CN115182829A - Large-pressure-difference high-rotation-speed floating ring sealing test bench - Google Patents
Large-pressure-difference high-rotation-speed floating ring sealing test bench Download PDFInfo
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- CN115182829A CN115182829A CN202210835991.XA CN202210835991A CN115182829A CN 115182829 A CN115182829 A CN 115182829A CN 202210835991 A CN202210835991 A CN 202210835991A CN 115182829 A CN115182829 A CN 115182829A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02K—JET-PROPULSION PLANTS
- F02K9/00—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof
- F02K9/96—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof characterised by specially adapted arrangements for testing or measuring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0088—Testing machines
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- General Engineering & Computer Science (AREA)
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- Combustion & Propulsion (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A large-pressure-difference high-rotation-speed floating ring sealing test bench relates to the field of aerospace. The invention solves the problems that the existing test bed for testing the floating ring seal of the rocket turbopump directly pressurizes a high-pressure chamber by adopting a water supply pump, has limited pressurizing capacity and can not meet the sealing test of the floating ring with large pressure difference and high rotating speed. The center of the right end face of the rotor is axially provided with a hollow water supply hole with the depth reaching the center of the wheel disc, the right end of the hollow water supply hole is communicated with a pressure-bearing water tank, a plurality of water throwing holes tangent to the hollow water supply hole are uniformly processed in the wheel disc along the circumferential direction, a plurality of balance holes corresponding to the water throwing holes one by one are processed on the outer edge face of the wheel disc along the circumferential direction, two ends of each water throwing hole are respectively communicated with the corresponding hollow water supply hole and the corresponding balance hole, and a left water collecting cavity and a right water collecting cavity are in working medium circulation with the pressure-bearing water tank through a water circulation system. The invention is used for providing a required test environment for the floating ring test.
Description
Technical Field
The invention relates to the field of aerospace, in particular to a test bed for testing the sealing and dynamic response of a turbopump of a liquid rocket engine, and specifically relates to a large-pressure-difference high-rotation-speed floating ring sealing test.
Background
In the process installations in the modern aerospace industry sector, seals are of crucial importance because of the harsh operating conditions of the mechanical equipment. The sealing technology not only directly influences the normal operation of the fluid machinery due to the performance of the product, but also considers the sealing technology as the category of comprehensive engineering, has special significance for improving the integral sealing level of the machine, and is particularly important for the rotating machinery in the aerospace field.
The liquid rocket engine turbine is used for boosting an oxidant and a fuel through a turbine pump and then pushing the oxidant and the fuel into a combustion chamber, and the gap seal is a key component for controlling the leakage of the turbine pump and is directly related to the working efficiency and the operation stability of the liquid rocket engine. Under the severe environment of high rotating speed, large pressure difference, ultralow temperature and ultrahigh temperature in the turbopump of the liquid rocket engine, various contact sealing technologies such as brush sealing and flexible sheet sealing are difficult to meet the working requirements. Due to the existence of objective factors such as machining errors, dynamic bending and thermal deformation, the vibration of the rotor often causes the surface of the rotor to collide with the fixed clearance seal wall surface, and the sealing is failed. Under the oxygen-rich environment in the turbopump of the liquid oxygen liquid rocket engine, the contact and friction between the rotor and the stator part easily cause the oxygen-rich combustion of metal, and the reliability of the liquid rocket engine is reduced. The floating gap seal is a gap sealing element which can move relative to the rotor, has the function of self-centering relative to the rotor, and can be far smaller than the fixed gap seal in gap height, so that the leakage of a working medium is remarkably reduced. And the clearance sealing fluid can provide certain rigidity and damping for the rotor system, and the stability of the rotor system of the turbine pump can be improved.
The floating ring has a series of advantages of simple structure, reliable sealing, easy installation, adaptation to harsh environment and the like, and is widely applied to liquid rocket engines in the aerospace field in recent years. The floating clearance sealing technology with high sealing efficiency and high operation stability is an effective and most economical key technology for further improving the operation reliability of the liquid rocket engine. At present, a systematic theoretical method and a systematic simulation basis exist for the floating clearance seal, but the floating clearance seal leakage amount under high rotating speed and large pressure difference, and the dynamic response and operation stability technology of the floating ring structure need to be further researched in the aspect of tests.
