides cell wall of described backward bending type fluid type groove 39, a side is working surface 34, opposite side is non-working surface 35;
Medium in described backward bending type fluid type groove 39, when rotating ring 3 rotation, working surface by backward bending type fluid type groove 39 is accelerated into high-velocity fluid, under centrifugal action, along non-working surface 35 to rotating ring, 3 outside diameters flow and are pumped in Seal cage 1, and form low pressure area at import 31 places of backward bending type fluid type groove 39, medium in Seal cage 1 flows in backward bending type fluid type groove 39 by axial channel or the axial-radial combination duct 30 be communicated with Seal cage 1 on rotating ring 3 under differential pressure action, forms again and again and circulates from pumping; This time time from the pumping cyclic process, on the one hand, realized the selflubricating of mechanical seal; On the other hand, the continuous circulation of fluid between sealing surface, take away the frictional heat between sealing surface in time, realized the flushing certainly of sealing; And the effect of centrifugal force has increased the power in the direction of flow rotating ring 3 sealing surfaces outsides, reduced the leak-down rate of direction of flow rotating ring 3 sealing surface inboards; Particularly; the effect of centrifugal force; make the sealed fluid that contains solid particle entered in backward bending type fluid type groove 39; can produce solid particle separates with matrix; the solid particle that wherein density is large obtains larger centrifugal force; be pumped out and again deliver in Seal cage 1 with fluid, do not enter sealing Ba37Qu, avoided the abrasive wear between sealing surface.
The described fluid that is accelerated into high speed by backward bending type fluid type groove 39 working surfaces 31, in the process that is pumped out backward bending type fluid type groove 39, along with the increase gradually of the actual internal area of backward bending type fluid type groove 39, flow velocity reduces, pressure increases, and forms the opening force that separates rotating ring 3 and stationary ring 11.
The both sides cell wall molded line of described backward bending type fluid type groove 39 is helix.
The helix of the both sides cell wall molded line of described backward bending type fluid type groove 39 has identical helix angle.
The helix angle of the helix of the both sides cell wall molded line of described backward bending type fluid type groove 39 does not wait, and the helix angle of working surface 34 is less than the helix angle of non-working surface 35.
Helix and import 31 circular holes of the both sides cell wall molded line of described backward bending type fluid type groove 39 are tangent.
Axial-radial combination duct 30 on described rotating ring 3 is wedge-like opening 38 with the cross section of the joint of rotating ring 3 peripheries.
Another technological scheme of the present utility model is:
A kind of from the mechanical seal of pumping Hydrodynamic pressure type, be arranged between the casing 2 and axle 10 or axle sleeve 8 of rotating machinery, for rotating ring 3, rotating ring O shape circle 12, stationary ring 11, stationary ring with O shape enclose 5, spring 7, stationary seat 14 etc. form; Rotating ring 3 end faces that coordinate with stationary ring 11 are divided into the groove district and seal the external lateral portion that Ba37，Cao Qu is distributed in end face, and sealing dam 37 is distributed in the external lateral portion of end face; The groove district offers 3 groups of above backward bending type fluid type grooves 39, and the sealing surface between backward bending type fluid type groove 39 forms the sealing weir; Described backward bending type fluid type groove 39 comprises slope groove 32 and 33 two parts of rising as high as the banks, the large radius position of slope groove 32 in the rotating ring end face, 33 positions of the minor radius in the rotating ring end face of rising as high as the banks; The import 31 of described backward bending type fluid type groove 39 is communicated with the circular ring slot 36 that is arranged on rotating ring 3 sealing surface middle parts, and described circular ring slot 36 has an axial channel be communicated with Seal cage 1 or axial-radial combination duct 30 at least.
Described circular ring slot 36 have collect selflubricating, from flushing medium with prevent that inhomogeneous and fluids backward bending type fluid type groove 39 import 31 places of pumped medium from supplementing the effect that cavitation occurs not in time.
When 32 angles with end face of slope groove of backward bending type fluid type groove 39 are 0 or during rp=r2, the dark type groove such as be; When rp=ro, it is single slope groove 32.By changing quantity and the parameter of backward bending type fluid type groove 39, can meet the seal request of different sealed mediums.
