CN203321738U - Hydraulic brake stator-rotor assembly - Google Patents
Hydraulic brake stator-rotor assembly Download PDFInfo
- Publication number
- CN203321738U CN203321738U CN2013203827445U CN201320382744U CN203321738U CN 203321738 U CN203321738 U CN 203321738U CN 2013203827445 U CN2013203827445 U CN 2013203827445U CN 201320382744 U CN201320382744 U CN 201320382744U CN 203321738 U CN203321738 U CN 203321738U
- Authority
- CN
- China
- Prior art keywords
- stator
- rotor
- blades
- blade
- diameter
- 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
- 238000009434 installation Methods 0.000 claims description 4
- 241000411851 herbal medicine Species 0.000 claims description 2
- 238000005553 drilling Methods 0.000 abstract description 20
- 238000010586 diagram Methods 0.000 description 5
- 238000005516 engineering process Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 239000003245 coal Substances 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 239000011435 rock Substances 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 239000012224 working solution Substances 0.000 description 1
Images
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
Landscapes
- Hydraulic Turbines (AREA)
Abstract
The utility model discloses a hydraulic brake stator-rotor assembly. The hydraulic brake stator-rotor assembly comprises a rotor and a stator which are coaxially sheathed, the rotor comprises a cylindrical rotor body, a plurality of rotor blades and annular rotor blade tips, wherein a boss which is radially convex is arranged on the periphery at one end of the rotor body; the stator comprises a cylindrical stator body, a plurality of stator blade and annular stator blade tips; the inner walls of the stator blade tips and the outer wall of the rotor body are coaxially sheathed, the blade profiles of the stator blades and the rotor blades are straight blades, and the inclination angle of the stator blades and the inclination angle of the rotor blades are equal and are same in direction. The hydraulic brake stator-rotor assembly disclosed by the utility model has the advantages of simple structure, low brake pressure drop, appropriate brake torque, small hydraulic loss and long service life, and a certain number of hydraulic brake stators and rotors and a certain number of turbine stators and rotors are combined and assembled together, so that the idle speed and the working rotational speed of a turbine drilling tool can be significantly reduced, and the working time of the turbine drilling tool and the drilling depth of turbine drilling are increased.
Description
Technical Field
The utility model relates to a drilling or the creeping into of fields such as geology, railway, electric power, communication of fields such as oil, natural gas, coal bed gas, shale gas exploitation are with turbine drilling tool in the pit, especially a hydraulic braking level stator-rotor sub-assembly belongs to the mechanical manufacturing technology field.
Background
The turbine drilling tool is the earliest downhole hydraulic motor in industrial application, and is used for converting the hydraulic pressure energy of working fluid into mechanical energy to drive a drill bit to rotate so as to break down downhole rocks. The turbine drilling tool is a downhole power drilling tool commonly used in oil fields. Because the rotating speed of the turbine drilling tool consisting of the multistage turbine stator and rotor assembly is too high, a drill bit bearing or teeth are worn out too fast, and the drilling footage and the pure drilling time of one drill are much lower than those of rotary table drilling.
In view of the shortcoming that above-mentioned current turbine drilling technology exists, the utility model discloses the inventor is based on engaging in relevant scientific research and field test for a long time, improves actively and innovates prior art to realize a pressure drop and hang down, idle running rotational speed and operating speed are low, the moderate turbine drilling tool of working torque.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a simple structure, braking pressure drop are low, braking moment of torsion is moderate, hydraulic loss is little, longe-lived water conservancy braking level stator-rotor sub-assembly.
In order to achieve the above object, the utility model provides a hydraulic braking stage stator-rotor assembly, including coaxial sheathed rotor and stator, the rotor includes cylindrical rotor body, a plurality of rotor blades and annular rotor blade shroud, the one end periphery of the rotor body is provided with a boss protruding in the radial direction, the plurality of rotor blades are evenly distributed along the outer circumferential surface of the boss, the rotor blade shroud is sheathed on the outer edge of the rotor blade; the stator comprises a cylindrical stator body, a plurality of stator blades and a circular stator blade shroud, wherein the plurality of stator blades are uniformly distributed along the inner circumferential surface of the stator body, and the outer wall of the stator blade shroud is connected with the inner edges of the stator blades; the inner wall of the stator blade shroud is coaxially sleeved with the outer wall of the rotor body, the blade profiles of the stator blades and the rotor blades are straight blades, the center lines of the stator blades and the rotor blades respectively form an inclination angle with a plane perpendicular to the axes of the rotor and the stator, and the inclination angles of the stator blades and the rotor blades are equal in size and same in direction.