The invention discloses a test bed for testing the sealing of a floating ring of a rocket turbopump, which is disclosed by Chinese invention patent with the publication number of CN111636981A and the publication date of 2020, 9, 8. According to the floating ring sealing test bench, the front cavity and the rear cavity of the high-pressure cavity forming the floating ring work are provided with the pore passages communicated with the floating ring channel, the water supply pump is adopted to directly pressurize the high-pressure cavity through the pore passages, the pressure value in the high-pressure cavity is directly determined by the pressurization value of the water supply pump due to the pressurization mode, the maximum pressure value which can be provided by the water supply pump is relatively small due to the limited pressurization capacity of the water supply pump, 1.5-2.5MPa sealing pressure difference can be provided for the floating ring test, and the large-pressure-difference and high-rotating-speed floating ring sealing test cannot be met.
Disclosure of Invention
The invention aims to solve the problems that the existing test bed for testing the floating ring seal of the rocket turbopump directly pressurizes a high-pressure chamber by adopting a water supply pump, has limited pressurizing capacity and cannot meet the sealing test of the floating ring with large pressure difference and high rotating speed, and further provides the test bed for testing the floating ring seal with large pressure difference and high rotating speed.
The technical scheme of the invention is as follows:
a large-pressure-difference high-rotation-speed floating ring sealing test bed comprises a floating ring testing and pressurizing integrated device 4, a driving mechanism for providing power for the floating ring testing and pressurizing integrated device 4, a data acquisition and control system 5 for acquiring measurement parameters required by the floating ring testing, a pressure-bearing water tank 8, a water circulation system for providing a testing medium for the floating ring testing, two supporting assemblies 3 and a cooling and lubricating system 10 for cooling and lubricating the supporting assemblies 3 and the driving mechanism; the floating ring testing and pressurizing integrated device 4 comprises a floating ring testing cavity, a left water collecting cavity 4-8, a right water collecting cavity 4-18, a rotor 4-19 and two floating ring testing pieces 4-17, wherein the left side and the right side of the floating ring testing cavity are respectively connected with the left water collecting cavity 4-8 and the right water collecting cavity 4-18, the left end of the rotor 4-19 sequentially axially penetrates through the left half part of the floating ring testing cavity and the left water collecting cavity 4-8 and is fixedly connected with the output end of a driving mechanism, the right end of the rotor 4-19 sequentially axially penetrates through the right half part of the floating ring testing cavity and the right water collecting cavity 4-18 and is rotatably connected with a pressure-bearing water tank 8, two supporting components 3 for supporting the rotors 4 to 19 are respectively arranged between the left water collecting cavity 4 to 8 and the driving mechanism and between the right water collecting cavity 4 to 18 and the pressure-bearing water tank 8, a wheel disc is processed in the middle of the rotors 4 to 19, floating ring contact surfaces are respectively processed on the rotors 4 to 19 on two sides of the wheel disc, the floating ring contact surfaces on two sides of the wheel disc and the transition part of the outer edge of the wheel disc are both processed into cones, floating ring test pieces 4 to 17 are sleeved on the floating ring contact surfaces on two sides of the wheel disc, the wheel disc and the two floating ring test pieces 4 to 17 are respectively arranged in a sealing cavity of the floating ring test cavity, and the wall surface of the sealing cavity of the floating ring test cavity is used for the stator end wall contacted with a floating ring boss; the center of the right end face of the rotor 4-19 is axially provided with a hollow water supply hole 4-19.1 with the depth reaching the center of the wheel disc, the right end of the hollow water supply hole 4-19.1 is communicated with the pressure-bearing water tank 8, the inside of the wheel disc is uniformly provided with a plurality of water throwing holes 4-19.2 tangent to the hollow water supply hole 4-19.1 along the circumferential direction, the outer edge face of the wheel disc is provided with a plurality of balance holes corresponding to the water throwing holes 4-19.2 one by one, two ends of each water throwing hole 4-19.2 are respectively communicated with the corresponding hollow water supply hole 4-19.1 and the balance hole, and the left water collecting cavity 4-8 and the right water collecting cavity 4-18 are communicated with the pressure-bearing water tank 8 through a water circulation system to perform working medium circulation.
Further, the floating ring testing cavity comprises a left high-pressure cavity 4-13, a spring sealing ring 4-14, a right high-pressure cavity 4-15, a testing table base 4-24 and a plurality of stud through bolts 4-16, the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15 are arranged above the testing table base 4-24 in parallel and oppositely, the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15 are fixedly connected through the plurality of stud through bolts 4-16, the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15 are sealed through the spring sealing ring 4-14, and the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15 are respectively and fixedly connected with the testing table base 4-24.