Beneficial effect of the present invention
Described in the utility model a kind of from the mechanical seal of pumping Hydrodynamic pressure type, there is following advantage:
1. there is superior sealability, be applicable to carry centrifugal pump, centrifugal compressor, mixing plant and other rotating machinery class shaft seals of the various process fluids such as inflammable, explosive, poisonous, can realize that the microcosmic of sealed fluid is without leakage.
2. in rotating ring when rotation,, the different quality particle produces different centrifugal force, makes of the present utility modelly from the mechanical seal of pumping Hydrodynamic pressure type, to have automatic removing solid particle function, can avoid sealing the abrasive wear on dam.
3. using scope is wide, both can be used as hydraulic seal, can be used as again gas seal.
4. unique selflubricating, from cooling pre-washing function, guaranteed stability and the durability of mechanical seal work.
5. under static state the high pressure side fluid directly injects between sealing surface, eliminated the solid friction that starts moment between sealing surface, and can form rapidly again fluid film and two sealing surfaces are separated starting moment, therefore sealing is also applicable as the frequent rotating machinery class shaft seal of start-stop.
6. the high pressure buffer fluid, from sealed medium, has saved the transporting system of high pressure buffer fluid, has reduced the operating cost of pump, the corresponding economic benefit that improved.
The accompanying drawing explanation
Fig. 1 offers the shaft section structural representation from the mechanical seal of pumping Hydrodynamic pressure type that backward bending type fluid type groove, import are communicated with Seal cage by the axial channel on rotating ring.
Fig. 2 is the rotating ring end view of offering backward bending type fluid type groove.
Fig. 3 be offer that backward bending type fluid type groove and import annular groove, import be communicated with Seal cage by the combination of the axial-radial on rotating ring duct the shaft section structural representation from the mechanical seal of pumping Hydrodynamic pressure type.
Fig. 4 offers the rotating ring end view of backward bending type fluid type groove and import annular groove.
The A-A sectional view that Fig. 5 is Fig. 3.
Wherein,
The inside radius of seal face bonded to each other between R1-rotating ring and stationary ring;
The outer radius of seal face bonded to each other between R2-rotating ring and stationary ring;
Rp-type groove step radius
Ro-type groove inlet hole position radius
Rk-type groove inlet hole radius
R3-type groove import annular groove inside radius
R4-type groove import annular groove outer radius
The pump of G-fluid type groove draws direction;
β-helix angle;
H-rises as high as the banks deeply
The angle of α-slope groove face and end face
The rotation direction of w-rotating ring;
The 1-Seal cage; The 2-casing; The 3-rotating ring; 30-axial channel or axial-radial combination duct; The 31-import; 32-slope groove; 33-rises as high as the banks; The 34-working surface; The 35-non-working surface; The 36-circular ring slot; 37-seals dam; 38-wedge-like opening; 39-backward bending type fluid type groove; 4-O shape circle; O shape circle for the 5-stationary ring; The 6-stop pin; The 7-spring; The 8-axle sleeve; 9,13-Cock screw; The 10-axle; The 11-stationary ring; O shape circle for the 12-rotating ring; The 14-stationary seat.
Embodiment
Describe mode of execution of the present utility model in detail below in conjunction with drawings and Examples.