The hydraulic braking stage stator-rotor assembly as described above, wherein the axial height L of the stator and the rotor is 25mm to 55 mm.
The hydrobraking stage stator-rotor assembly as described above, wherein the axial height L of the rotor shroud1Axial height L of said stator shroud2Are equal, i.e. L1＝L28 mm-19 mm; axial height L of the rotor blade3Axial height L from the stator blade4Are equal, i.e. L3＝L48mm to 19mm, and L1＝L2≥L3＝L4。
The hydrobraking stage stator-rotor assembly as described above, wherein the inner circumferential diameter of the rotor shroud is equal to the inner circumferential diameter of the stator body and the inner circumferential diameter of the rotor shroud and the inner circumferential diameter of the stator body constitute a flowpath outer diameter D1(ii) a The diameter of the outer circumference of the boss of the rotor body is equal to the diameter of the outer circumference of the stator blade shroud, and the diameter of the outer circumference of the boss of the rotor body and the diameter of the outer circumference of the stator blade shroud form a flow channel inner diameter D2(ii) a The outer diameter D of the flow passage1And the inner diameter D of the flow passage2The arithmetic mean of (a) is the mean flow channel diameter D; the outer diameter D of the flow passage1And the inner diameter D of the flow passage2Half of the difference is the flow channel width h, which is (D)1-D2)/2＝7.0mm～15.0mm。
The hydrobraking stage stator-rotor assembly as described above, wherein the rotor blade pitch angle is the rotor blade setting angle β1The stator blade inclination angle is a stator blade installation angle beta2And β1＝β210 to 160 degrees; the average thickness of the rotor blade is c1, and the average thickness of the stator blade is c2And c is1＝c2＝1.0mm～5.0mm。
The hydrobraking stage stator-rotor assembly as described above, wherein the number of blades n of said rotor blade1Number n of blades of the stator blade2Are each n110 to 35 of n210-35 pieces of the Chinese herbal medicines; pitch t between two adjacent rotor blades1Pitch t between two adjacent stator blades2Are each t1＝5.0mm～10.0mm，t2＝5.0mm～10.0mm。
The hydrobraking stage stator-rotor assembly as described above, wherein the leading and trailing edges of the stator blades and the rotor blades are rectilinear or arcuate.
The utility model has the following characteristics and advantages:
the utility model discloses hydraulic braking level stator-rotor sub-assembly simple structure, braking pressure reduce, braking moment of torsion is moderate, hydraulic loss is little, longe-lived.
Drawings
The drawings are only intended to illustrate and explain the present invention and do not limit the scope of the invention. Wherein,
FIG. 1 is a schematic structural diagram of a first embodiment of a hydraulic braking stage stator-rotor assembly according to the present invention;
fig. 2 is a schematic cross-sectional view of a stator according to a first embodiment of the present invention;
fig. 3 is a schematic perspective view of a stator according to a first embodiment of the present invention;
fig. 4 is a schematic view of a stator vane according to a first embodiment of the present invention, which is expanded along a cylinder with an average diameter of a flow channel;
fig. 5 is a schematic cross-sectional structure view of a rotor according to a first embodiment of the present invention;
fig. 6 is a schematic perspective view of a rotor according to a first embodiment of the present invention;
fig. 7 is a schematic view of a rotor blade according to a first embodiment of the present invention expanded along a flow channel mean diameter cylinder;
FIG. 8 is a schematic structural view of a second embodiment of a hydraulic braking stage turbine stator-rotor assembly according to the present invention;
fig. 9 is a schematic sectional view of a stator according to a second embodiment of the present invention;
fig. 10 is a schematic perspective view of a stator according to a second embodiment of the present invention;
fig. 11 is a schematic view of the stator vane according to the second embodiment of the present invention expanded along the cylinder with the average diameter of the flow channel;
fig. 12 is a schematic sectional view of a rotor according to a second embodiment of the present invention;
fig. 13 is a schematic perspective view of a rotor according to a second embodiment of the present invention;
fig. 14 is a schematic view of a rotor blade according to a second embodiment of the present invention, expanded along a flow channel mean diameter cylinder.