Further, the data acquisition and control system 5 comprises four first eddy current displacement sensors 4-12 for measuring the movement tracks of the floating ring test pieces 4-17, the first eddy current displacement sensors 4-12 are pressure-resistant eddy current displacement sensors, two high-pressure cavity connection threaded holes are respectively machined on the outer arc surfaces of the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15 in a 90-degree circumferential direction, the floating ring test cavity further comprises four thread sleeves 4-11, four displacement sensor locking nuts, four thread sleeves 4-11 and four displacement sensor locking nuts, the outer cylindrical surfaces of the thread sleeves 4-11 are integrally machined into external threads, the thread sleeves 4-11 are spirally installed in the high-pressure cavity connection threaded holes and fixed on the floating ring test cavity through the displacement sensor locking nuts, diameter-variable through holes are machined inside the thread sleeves 4-11, the lower half portions of the diameter-variable through holes are machined into displacement sensor connection threaded holes and provided with spigot positioning, the upper half portions of the diameter-variable through holes are machined into through holes, the pressure-resistant eddy current displacement sensors are spirally installed in the thread holes and sealed through a pressure-resistant eddy current displacement sensor connection threaded holes, the pressure-resistant eddy current displacement sensors are directed to the outer floating ring test cavity, and the pressure-resistant eddy current displacement sensors.
Furthermore, the water circulation system comprises a water supply pump 6, a water storage tank 7 and a water return pump 9, wherein a water inlet pipeline of the water supply pump 6 is connected with the water storage tank 7, a water outlet pipeline of the water supply pump 6 is connected with a pressure-bearing water tank 8, a water inlet pipeline of the water return pump 9 is respectively connected with a left water collecting cavity 4-8 and a right water collecting cavity 4-18 through a three-way valve, a water outlet pipeline of the water return pump 9 is connected with the water storage tank 7, a working medium in the water storage tank 7 is pressurized by the water supply pump 6 and then conveyed into the pressure-bearing water tank 8, the pressure-bearing water tank 8 is connected with the right end of a hollow water supply hole 4-19.1 of a rotor 4-19 in the floating ring testing and pressurizing integrated device 4, and is discharged into the water storage tank 7 through the water return pump 9 after the floating ring sealing test, so that the circulation of the working medium is realized.
Further, the floating ring testing and pressurizing integrated device 4 further comprises a water tank end filler seal 4-22 and two water collecting cavity end filler seals 4-7, axial sealing is achieved between the left water collecting cavity 4-8 and the rotor 4-19 and between the right water collecting cavity 4-18 and the rotor 4-19 through the two water collecting cavity end filler seals 4-7 respectively, and axial sealing is achieved between the pressure-bearing water tank 8 and the rotor 4-19 through the water tank end filler seal 4-22.
Furthermore, the data acquisition and control system 5 also comprises four second eddy current displacement sensors 4-9 for measuring the movement tracks of the rotors 4-19, two displacement sensor mounting holes are respectively processed on the outer arc surfaces of the left water collection cavity 4-8 and the right water collection cavity 4-18 in a circumferential direction of 90 degrees, the second eddy current displacement sensors 4-9 are mounted in the displacement sensor mounting holes and sealed through sealing glue, and probes of the second eddy current displacement sensors 4-9 point to the rotors 4-19.
Further, the data acquisition and control system 5 also comprises turbine flow meters 4-23 for measuring the leakage amount of the floating ring, and the turbine flow meters 4-23 are arranged between the water supply pump 6 and the pressure-bearing water tank 8.
Further, the data acquisition and control system 5 further comprises four pressure sensors 4-10, two pressure sensors 4-10 are respectively installed in the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15, wherein one pressure sensor 4-10 is used for monitoring the fluid pressure at the top of the inner disk of the left high-pressure cavity 4-13 or the right high-pressure cavity 4-15, and the other pressure sensor 4-10 is used for monitoring the fluid pressure at the installation position of the floating ring test piece 4-17 in the left high-pressure cavity 4-13 or the right high-pressure cavity 4-15.