Embodiment one
Fig. 1 and Fig. 2 have described a kind of from the mechanical seal of pumping Hydrodynamic pressure type, and it is arranged between the casing 2 and axle 10 or axle sleeve 8 of rotating machinery, for rotating ring 3, rotating ring O shape circle 12, stationary ring 11, stationary ring with O shape enclose 5, spring 7, stationary seat 14 etc. form; Rotating ring 3 end faces that coordinate with stationary ring 11 are divided into the groove district and seal the external lateral portion that Ba37，Cao Qu is distributed in end face, and sealing dam 37 is distributed in the external lateral portion of end face; The groove district offers 12 groups of backward bending type fluid type grooves 39, and the sealing surface between backward bending type fluid type groove 39 forms the sealing weir;
Described backward bending type fluid type groove 39 comprises slope groove 32 and 33 two parts of rising as high as the banks, the large radius position of slope groove 32 in the rotating ring end face, 33 positions of the minor radius in the rotating ring end face of rising as high as the banks;
The outlet of described backward bending type fluid type groove 39 is positioned at the outer radius of rotating ring sealing surface, and import 31 is positioned at the middle part of rotating ring 3 sealing surfaces, and the import 31 of described backward bending type fluid type groove 39 is communicated with Seal cage 1 by the axial channel 30 on rotating ring 3;
The both sides cell wall of described backward bending type fluid type groove 39, a side is working surface 34, opposite side is non-working surface 35;
Medium in described backward bending type fluid type groove 39, when rotating ring 3 rotation, working surface 34 by backward bending type fluid type groove 39 is accelerated into high-velocity fluid, under centrifugal action, along non-working surface 35 to rotating ring, 3 outside diameters flow and are pumped in Seal cage 1, and forming low pressure area at import 31 places of backward bending type fluid type groove 39, the medium in Seal cage 1 flows in backward bending type fluid type groove 39 by the axial channel 30 be communicated with Seal cage 1 on rotating ring 3 under differential pressure action, forms again and again and circulates from pumping; This time time from the pumping cyclic process, on the one hand, realized the selflubricating of mechanical seal; On the other hand, the continuous circulation of fluid between sealing surface, take away the frictional heat between sealing surface in time, realized the flushing certainly of sealing; And the effect of centrifugal force has increased the power in the direction of flow rotating ring 3 sealing surfaces outsides, reduced the leak-down rate of direction of flow rotating ring 3 sealing surface inboards; Particularly; the effect of centrifugal force; make the sealed fluid that contains solid particle entered in backward bending type fluid type groove 39; can produce solid particle separates with matrix; the solid particle that wherein density is large obtains larger centrifugal force; be pumped out and again deliver in Seal cage 1 with fluid, do not enter sealing Ba37Qu, avoided the abrasive wear between sealing surface.
The described fluid that is accelerated into high speed by backward bending type fluid type groove 39 working surfaces 31, in the process that is pumped out backward bending type fluid type groove 39, along with the increase gradually of the actual internal area of backward bending type fluid type groove 39, flow velocity reduces, pressure increases, and forms the opening force that separates rotating ring 3 and stationary ring 11.
The both sides cell wall molded line of described backward bending type fluid type groove 39 is helix.
The helix of the both sides cell wall molded line of described backward bending type fluid type groove 39 has identical helix angle.
Helix and import 31 circular holes of the both sides cell wall molded line of described backward bending type fluid type groove 39 are tangent.
Embodiment two
Fig. 3 to Fig. 5 is another kind of from the mechanical seal of pumping Hydrodynamic pressure type, be that with embodiment one difference the import 31 of the described backward bending type fluid type of the present embodiment groove 39 is communicated with the circular ring slot 36 that is arranged on rotating ring 3 sealing surface middle parts, described circular ring slot 36 is provided with 6 axial-radial combination ducts 30 that are communicated with Seal cage 1; Axial-radial combination duct 30 on described rotating ring 3 is wedge-like opening 38 with the cross section of the joint of rotating ring 3 peripheries; Described circular ring slot 36 have collect selflubricating, from flushing medium with prevent that inhomogeneous and fluids backward bending type fluid type groove 39 import 31 places of pumped medium from supplementing the effect that cavitation occurs not in time.
All the other structures and mode of execution are identical with embodiment one.
