CN103697170A - Mechanical sealing device with self supporting type middle differential ring - Google Patents
Mechanical sealing device with self supporting type middle differential ring Download PDFInfo
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- CN103697170A CN103697170A CN201210367097.0A CN201210367097A CN103697170A CN 103697170 A CN103697170 A CN 103697170A CN 201210367097 A CN201210367097 A CN 201210367097A CN 103697170 A CN103697170 A CN 103697170A
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Abstract
The invention provides a mechanical sealing device with a self supporting type middle differential ring. A middle ring structure with the rotating speed differences is arranged between the relative sealing end surfaces of a static ring positioned on a static ring seat and a rotating ring capable of rotating along with a rotating shaft, the axial end surfaces of the two sides of the middle ring structure are respectively in sealed matching with the sealing surfaces of the rotating ring and the static ring, the middle ring structure comprises a middle ring body and a magnetic structure body annularly arranged and connected onto the outer cylindrical surface of the middle ring body, a stator assembly at least provided with two groups of electromagnetic coil winding grooves arranged at intervals is arranged in the corresponding circumference part of the static ring seat separately opposite to the magnetic body structure in annular arrangement, and the middle ring body is hollowly sheathed outside a shaft sleeve synchronously rotating along with the rotating shaft through the inner hole surface. The sealing device has the advantages that the relative rotating speed adjustability and controllability of the sealing end surface can be realized, so the rotating speed of a sealed machine unit does not directly determine the relative rotating speed of the sealing end surface, the problem that a middle ring needs to be singly supported and needs to be driven by a single driving element is also solved, meanwhile, the mutual interference during two-stage or multi-stage sealing is eliminated, and the influence of installation errors, vibration, work deformation and the like is reduced, so both the high-speed contact type mechanical sealing and the low-speed non-contact mechanical sealing are more stable.
Description
Technical field
The present invention relates to a kind of mechanical seal device with middle differential ring structure in running shaft mechanical sealing technology field, applicable to the end face seal between the rotary machine running shafts such as compressor, pump, reactor, stirrer.
Background technique
Core component in fluid end face mechanical sealing device, is rotating ring (rotating ring) and the stationary ring (stationary ring) arranging face-to-face, and the sealing surface by its axial opposite end directly contacts or the separation of little gap realizes the sealing (being end face seal) of medium.The tradition rotating ring of mechanical seal and the running shaft of sealed unit are connected and remain synchronous rotary, and it is upper that stationary ring is circumferentially fixed on support (static ring seat), so the relative rotation speed between moving/stationary ring seal face, are the rotating speed of sealed unit running shaft.Because the relative rotation speed between its two sealing surface is determined by the rotating speed of the running shaft of sealed unit completely, cannot regulate and control, make normal use, particularly impact that relative rotation speed between sealing surface can have a strong impact on sealing at a high speed and the stability that seals of low speed unit axial end.For example: the relative rotation speed of contacting mechanical seal between fast state lower sealing surface is too high, can cause sealing surface to produce the phenomenons such as serious friction, wearing and tearing, heating, distortion, sealability declines rapidly, even cisco unity malfunction; And non-contact mechanical seal is under low speed state, between end face, fluid film can not generate enough opening forces and rigidity, has caused guaranteeing the normal separation of sealing surface and the stability in gap.In addition, when sealed unit running shaft speed fluctuation, particularly open, the stopping time, the contact condition between sealing surface more can sharply worsen.
For this reason, in China Patent Publication No. CN101806362A and notification number CN201772069U, disclose a kind of by be provided with the mode of the middle rotating ring with rotation differential between rotating ring and stationary ring, can change the relative rotation speed between two sealing surfaces in mechanical seal, and the relative rotation speed of its sealing surface can be regulated and controled.In this structure, the adjustment of the structure of said middle rotating ring, supporting and rotating speed and control are the keys that realizes its function.
In No. 201220148219.2 patents, the applicant had once proposed a kind of mechanical seal device with middle differential ring on this basis, by the planetary gear train variable-speed unit with main driving axle, drove this central ring to rotate.Because it all the time need be by an independent power source and through a series of mechanical transmission to the driving of central ring, drive the central ring rotation that need to carry out equally separate support, though thereby it can guarantee the realization of single-stage sealing, but to two-stage or have when more multi-stage sealed, between sealing actuators at different levels, there will be and be difficult to the mutual interference eliminated.In addition, due to the supporting to central ring, with and the structure of driving/driving component comparatively complicated, the alignment error of the structure members such as actuator and bearing, the vibration in operation process, working deformation etc., central ring is imported in capital rigidly into, is also the very important factor that affects its working stability.