Further, the data acquisition and control system 5 also comprises a rotating speed measuring instrument 4-25 for measuring the rotating speed of the rotor 4-19, and the rotating speed measuring instrument 4-25 is arranged at one end of the rotor 4-19 close to the driving mechanism.
Furthermore, the supporting component 3 comprises a bearing seat, a bearing closing cover 4-3, a bearing locking nut 4-4, a bearing closing chamber 4-6, two bearing end covers 4-2 and two angular contact bearings 4-5, a circular through hole is processed on the bearing seat, two oil guide ring grooves are processed on the inner wall of the circular through hole of the bearing seat along the circumferential direction, oil outlet holes are processed on the left side end surface of the bearing seat of the oil guide ring grooves along the axial direction, the oil outlet is respectively communicated with the two oil guide ring grooves through two oil ways, the bearing closing chamber 4-6 is coaxially arranged in the circular through hole of the bearing seat, the end surface of one side of the bearing closing chamber 4-6, which is close to the left water collecting cavity 4-8, is provided with a shaft hole which is rotatably matched with the rotor 4-19, the end part of one side of the bearing closing chamber 4-6, which is close to the driving mechanism, is provided with a bearing closing cover 4-3, an oil pipe assembly hole is processed in the bearing sealing cover 4-3, two angular contact bearings 4-5 which are arranged side by side are coaxially installed in a bearing sealing chamber 4-6, the angular contact bearings 4-5 and the bearing sealing chamber 4-6 are integrally sleeved on the rotor 4-19, one end of each angular contact bearing 4-5 is axially positioned through a coaxial shaft shoulder, the other end of each angular contact bearing 4-5 is axially positioned through a bearing locking nut 4-4, the two bearing end covers 4-2 which are positioned on two sides of the bearing seat are both sleeved on the rotor 4-19, the bearing end covers 4-2 are connected with the bearing seat through connecting screws, and an oil pipe joint 4-1 sequentially penetrates through the bearing end covers 4-2 and the bearing sealing cover 4-3 and is communicated with a bearing sealing cavity formed by the bearing sealing chamber 4-6 and the bearing sealing cover 4-3.
Compared with the prior art, the invention has the following effects:
the invention provides a large-pressure-difference high-rotation-speed floating ring sealing test bed for better clarifying the influence rule of the parameters and the operation working conditions of the existing floating ring sealing structure on the operation state of a floating ring of a large-pressure-difference high-rotation-speed turbine pump. The test bed is used for realizing the leakage rate of the floating ring seal of the turbopump of the liquid rocket engine, the dynamic response of the floating ring structure and the test of the running stability. The working medium is pressurized by the water supply pump 6 for the first time and then injected into the pressure-bearing water tank 8, the working medium axially enters the hollow liquid supply holes 4-19.1 of the rotors 4-19 and is filled in the rotors 4-19, the liquid throwing holes 4-19.2 in the wheel disc drive the working medium to flow towards the outer edge of the wheel disc due to the rapid rotation of the wheel disc, so that the liquid throwing holes 4-19.2 do work on the working medium, the kinetic energy and the pressure energy of the working medium are increased at the moment, the secondary pressurization of the working medium is realized by the deceleration and pressurization after passing through the shell of the floating ring test cavity, and the working pressure required by the sealing inlet of the floating ring 4-17 is reached. The floating ring sealing test bench can provide at least 6MPa of sealing pressure difference and 18000rpm of rotation speed for testing the floating ring, can provide accurate parameters and technical guarantee for researching the leakage rate of the floating ring of the turbine pump of the liquid rocket engine, the dynamic response of the floating ring structure and the operation stability, has various test capabilities, and provides technical support for the design of the floating ring gap sealing of the turbine pump.
Drawings
FIG. 1 is a flow chart of the system components of a large differential pressure, high rotational speed floating ring seal test rig according to the present invention;
FIG. 2 is a main sectional view of a large differential pressure, high speed floating ring seal test stand body of the present invention;
FIG. 3 is an axial cross-sectional view of a floating ring seal dynamic response test position in accordance with a third embodiment of the present invention;
FIG. 4 is a schematic structural view of the assembled pressurized water tank 8, floating ring test pieces 4-17 and rotors 4-19 of the present invention;
FIG. 5 isbase:Sub>A cross-sectional view at A-A of FIG. 4;
FIG. 6 is a perspective view of a large differential pressure, high speed floating ring seal test rig of the present invention.