Claims (7)
1. one kind from the mechanical seal of pumping Hydrodynamic pressure type, be arranged between the casing (2) and axle (10) or axle sleeve (8) of rotating machinery, for rotating ring (3), rotating ring, O shape circle (12), stationary ring (11), stationary ring enclose (5), spring (7), stationary seat (14) etc. with O shape and form, and it is characterized in that:
Rotating ring (3) end face coordinated with stationary ring (11) is divided into the groove district and seals the external lateral portion that ，Cao district, dam (37) is distributed in end face, and sealing dam (37) is distributed in the external lateral portion of end face; The groove district offers 3 groups of above backward bending type fluid type grooves (39), and the sealing surface between backward bending type fluid type groove (39) forms the sealing weir;
Described backward bending type fluid type groove (39) comprises slope groove (32) and (33) two parts of rising as high as the banks, the large radius position of slope groove (32) in the rotating ring end face, (33) the minor radius position in the rotating ring end face of rising as high as the banks;
The outlet of described backward bending type fluid type groove (39) is positioned at the outer radius of rotating ring sealing surface, import (31) is positioned at the middle part of rotating ring (3) sealing surface, and the import (31) of described backward bending type fluid type groove (39) is communicated with Seal cage (1) by the axial channel on rotating ring (3) or axial-radial combination duct (30);
The both sides cell wall of described backward bending type fluid type groove (39), a side is working surface (34), opposite side is non-working surface (35).
2. as claimed in claim 1 from the mechanical seal of pumping Hydrodynamic pressure type, it is characterized in that: the both sides cell wall molded line of described backward bending type fluid type groove (39) is helix.
3. as claimed in claim 1 or 2 from the mechanical seal of pumping Hydrodynamic pressure type, it is characterized in that: the helix of the both sides cell wall molded line of described backward bending type fluid type groove (39) has identical helix angle.
4. as claimed in claim 1 or 2 from the mechanical seal of pumping Hydrodynamic pressure type, it is characterized in that: the helix angle of the helix of the both sides cell wall molded line of described backward bending type fluid type groove (39) does not wait, and the helix angle of working surface (34) is less than the helix angle of non-working surface (35).
5. as claimed in claim 1 or 2 from the mechanical seal of pumping Hydrodynamic pressure type, it is characterized in that: helix and import (31) circular hole of the both sides cell wall molded line of described backward bending type fluid type groove (39) are tangent.
6. as claimed in claim 1 from the mechanical seal of pumping Hydrodynamic pressure type, it is characterized in that: the axial-radial combination duct (30) on described rotating ring (3) is wedge-like opening (38) with the cross section of the joint of rotating ring (3) periphery.
7. one kind from the mechanical seal of pumping Hydrodynamic pressure type, be arranged between the casing (2) and axle (10) or axle sleeve (8) of rotating machinery, for rotating ring (3), rotating ring, O shape circle (12), stationary ring (11), stationary ring enclose (5), spring (7), stationary seat (14) etc. with O shape and form, and it is characterized in that:
Rotating ring (3) end face coordinated with stationary ring (11) is divided into the groove district and seals the external lateral portion that ，Cao district, dam (37) is distributed in end face, and sealing dam (37) is distributed in the external lateral portion of end face; The groove district offers 3 groups of above backward bending type fluid type grooves (39), and the sealing surface between backward bending type fluid type groove (39) forms the sealing weir;
Described backward bending type fluid type groove (39) comprises slope groove (32) and (33) two parts of rising as high as the banks, the large radius position of slope groove (32) in the rotating ring end face, (33) the minor radius position in the rotating ring end face of rising as high as the banks;
The import (31) of described backward bending type fluid type groove (39) is communicated with the circular ring slot (36) that is arranged on rotating ring (3) sealing surface middle part, and described circular ring slot (36) has an axial channel be communicated with Seal cage (1) or axial-radial combination duct (30) at least.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013202952931U CN203335870U (en) | 2013-05-28 | 2013-05-28 | Self-pumping fluid-dynamic-pressure-type mechanical seal |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013202952931U CN203335870U (en) | 2013-05-28 | 2013-05-28 | Self-pumping fluid-dynamic-pressure-type mechanical seal |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203335870U true CN203335870U (en) | 2013-12-11 |