Summary of the invention
For above-mentioned situation, the invention provides a kind of mechanical seal device with differential ring in the middle of self support type, certainly the supporting of differential speed rotation ring and the mechanical seal device of rotation speed regulating and controlling in the middle of particularly realizing by electromagnetic action principle, simplify the structure, and can effectively eliminate the mutual interference between sealings at different levels, improved higher/compared with the working life of the slow-speed of revolution and frequent start-stop type unit sealing.
The mechanical seal device of differential ring in the middle of band self support type of the present invention, its basic structure is equally between the rotating ring and the relative seal face of the stationary ring in static ring seat that can rotate with running shaft, is provided with the central ring structure that its both sides axial end is sealed and matched with the sealing surface of rotating ring and stationary ring respectively and has speed discrepancy.In said central ring structure, include central ring body and in ring-type mode, arrange the magnetic texure body being connected on its external cylindrical surface; In the corresponding circumferential location of the relative static ring seat in the magnet structure interval with this annular configuration, corresponding being provided with is at least furnished with for the stator module of the winding slot of electromagnetic coil winding is set with two groups of intervals.Said this central ring body, is placed in running shaft outside the synchronous axle sleeve rotating through its inner hole surface, makes it can produce axial movement and bias radially with respect to the sleeve outer circle cylinder rotating with running shaft.Electromagnetic coil winding in said stator module winding slot, can be connected with direct current or ac power supply, is wherein preferably use threephase AC, the three-phase coiling group that corresponding employing can be mated with threephase AC of the electromagnetic coil winding in winding slot.
Certainly supporting and the rotation of this centre differential speed rotation ring in the above-mentioned mechanical seal device of the present invention, it is to realize by the same principle with electric electromechanics magnetic energy conversion: the rotating magnetic field producing pass into electric current successively with rotation mode in spaced apart electromagnetic coil winding in the stator module of the circumferential location of static ring seat after, the ring-type mode on central ring body external cylindrical surface that acts on is arranged the magnetic texure body of connection, can drive the rotation of central ring body, and drive is placed in the central ring structure outside running shaft axle sleeve, automatically in suspending, be placed in the state rotating operation outside axle sleeve.Change electric current [strength or frequency that stator passes into coiling group in assembly, can realize the adjustment of middle rotating ring rotating speed and control.
In the motor of application electromagnetic conversion principle, can there is at present dividing of permanent magnetic drive and electric excitation driving.Permanent mechanism driving mechanism is to set up excitation field by permanent magnet, realizes the device of energy converting between mechanical.Along with improving constantly of permanent magnetic material performance, particularly rare earth permanent-magnetic material, the development of the further perfect and control technique of processing technology, the application area of permanent magnetic drive is more and more wider, and develops to higher level.With respect to electric excitation driving machine structure, permanent mechanism driving mechanism has the features such as compact structure, volume be little, lightweight, and size and structural type versatile and flexible, can topology go out a variety of structural type.Because permanent mechanism driving mechanism has been cancelled electric excitation system, thereby improve the efficiency of driving mechanism, and made simple in structurely, reliable, can realize the unapproachable high-performance of electric excitation driving machine structure.Therefore, in said structure of the present invention, said magnetic texure body is preferably permanent-magnet material structure, and is more particularly preferably SmCo or NdFeB material structure.
For convenience of the further setting to additional structure, be convenient to the fine finishing to component, and the radial dimension that reduces to a certain extent central ring body, in above-mentioned mechanical seal device, on the said axle sleeve with the synchronous rotation of running shaft, can also further be fixed with turnbarrel, said central ring body is placed in outside the external cylindrical surface of this turnbarrel to have the mode in said radially monolateral gap through its inner hole surface.
Consider the impact of thermal expansivity difference, assembly process and the discontinuity of the factors such as surface Machining roughness in actual production and deviation from cylindrical form, material, and central ring body is radially subject to the floated situation of kinetic pressure when rotated, in said structure, the said radially monolateral gap being placed in outside this rotary sleeve or turnbarrel external cylindrical surface, can be preferably 0.001 ~ 0.2 millimeter.Test demonstration, excessive gap can reduce the kinetic pressure that rotation produces in various degree, and can increase possibility and the amplitude of radially electric shock.