In the figure:
1 is a driving motor; 2 is a gear box; 3 is a supporting component; 4, a floating ring testing and pressurizing integrated device; 5 is a data acquisition and control system; 6 is a water supply pump; 7 is a water storage tank; 8 is a pressure-bearing water tank; 9 is a water return pump; 10 is a cooling and lubricating system;
4-1 is an oil pipe joint; 4-2 is a bearing end cover; 4-3 is a bearing closing cover; 4-4 is a bearing lock nut; 4-5 are angular contact bearings; 4-6 is a bearing closed chamber; 4-7 is a water collecting cavity end packing seal; 4-8 is a left water collecting cavity; 4-9 is a second eddy current displacement sensor; 4-10 are pressure sensors; 4-11 is a thread sleeve; 4-12 are first eddy current displacement sensors; 4-13 is a left high-pressure cavity; 4-14 are elastic sealing rings; 4-15 is a right high-pressure cavity; 4-16 are stud through bolts; 4-17 are floating ring test pieces; 4-18 is a right water collecting cavity; 4-19 are rotors; 4-20 is a disc spring; 4-21 is labyrinth seal; 4-22 is water tank end packing seal; 4-23 turbine flow meters; 4-24 are test bed bases; 4-25 is a rotating speed tester;
4-19.1 are hollow water supply holes; 4-19.2 are water throwing holes.
Detailed Description
The first embodiment is as follows: the embodiment is described with reference to fig. 1 to 6, and the large-pressure-difference high-rotation-speed floating ring sealing test bench of the embodiment comprises a floating ring testing and pressurizing integrated device 4, a driving mechanism for providing power for the floating ring testing and pressurizing integrated device 4, a data acquisition and control system 5 for acquiring measurement parameters required by the floating ring testing, a pressure-bearing water tank 8, a water circulation system for providing a testing medium for the floating ring testing, two supporting assemblies 3 and a cooling and lubricating system 10 for cooling and lubricating the supporting assemblies 3 and the driving mechanism; the floating ring testing and pressurizing integrated device 4 comprises a floating ring testing cavity, a left water collecting cavity 4-8, a right water collecting cavity 4-18, a rotor 4-19 and two floating ring testing pieces 4-17, wherein the left side and the right side of the floating ring testing cavity are respectively connected with the left water collecting cavity 4-8 and the right water collecting cavity 4-18, the left end of the rotor 4-19 sequentially axially penetrates through the left half part of the floating ring testing cavity and the left water collecting cavity 4-8 and is fixedly connected with the output end of a driving mechanism, the right end of the rotor 4-19 sequentially axially penetrates through the right half part of the floating ring testing cavity and the right water collecting cavity 4-18 and is rotatably connected with a pressure-bearing water tank 8, two supporting components 3 for supporting the rotors 4 to 19 are respectively arranged between the left water collecting cavity 4 to 8 and the driving mechanism and between the right water collecting cavity 4 to 18 and the pressure-bearing water tank 8, a wheel disc is processed in the middle of the rotors 4 to 19, floating ring contact surfaces are respectively processed on the rotors 4 to 19 on two sides of the wheel disc, the floating ring contact surfaces on two sides of the wheel disc and the transition part of the outer edge of the wheel disc are both processed into cones, floating ring test pieces 4 to 17 are sleeved on the floating ring contact surfaces on two sides of the wheel disc, the wheel disc and the two floating ring test pieces 4 to 17 are respectively arranged in a sealing cavity of the floating ring test cavity, and the wall surface of the sealing cavity of the floating ring test cavity is used for the stator end wall contacted with a floating ring boss; the center of the right end face of the rotor 4-19 is axially provided with a hollow water supply hole 4-19.1 with the depth reaching the center of the wheel disc, the right end of the hollow water supply hole 4-19.1 is communicated with the pressure-bearing water tank 8, the inside of the wheel disc is uniformly provided with a plurality of water throwing holes 4-19.2 tangent to the hollow water supply hole 4-19.1 along the circumferential direction, the outer edge face of the wheel disc is provided with a plurality of balance holes corresponding to the water throwing holes 4-19.2 one by one, two ends of each water throwing hole 4-19.2 are respectively communicated with the corresponding hollow water supply hole 4-19.1 and the balance hole, and the left water collecting cavity 4-8 and the right water collecting cavity 4-18 are communicated with the pressure-bearing water tank 8 through a water circulation system to perform working medium circulation.