Description of reference numerals:
1-example a rotor; 101-a rotor body; 102-a rotor blade; 103-rotor shroud; 104-boss;
2-example stator; 201-a stator body; 202-stator blades; 203-stator shroud;
3-example two rotors; 301-a rotor body; 302-rotor blades; 303-rotor shroud; 304-a boss;
4-example two stator; 401-a stator body; 402-stator vanes; 403-stator shroud.
Detailed Description
In order to clearly understand the technical features, objects, and effects of the present invention, embodiments of the present invention will be described with reference to the accompanying drawings.
Example one
Fig. 1 to 7 are schematic structural diagrams of a first embodiment of the hydraulic braking stage stator/rotor assembly according to the present invention, an embodiment of a stator sectional structure, an embodiment of a stator three-dimensional structure, an embodiment of a stator blade along a cylindrical surface of a mean diameter of a flow channel, an embodiment of a rotor sectional structure, an embodiment of a rotor three-dimensional structure, and an embodiment of a rotor blade along a cylindrical surface of a mean diameter of a flow channel.
As shown in fig. 1, the present invention provides a hydraulic braking stage stator-rotor assembly, which comprises a rotor 1 and a stator 2 coaxially sleeved. As shown in fig. 2 and 3, the stator 2 includes a cylindrical stator body 201, a plurality of stator blades 202, and an annular stator shroud 203, the plurality of stator blades 202 are uniformly distributed along an inner circumferential surface of the stator body 201, and an outer wall of the stator shroud 203 is connected to an inner edge of the stator blade 202, so that the stator body 201, the plurality of stator blades 202, and the stator shroud 203 form the stator 2 of an integrated structure. As shown in fig. 5, the rotor 1 includes a cylindrical rotor body 101, a plurality of rotor blades 102, and an annular rotor shroud 103, wherein a radially protruding boss 104 is disposed on an outer periphery of one end of the rotor body 101, the plurality of rotor blades 102 are uniformly distributed along an outer circumferential surface of the rotor body 101, and the rotor shroud 103 is sleeved on an outer edge of the rotor blade 102, so that the rotor body 101, the blades 102, and the rotor shroud 103 form the rotor 1 of an integrated structure. As shown in fig. 1, the inner wall of the stator shroud 203 is fitted with the outer wall of the rotor body 101, and the stator body 201 is coaxial with the central axis of the rotor body 101, that is, the inner wall of the stator shroud 203 is fitted with the outer wall of the rotor body 101, so that the stator 2 is fitted with the rotor 1. As shown in fig. 4 and 7, the profiles of the stator blade 202 and the rotor blade 102 are straight blades (straight lines), the center line of the stator blade 202 and the center line of the rotor blade 102 respectively form a certain inclination angle with a plane perpendicular to the axes of the rotor 1 and the stator 2, and the inclination angle of the stator blade 202 is equal to the inclination angle of the rotor blade 102 in the same direction.
Further, as shown in fig. 1, 2 and 5, the axial heights L of the stator 2 and the rotor 1 of the hydraulic braking stage are 25mm to 55 mm; for easy installation and use, the outer diameter D of the stator of the hydraulic braking stageseInner diameter D of the rotor of the hydraulic brake stage, which is the same as the outer diameter of the stator of the turbine stageriThe same as the turbine stage rotor inner diameter.
Further, as shown in FIGS. 1, 2, and 5, the axial height L of the rotor shroud 103 of the hydrodynamic braking stage1Axial height L of stator blade shroud 2032Are equal, i.e. L1＝L28 mm-19 mm; axial height L of rotor blade 1023Axial height L from stator blade 2024Are equal, i.e. L3＝L48mm to 19mm, and L1＝L2≥L3＝L4So as to be convenient for installation and processing.