In said structure, the said magnetic texure body being connected on central ring body external cylindrical surface of arranging in ring-type mode, can directly be connected on central ring body external cylindrical surface.But be arranged on this magnetic texure body on central ring body external cylindrical surface in the adverse effect of bringing with the rotation of central ring structure, the centrifugal stress that particularly produces during High Rotation Speed for reducing and offsetting; even contingent explosion when High Rotation Speed, preferably adopts and makes said magnetic texure body be arranged on the mode on central ring body external cylindrical surface through the protection structure of magnetic conductivity.
Said protection structure can be complementary reinforcement or the ruggedized construction of various ways.For example, a kind of selectable mode, by two, with inner hole surface interference, to be assemblied on central ring body external cylindrical surface and the planar disk of radial expansion, and overlap formed cavity body structure with the sealing that is cylndrical surface form at its radial outside end, said this magnetic texure body can axially be assemblied between this two planar disk by clearance type, and is matched with the inner hole surface side of sealing cover.For guaranteeing electromagnetism conduction, wherein at least this sealing is overlapped and should be had magnetic conductivity, to guarantee that it normally works with electromagnetic mode.
The above-mentioned said cavity type protection structure being formed by two planar disk of axially spaced-apart and the sealing of radial outside end cylndrical surface form cover thereof; it can be the cavity body structure of integrated; more preferably make sealing wherein cover and the planar disk of its both sides axially assemble with clearance type, and the assembling type cavity body structure being in transmission connection through modes such as driving pins therebetween.
On said structure basis, at inner hole surface and the rotary sleeve of said central ring body or rotate in the relative engagement face between the external cylindrical surface of sleeve, on the fitting surface of at least one side, in the equidistant mode around its side face, be distributed with the shallow slot in recessed its surface.Here said shallow slot, can be by the same or similar fashion setting of offering shallow slot at present on seal face, and the degree of depth of shallow slot also can, by common mode, be preferably 0.001 ~ 0.2 millimeter.The form of shallow slot equally also can be selected in the straight-line groove as conventional, oblique trunking, spiral chute, arc groove, chevron-notch, T-slot etc.
According to calculating and test result shows, generally, the hydrodynamic pressure relatively producing during rotation between said above-mentioned cylindrical fit face, within the specific limits can with shallow slot magnitude setting increase and corresponding increase.For example, when shallow slot offer quantity≤8 time, hydrodynamic pressure can increase sharply with the increase of shallow slot quantity; When shallow slot quantity continues to increase to after more than 12, hydrodynamic pressure only has less increase with the increase of shallow slot quantity; After shallow slot quantity is more than 20, the impact of the increase convection cell kinetic pressure of shallow slot quantity is very faint.Therefore, the said inner hole surface at central ring body and/or, axle sleeve or rotate the shallow slot quantity of said equidistant distribution on the external cylindrical surface of sleeve, is preferably 6 ~ 24.
The said inner hole surface at central ring body and/or, axle sleeve or rotate between the external cylindrical surface of sleeve said shallow slot on relative engagement face, can be for arranging to run through the through slot mode of its both sides end face; Also the non-penetrating flute profile formula that the two side ends of its fitting surface of can serving as reasons is extended towards the circumference barrier structure that is positioned at its axial width symmetrical center line position.Wherein, while non-penetrating groove being set in the said axial both sides mode that is positioned at circumference barrier structure, more preferably adopt the form in the axial bilateral symmetry distribution of circumference barrier structure.
The above-mentioned mechanical seal device with differential ring in the middle of self support type of the present invention, the principle of changing by electromagnetic energy and hydrodynamic principle, both realized the supporting certainly of differential ring in the middle of making, the regulation and control to the driving of middle differential ring and rotating speed have been realized again simultaneously, and the independent supporting that need solve central ring at present and actuator driving problems have separately been solved, also solved and carried out two-stage or the mutual interference between its driving and transmission when multi-stage sealed, with and because of alignment error, vibration, the rigidity such as working deformation are imported the impact that central ring unavoidably brings into, make high speed contacting mechanical seal and low speed non-contact mechanical seal can there is higher stability.
Below in conjunction with the embodiment by accompanying drawing illustrated embodiment, foregoing of the present invention is described in further detail again.But this should be interpreted as to the scope of the above-mentioned theme of the present invention only limits to following example.Without departing from the idea case in the present invention described above, various replacements or the change according to ordinary skill knowledge and customary means, made, all should comprise within the scope of the invention.