Family
ID=49704546
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013202952931U Expired - Fee Related CN203335870U (en) | 2013-05-28 | 2013-05-28 | Self-pumping fluid-dynamic-pressure-type mechanical seal |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203335870U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103982662A (en) * | 2014-06-11 | 2014-08-13 | 湘潭电机股份有限公司 | Rotary sealing device |
| WO2014190825A1 (en) * | 2013-05-28 | 2014-12-04 | 南京林业大学 | Pump-conveyed fluid dynamic-pressure mechanical seal |
| CN104235381A (en) * | 2014-08-29 | 2014-12-24 | 江苏大学 | Dynamic and static pressure combined mechanical seal structure with liquid storage tanks |
| CN108916386A (en) * | 2018-08-30 | 2018-11-30 | 大连威尔博合金科技有限公司 | A kind of mechanical seal ring |
| CN111188653A (en) * | 2020-03-06 | 2020-05-22 | 上海好米密封科技有限公司 | Gas lubrication dynamic pressure sealing device for miniature high-speed turboexpander |
| US12012915B2 (en) | 2021-02-09 | 2024-06-18 | Honda Motor Co., Ltd. | Pump cover attachment system |
-
2013
- 2013-05-28 CN CN2013202952931U patent/CN203335870U/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014190825A1 (en) * | 2013-05-28 | 2014-12-04 | 南京林业大学 | Pump-conveyed fluid dynamic-pressure mechanical seal |
| CN103982662A (en) * | 2014-06-11 | 2014-08-13 | 湘潭电机股份有限公司 | Rotary sealing device |
| CN104235381A (en) * | 2014-08-29 | 2014-12-24 | 江苏大学 | Dynamic and static pressure combined mechanical seal structure with liquid storage tanks |
| CN108916386A (en) * | 2018-08-30 | 2018-11-30 | 大连威尔博合金科技有限公司 | A kind of mechanical seal ring |
| CN111188653A (en) * | 2020-03-06 | 2020-05-22 | 上海好米密封科技有限公司 | Gas lubrication dynamic pressure sealing device for miniature high-speed turboexpander |
| US12012915B2 (en) | 2021-02-09 | 2024-06-18 | Honda Motor Co., Ltd. | Pump cover attachment system |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103267132B (en) | From the mechanical seal of pumping Hydrodynamic pressure type | |
| CN203335870U (en) | Self-pumping fluid-dynamic-pressure-type mechanical seal | |
| EP2940353B1 (en) | Sliding component | |
| CN105465371A (en) | Bidirectional-rotation self-pumping fluid dynamic pressure type mechanical seal | |
| CN2534429Y (en) | Double-row same-direction fluid dynamic pressure groove upstream pumping mechanical seal | |
| CN106439023B (en) | A kind of cosine curve type mechanical seal end surface structure | |
| CN201265547Y (en) | Balancing type single-suction horizontal multiple-stage centrifugal pump | |
| CN102927287A (en) | Mechanical end face seal with combined fluid slot structure | |
| CN103321748A (en) | Vertical combustion gas turbine | |
| CN206830240U (en) | Non-contact finger sealing device | |
| CN113090337A (en) | Reverse shaft sealing device for double-rotor aircraft engine | |
| CN206206599U (en) | A kind of bidirectional rotation auxiliary start stop mode can the tree-like groove end face seal structure of resorption type | |
| CN112963543B (en) | Diffusion type self-pumping fluid dynamic and static pressure type mechanical seal | |
| CN108050258B (en) | A kind of mechanical seal structure of imitative brambles shape type groove | |
| CN105697366A (en) | Blade type sea water pump | |
| CN203051777U (en) | Mechanical face seal with combined fluid groove structure | |
| CN211343700U (en) | Air bearing, rotor system and micro gas turbine | |
| CN115325034B (en) | High-speed rolling bearing sealing structure with fluid self-pumping effect | |
| CN208918899U (en) | One kind is like the combined mechanical seal end surface structure of comb dynamic and static pressure | |
| CN111005936A (en) | Air bearing, rotor system and micro gas turbine | |
| CN207178686U (en) | Zero leakage pumping formula mechanical seal | |
| CN103047171A (en) | Novel full-function floating throttling device | |
| CN114060108B (en) | Water lubrication bearing of turbine type energy recovery integrated machine | |
| CN202280841U (en) | Double-column reverse-intersecting fluid dynamic pressing groove mechanical seal | |
| CN110410504B (en) | Mechanical seal end face structure of variable-depth spiral T-shaped groove |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 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: 20131211 Termination date: 20160528 |