Further, as shown in fig. 1, 2 and 5, the inner ring channel of the hydrodynamic braking stage rotor shroud 103 and the inner circumferential wall of the stator body 201 form a liquid flow passage. The diameter of the inner circumference of the rotor shroud 103 is equal to the diameter of the inner circumference of the stator body 201 and the diameter of the inner circumference of the rotor shroud 103 and the diameter of the inner circumference of the stator body 201 form the outer diameter D of the flow passage1(ii) a The outer circumferential diameter of the boss 104 of the rotor body 101 is equal to the outer circumferential diameter of the stator shroud 203 and the outer circumferential diameter of the boss 104 of the rotor body 101 and the outer circumferential diameter of the stator shroud 203 constitute a flow passage inner diameter D2(ii) a Outer diameter D of flow channel1And the inner diameter D of the flow passage2The arithmetic mean of (a) is the mean flow channel diameter D; outer diameter D of flow channel1And the inner diameter D of the flow passage2Half of the difference is the flow channel width h, which is (D)1-D2) 7.0 mm-15.0 mm is defined as/2; advice D1And D2The value of (A) is the same as the inner and outer diameters of the turbine stage stator and rotor flow passage.
Further, as shown in FIGS. 4 and 7, the profiles of the stator blades 202 and the rotor blades 102 of the hydrodynamic braking stage are straight blades, the center line of the stator blades 202 and the center line of the rotor blades 102The rotor blade 102 centerline forms the same pitch angle with a plane perpendicular to the stator and rotor axes, i.e., the stator blade 202 stagger angle β2Angle of incidence beta with rotor blade 1021Equal, the value range is less than or equal to beta in 10 degrees1＝β2< 90 °; stator blade 202 average thickness c2And the average thickness c of the rotor blade 1011Equal, value range c1＝c2＝c＝1.0mm～5.0mm。
Further, the number n of the stator vanes 202 of the hydrodynamic braking stage2Number n of blades corresponding to the number of the rotor blades 1021Are each n110 to 35 of n210 ~ 35 to satisfy different operating mode demands. As shown in fig. 4 and 7, the pitch t between two adjacent stator blades 2022Or pitch t between two adjacent rotor blades 1021Are each t1＝5.0mm～10.0mm，t2＝5.0mm～10.0mm。
The utility model discloses when using, the extension that the blade 102 of hydraulic braking stage rotor 1 is equal to the blade 202 of stator 2 (stator blade is the same with rotor blade's angle of erection), and when hydraulic braking stage stator-rotor sub-assembly and turbine stage stator-rotor sub-assembly install on same root main shaft, when the stator-rotor sub-assembly was flowed through to the working solution, turbine stage rotor was rotatory and produce the moment of torsion, and hydraulic braking stage rotor is driven rotatoryly. Since the inclination direction of the stator blades of the brake stage is opposite to that of the stator blades of the turbine stage, the working fluid flowing out of the stator of the brake stage can block the rotation of the rotor blades of the brake stage, i.e. the main shaft of the turbine drilling tool can not generate working torque and consumes the torque, so that the rotating speed of the main shaft is reduced. Meanwhile, when the hydraulic braking stage rotor rotates, the working wheel of the axial flow pump is arranged, the working wheel can assist the drilling pump to pressurize the working liquid, and the function of adjusting the pressure of the system is achieved.
To sum up, the utility model discloses an above-mentioned structural design for the hydraulic braking level decides the rotor sub-assembly and can reduce turbine drilling tool idling speed, makes turbine drilling tool operating speed region narrow, has improved the overload capacity of turbine drilling tool.
Example two
Fig. 8 to fig. 14 are schematic structural diagrams of a second embodiment of the hydraulic braking stage turbine stator/rotor assembly according to the present invention, a schematic sectional structure of a second stator according to the second embodiment, a schematic perspective structure of a second stator according to the second embodiment, a schematic expansion diagram of a second stator blade according to the second embodiment along a cylindrical surface of an average diameter of a flow channel, a schematic sectional structure of a second rotor according to the second embodiment, a schematic perspective structure of a second rotor according to the second embodiment, and a schematic expansion diagram of a second rotor blade according to the second embodiment along a cylindrical surface of an average.