Accompanying drawing explanation
Fig. 1 is a kind of structural representation of the mechanical seal device of differential ring in the middle of band self support type of the present invention.
Fig. 2 is a kind of structure for amplifying schematic diagram of central ring structure in Fig. 1.
Fig. 3 arranges a kind of structural representation of indent shallow slot between the circumference fitting surface of central ring body and its outboard structure.
Fig. 4 is the schematic diagram of a kind of stator module of arranging with central ring structural correspondence circumferential part in static ring seat in Fig. 1.
Embodiment
As shown in the figure be a kind of structural type of the mechanical seal device of differential ring in the middle of band self support type of the present invention.Sealing device mainly consists of rotating ring 1, the central ring structure 2 with speed discrepancy, stator module 3, stationary ring 4, static ring seat 5, stop pin 6, spring 7, throw-out collar 8, snap ring 9, tolerance ring 10, axle sleeve 11 etc.
In central ring structure 2, include central ring body 204, be preferably the permanent magnet 201 of SmCo or NdFeB material, be the ferromagnetic material sealing cover 202 of cylndrical surface form, and be assemblied in two radial expansion planar disk 203 on central ring body 204 external cylindrical surfaces with the interference of axially spaced-apart mode.Two planar disk 203 are at the two side ends face of sealing cover 202, take respectively the contactless axial assembling that gap is 0.01 ~ 0.2 millimeter, and translateral driving pin 214 is in transmission connection with sealing cover 202, form the cavity type protection structure to permanent magnet 201.Permanent magnet 201 is in this protection structure, and bi-side are assemblied between two planar disk 203 so that same little gap is contactless, and is connected with inner hole surface interference fit or the Spielpassung of sealing cover 202 with its external cylindrical surface.The inner hole surface 208 of central ring body 204 be take mode empty set that radially monolateral gap h is 0.001 ~ 0.2 millimeter on the external cylindrical surface 210 of rotor sleeve 205.Central ring body 204, be connected in its outer circumferential face by sealing cover 202, the protection structure that forms of planar disk 203, and be arranged at the permanent magnet 201 in this protection structure, form the integrated central ring structure 2 that can rotate around the common axis line of running shaft 207.
Test shows, the inner hole surface of the external cylindrical surface of permanent magnet 201 and sealing cover 202 is during with interference fit or Spielpassung, and magnitude of interference during interference fit should be not more than 30 microns, and gap width during Spielpassung should be not more than 100 microns.Because sealing cover 202 forms and coordinates with the external cylindrical surface of permanent magnet 201, the centrifugal stress of this cooperation when rotation is interference fit while being greater than medium pressure stress, and produce thus certain prestressing force, to offset the centrifugal stress producing when permanent magnet 201 rotates, thus permanent magnet 201 explosions while preventing High Rotation Speed; When centrifugal stress is less than medium pressure stress, be Spielpassung, now sealing cover 202 radial contraction under pressure medium effect, finally contacts with the outer surface of permanent magnet 201, and form certain pressure stress, to offset the centrifugal stress producing when permanent magnet 201 rotates.
In the inner hole surface 208 of central ring body 204 and/or rotate in sleeve 205 external cylindrical surfaces 210, can, according to current the same manner on the sealing surface of end face seal, around its relative engagement side face, be distributed with equally spacedly the shallow slot 215 of the forms such as 6 ~ 24 recessed straight-line grooves of surperficial interior 0.001 ~ 0.2 millimeter, oblique trunking, spiral chute, arc groove, chevron-notch, T-slot.The through groove that this shallow slot can coordinate side face both sides end face for running through it, also can be mode as shown in Figure 3, the non-penetrating oblique trunking that the two side ends of its fitting surface of serving as reasons is extended towards the circumference barrier structure (dam) 217 of 213 of the symmetrical center line of its axial width, 215 of each circumferential adjacent shallow slots, separate mutually through corresponding weir 216.Each non-penetrating groove of circumference barrier structure 217 axial both sides, is distributed in the axial both sides of circumference barrier structure 217 with symmetric form.
In the working procedure of above-mentioned seal arrangement, the rotating speed of sealed unit running shaft 207 is n
1, the rotating speed of central ring structure 2 is n
2.The rotating speed of the rotating speed of rotating ring 1 and running shaft 207 is all n
1, rotating ring 1 is n with the relative rotation speed of sealing surface that central ring structure 2 forms
2± n
1, central ring structure 2 is n with the relative rotation speed of the formation sealing surface of stationary ring 4
2.N
1immutable, but n
2can be as required, by adjusting the electric current [strength of coiling group in stator module 3, adjust, just can change the rotating speed of middle rotating ring, thereby realization regulates and controls to the relative rotation speed between two groups of sealing surfaces, and be not subject to the impact of sealed unit running shaft 207 rotating speeds.