In this embodiment, the rotor 3 of the hydrodynamic braking stage stator-rotor assembly comprises a rotor body 301, rotor blades 302, a rotor shroud 303 and a boss 304; the stator 4 includes a stator body 401, stator blades 402, and a stator shroud 403. The difference between the present embodiment and the first embodiment is that the leading edge and the trailing edge of the blade are not straight lines, but are circular arcs (the circular arc radius r is 0.5c sin β), and the circular arcs of the leading edge and the trailing edge are respectively tangent to the blade back and the blade basin profile, so that the hydraulic loss of the brake stage can be greatly reduced. The radius of the leading edge of the blade is r1Trailing edge radius r2Range of values r1＝0.5～2.5mm，r2＝0.5～2.5mm。
The above description is only exemplary of the present invention, and is not intended to limit the scope of the present invention. Any person skilled in the art should also realize that such equivalent changes and modifications can be made without departing from the spirit and principles of the present invention.
Claims (7)
1. A hydraulic brake stage stator-rotor assembly, comprising a rotor and a stator coaxially sleeved, characterized in that: the rotor comprises a cylindrical rotor body, a plurality of rotor blades and a circular rotor blade shroud, wherein a boss protruding in the radial direction is arranged on the periphery of one end of the rotor body, the plurality of rotor blades are uniformly distributed along the outer circumferential surface of the boss, and the rotor blade shroud is sleeved on the outer edge of the rotor blade; the stator comprises a cylindrical stator body, a plurality of stator blades and a circular stator blade shroud, wherein the plurality of stator blades are uniformly distributed along the inner circumferential surface of the stator body, and the outer wall of the stator blade shroud is connected with the inner edges of the stator blades; the inner wall of the stator blade shroud is coaxially sleeved with the outer wall of the rotor body, the blade profiles of the stator blades and the rotor blades are straight blades, the center lines of the stator blades and the rotor blades respectively form an inclination angle with a plane perpendicular to the axes of the rotor and the stator, and the inclination angles of the stator blades and the rotor blades are equal in size and same in direction.
2. The hydrobrake stage stator-rotor assembly according to claim 1, wherein: the axial height L of the stator and the rotor is 25-55 mm.
3. The hydrobrake stage stator-rotor assembly according to claim 1, wherein: axial height L of the rotor shroud1Axial height L of said stator shroud2Are equal, i.e. L1＝L28 mm-19 mm; axial height L of the rotor blade3Axial height L from the stator blade4Are equal, i.e. L3＝L48mm to 19mm, and L1＝L2≥L3＝L4。
4. The hydrobrake stage stator-rotor assembly according to claim 1, wherein: the diameter of the inner circumference of the rotor shroud is equal to the diameter of the inner circumference of the stator body and the diameter of the inner circumference of the rotor shroud and the diameter of the inner circumference of the stator body form the outer diameter D of the flow passage1(ii) a The diameter of the outer circumference of the boss of the rotor body is equal to the diameter of the outer circumference of the stator blade shroud, and the diameter of the outer circumference of the boss of the rotor body and the diameter of the outer circumference of the stator blade shroud form a flow channel inner diameter D2(ii) a The outer diameter D of the flow passage1And the inner diameter D of the flow passage2The arithmetic mean of (a) is the mean flow channel diameter D; the outer diameter D of the flow passage1And the inner diameter D of the flow passage2Half of the difference is the flow channel width h, which is (D)1-D2)/2＝7.0mm～15.0mm。
5. The hydrobrake stage stator-rotor assembly according to claim 1, wherein: the inclination angle of the rotor blade is a rotor blade mounting angle beta1The stator blade inclination angle is a stator blade installation angle beta2And β1＝β210 to 160 degrees; the average thickness of the rotor blade is c1The average thickness of the stator blade is c2And c is1＝c2＝1.0mm～5.0mm。