For example, in the present embodiment, if the relative rotation speed optimum range of sealing surface is 8000 ~ 12000 rpm, normal working speed is 1000 rpm, with regard to several operating modes, the relative rotation speed of two sealing surfaces is calculated respectively below.
(1) sealed unit running shaft 207 stops, and unit stops, now n
1=0rpm.
Sealing surface is now relatively without rotating in tradition mechanical seal, thereby it may cause violent fretting wear to sealing in opening/stop process.In the present embodiment, the rotating speed that can directly adjust central ring structure 2 is n
2=10000 rpm, the relative rotation speed of first group of sealing surface is n
2± n
1=10000 rpm, the relative rotation speed of second group of sealing surface is n
2=10000 rpm, sealing surface relative rotation speed is all in optimum range.
(2) sealed unit running shaft 207 start or docking process in, n now
1=100rpm.
In tradition mechanical seal, sealing surface relative rotation speed is now 100rpm.In the present embodiment, the rotating speed that can directly adjust central ring structure 2 is n
2=10000 rpm, the relative rotation speed of first group of sealing surface is n
2+ n
1=10100 rpm, n
2-n
1=9900 rpm, the relative rotation speed of second group of sealing surface is n
2=10000 rpm, sealing surface relative rotation speed is all in optimum range.
(3) sealed unit running shaft 207 in normal operation, n now
1=1000rpm.
Tradition mechanical seal sealing surface relative rotation speed is now 1000rpm.In the present embodiment, the rotating speed that can directly adjust central ring structure 2 is n
2=10000 rpm, the relative rotation speed of first group of sealing surface is n
2+ n
1=11000 rpm, n
2-n
1=9000 rpm, the relative rotation speed of second group of sealing surface is n
2=10000 rpm, sealing surface relative rotation speed is all in optimum range.
Above embodiment only, with structure and the working procedure thereof of single-stage sealing, describes seal arrangement of the present invention.In actual use, sealing total arrangement as required, can also on the basis of said structure of the present invention, suitably change, realize as mechanical single seal, double seals, tandem seal (more than two-stage), series connection band in the middle of labyrinth (more than two-stage), can also form corresponding combined labyrinth and carbon gland with other seal style such as floating-ring seal, carbon ring seal, labyrinth seal.
Claims (10)
1. with the mechanical seal device of differential ring in the middle of self support type, at the rotating ring (1) that can rotate with running shaft be positioned between the relative seal face of the stationary ring (4) in static ring seat (5), be provided with the central ring structure (2) that both sides axial end is sealed and matched with the sealing surface of rotating ring (1) and stationary ring (4) respectively and has speed discrepancy, it is characterized in that including in central ring structure (2) central ring body (204) and in ring-type mode, arrange the magnetic texure body (201) being connected on its external cylindrical surface, corresponding circumferential location in the relative static ring seat (5) in the magnet structure with this annular configuration (201) interval, corresponding be provided with at least spaced apart for the stator module (3) of electromagnetic coil winding winding slot (301) is set with two groups, central ring body (204) is placed in running shaft (207) outside the synchronous axle sleeve (11) rotating through its inner hole surface (208).
2. mechanical seal device as claimed in claim 1, it is characterized in that being fixed with turnbarrel (205) on the said axle sleeve (11) synchronously rotating with running shaft, central ring body (204) is placed in outside the external cylindrical surface (210) of turnbarrel (205) to have the mode in radially monolateral gap (h) through its inner hole surface (208), and radially monolateral gap (h) is preferably 0.001 ~ 0.2 millimeter.
3. mechanical seal device as claimed in claim 1, is characterized in that said magnetic texure body (201) is arranged on central ring body (204) external cylindrical surface through the protection structure of magnetic conductivity.
4. mechanical seal device as claimed in claim 3; it is characterized in that said protection structure is served as reasons is assemblied in two planar disk (203) of radial expansion on central ring body (204) external cylindrical surface with inner hole surface interference; with the formed cavity body structure of sealing cover (202) in its radial outside end cylndrical surface form; magnetic texure body (201) is axially assemblied between this two planar disk (203) with clearance type; and be matched with the inner hole surface side that (202) are overlapped in sealing, at least this sealing cover (202) has magnetic conductivity.
5. mechanical seal device as claimed in claim 4, is characterized in that said sealing cover (202) and planar disk (203) clearance type of its both sides axially assemble, and are in transmission connection through driving pin (214) therebetween.
6. mechanical seal device as claimed in claim 1, is characterized in that said magnetic texure body (201) is permanent-magnet material structure, is preferably SmCo or NdFeB material structure.
7. the mechanical seal device as described in one of claim 1 to 6, it is characterized in that at inner hole surface (208) and the axle sleeve (11) of said central ring body (204) or rotate in the relative engagement face between the external cylindrical surface (210) of sleeve (205), on the fitting surface of at least one side, in the equidistant mode around its side face, be distributed with the shallow slot (215) in recessed its surface, comprise any in straight-line groove, oblique trunking, spiral chute, arc groove, chevron-notch, T-slot.
8. mechanical seal device as claimed in claim 7, it is characterized in that said central ring body (204) inner hole surface (208) and/or axle sleeve (11), to rotate between the external cylindrical surface (210) of sleeve (205) shallow slot (215) quantity of said equidistant distribution on relative engagement face be 6 ~ 24.
9. mechanical seal device as claimed in claim 7, it is characterized in that said central ring body (204) inner hole surface (208) and/or axle sleeve (11), rotate between the external cylindrical surface (210) of sleeve (205) shallow slot (215) on relative engagement face for running through the through groove of its both sides end face.
10. mechanical seal device as claimed in claim 7, it is characterized in that said central ring body (204) inner hole surface (208) and/or axle sleeve (11), rotate the shallow slot (215) on relative engagement face between the external cylindrical surface (210) of sleeve (205), the non-penetrating groove that the two side ends of its fitting surface of serving as reasons is extended towards the circumference barrier structure (217) that is positioned at its axial width symmetrical center line (213) position, be positioned at the non-penetrating groove in axial both sides of said this circumference barrier structure (217), the axial bilateral symmetry being preferably in circumference barrier structure (217) distributes.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210367097.0A CN103697170A (en) | 2012-09-28 | 2012-09-28 | Mechanical sealing device with self supporting type middle differential ring |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210367097.0A CN103697170A (en) | 2012-09-28 | 2012-09-28 | Mechanical sealing device with self supporting type middle differential ring |
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| CN103697170A true CN103697170A (en) | 2014-04-02 |
Family
ID=50358801
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|---|---|---|---|
| CN201210367097.0A Pending CN103697170A (en) | 2012-09-28 | 2012-09-28 | Mechanical sealing device with self supporting type middle differential ring |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104179975A (en) * | 2014-07-22 | 2014-12-03 | 西安电子科技大学 | Controllable mechanical seal based on closing force change |
| CN107830179A (en) * | 2017-11-16 | 2018-03-23 | 江苏大学 | A kind of annular seal assembly that can effectively improve rotor dynamic behavior |
| CN108333185A (en) * | 2018-03-30 | 2018-07-27 | 西华大学 | High-pressure hydrogen storing fuel tank outer surface quality real time detecting sensor |
| CN108799444A (en) * | 2018-08-30 | 2018-11-13 | 浙江工业大学 | Planetary differential radial double mechanical seal |
| CN114382894A (en) * | 2021-12-15 | 2022-04-22 | 清华大学 | Dynamic pressure type magnetic liquid sealing device |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108333185A (en) * | 2018-03-30 | 2018-07-27 | 西华大学 | High-pressure hydrogen storing fuel tank outer surface quality real time detecting sensor |
| CN108333185B (en) * | 2018-03-30 | 2023-06-02 | 西华大学 | Real-time detection sensor for quality of outer surface of high-pressure hydrogen storage fuel tank |
| CN108799444A (en) * | 2018-08-30 | 2018-11-13 | 浙江工业大学 | Planetary differential radial double mechanical seal |
| CN108799444B (en) * | 2018-08-30 | 2024-03-26 | 浙江工业大学 | Planetary differential radial double-end-face mechanical seal |
| CN114382894A (en) * | 2021-12-15 | 2022-04-22 | 清华大学 | Dynamic pressure type magnetic liquid sealing device |
| CN114382894B (en) * | 2021-12-15 | 2022-09-20 | 清华大学 | Dynamic pressure type magnetic liquid sealing device |
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Application publication date: 20140402 |