6. The hydrobrake stage stator-rotor assembly according to claim 1, wherein: the number n of the blades of the rotor blade1Number n of blades of the stator blade2Are each n110 to 35 of n210-35 pieces of the Chinese herbal medicines; pitch t between two adjacent rotor blades1Pitch t between two adjacent stator blades2Are each t1＝5.0mm～10.0mm，t2＝5.0mm～10.0mm。
7. The hydrobrake stage stator-rotor assembly according to any one of claims 1 to 6, wherein: the leading edges and the trailing edges of the stator blades and the rotor blades are linear or circular arc-shaped.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013203827445U CN203321738U (en) | 2013-06-28 | 2013-06-28 | Hydraulic brake stator-rotor assembly |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013203827445U CN203321738U (en) | 2013-06-28 | 2013-06-28 | Hydraulic brake stator-rotor assembly |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203321738U true CN203321738U (en) | 2013-12-04 |
Family
ID=49661095
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013203827445U Expired - Fee Related CN203321738U (en) | 2013-06-28 | 2013-06-28 | Hydraulic brake stator-rotor assembly |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203321738U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104047795A (en) * | 2014-07-03 | 2014-09-17 | 中国石油大学(北京) | Point-projection wedge-shaped blade brake-stage stator and rotor assembly |
| CN104179622A (en) * | 2014-08-08 | 2014-12-03 | 中国石油大学(北京) | Braking level stator-rotor assembly provided with sweeping wedge-shaped blades |
-
2013
- 2013-06-28 CN CN2013203827445U patent/CN203321738U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104047795A (en) * | 2014-07-03 | 2014-09-17 | 中国石油大学(北京) | Point-projection wedge-shaped blade brake-stage stator and rotor assembly |
| CN104179622A (en) * | 2014-08-08 | 2014-12-03 | 中国石油大学(北京) | Braking level stator-rotor assembly provided with sweeping wedge-shaped blades |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103711631B (en) | Line projection's blade turbine rotor assembly parts and turbine motor | |
| CN202520472U (en) | Stator and rotor combination piece of turbine, and turbine motor | |
| CN203321738U (en) | Hydraulic brake stator-rotor assembly | |
| GB2431944A (en) | Turbodrill | |
| CN101776087B (en) | Rotation shell pump adopting spiral labyrinth dynamic seal | |
| RU2647016C2 (en) | Stator and rotor assembly of the turbine and turbine engine | |
| CN103939008B (en) | Line projection's blade activation level rotor composite member | |
| CN203308640U (en) | Turbine stator and rotor assembly and turbine motor | |
| CN204419688U (en) | A kind of centrifugal pump composite impeller | |
| KR20150044754A (en) | Blade bucket structure savonius turbine | |
| CN103334864A (en) | Turbine motor with hydraulic braking level stator and rotor components | |
| CN108691717B (en) | Mixed-flow water turbine with double rotating wheels | |
| CN204025142U (en) | A kind of impeller is biased the torque flow pump of band lordosis impeller | |
| CN204140259U (en) | Spot projection blade turbine rotor assembly parts and turbine motor | |
| CN204140257U (en) | Spot projection Wedge-shaped blade activation level rotor assembly parts | |
| CN203308648U (en) | Turbine motor with hydraulic brake stage stator-rotor assembly | |
| CN201739221U (en) | Rotary-shell pump adopting rectangular spiral labyrinth dynamic sealing on impeller hub | |
| CN104454024B (en) | A kind of multi-level centripetal turbine formula turbine section | |
| CN108005834A (en) | A kind of flow type centripetal turbine | |
| CN104632506A (en) | Double-impeller driving axial-flow type water turbine generator set | |
| CN109681462B (en) | Reversible axial-flow pump impeller adopting elliptical-tip combined wing type | |
| CN108266301A (en) | tubular turbine with rotating cylinder | |
| CN207539044U (en) | A kind of high-speed permanent magnetic electromechanical integral pump | |
| CN203867763U (en) | Telescopic wedge-shaped blade brake-stage stator and rotor assembly | |
| CN203962275U (en) | Scan Wedge-shaped blade retrostage rotor assembly parts |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20131204 |
|
| CU01 | Correction of utility model | ||
| CU01 | Correction of utility model |
Correction item: Termination upon expiration of patent Correct: Revocation of Patent Expiration and Termination False: On July 14, 2023, the expiration and termination of 39 volumes and 2802 issues of the patent Number: 28-02 Volume: 39 |
|
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20131204 |