In the embodiment, the driving mechanism comprises a driving motor 1 and a gear box 2, an output shaft of the driving motor 1 is connected with the gear box 2, an output shaft of the gear box 2 is connected with rotors 4-19 of the floating ring testing and pressurizing integrated device through a diaphragm coupler to provide power for the test bed, and the rotating speed of the driving motor 1 is controlled by a frequency converter to meet the requirement of testing the rotating speed. The gearbox 2, the rotor 4-19, the supporting component 3, the floating ring testing cavity, the left water collecting cavity 4-8, the right water collecting cavity 4-18 and the pressure-bearing water tank 8 are arranged on the same axis. The floating ring testing and pressurizing integrated device 4 is symmetrical in overall structure, the pressure in the floating ring testing cavity is balanced and stable, and the sealing inlet pressure and the rotating speed of the rotor 4-19 are controllable, so that the floating ring testing under various working conditions is met. The pressure-bearing water tank 8 is serially arranged in the axial water supply ends of the rotors 4 to 19, and the distance between the axial water supply ends makes the end part of the rotor flush with the pressure-bearing water tank 8. The number of the liquid throwing holes 4-19.2 and the balance holes on the wheel disc of the rotor 4-19 is 8.
The second embodiment is as follows: the embodiment is described with reference to fig. 2 and fig. 6, the floating ring test cavity of the embodiment comprises a left high-pressure cavity 4-13, a spring seal ring 4-14, a right high-pressure cavity 4-15, a test bed base 4-24 and a plurality of stud through bolts 4-16, the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15 are arranged above the test bed base 4-24 in parallel and opposite to each other, the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15 are fixedly connected through the plurality of stud through bolts 4-16, the spring seal ring 4-14 is adopted to seal the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15, and the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15 are respectively and fixedly connected with the test bed base 4-24. By the arrangement, the test bed bases 4-24 and the pressure-bearing water tank 8 are fixed on the foundation platform through foundation bolts. The left high-pressure cavity 4-13 and the right high-pressure cavity 4-15 are axially positioned by two cylindrical pins and are connected by 16 double-end through studs 4-16 which are uniformly distributed in the circumferential direction, the left water collecting cavity 4-8 and the right water collecting cavity 4-18 are respectively connected with the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15, and the connecting surfaces are sealed by spring sealing rings. Other components and connections are the same as in the first embodiment.
The third concrete implementation mode: the data acquisition and control system 5 of the embodiment comprises four first eddy current displacement sensors 4-12 for measuring the movement tracks of the floating ring test pieces 4-17, four thread sleeves 4-11 and four displacement sensor locking nuts, wherein the first eddy current displacement sensors 4-12 are pressure-resistant eddy current displacement sensors, two high-pressure cavity connecting threaded holes are respectively machined on the outer arc surfaces of the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15 at 90 degrees in the circumferential direction, the floating ring test cavity further comprises four thread sleeves 4-11 and four displacement sensor locking nuts, the outer cylindrical surfaces of the thread sleeves 4-11 are integrally machined into external threads, the thread sleeves 4-11 are spirally installed in the high-pressure cavity connecting threaded holes and fixed on the floating ring test cavity through the displacement sensor locking nuts, reducing through holes are machined in the thread sleeves 4-11, the lower half parts of the reducing through holes are machined into the displacement sensor connecting threaded holes and provided with stop ports for positioning, the upper half parts of the through holes are machined into through holes, the pressure-resistant eddy current displacement sensor connecting threaded holes are installed in the displacement sensor connecting threaded holes and sealed by a sealant, and the floating ring test cavity is sealed by the pressure-resistant eddy current displacement sensor locking nuts, and the floating ring test probes extending to the pressure ring test cavity 17. With the arrangement, the first eddy current displacement sensor 4-12 is used for monitoring the movement track of the floating ring test piece 4-17, the working pressure in the floating ring test cavity is not lower than 6MPa, the floating ring test sensor with the pressure-resistant specification not lower than 6MPa needs to be selected, and secondly, the problems of strength and sealing of the installation position of the floating ring test sensor need to be considered, the probe size of the conventional eddy current displacement sensor cannot meet the test and installation requirements of the floating ring easily, and the test requirements of the floating ring are met by adopting a threaded sleeve tool mode. Other compositions and connections are the same as in the first or second embodiments.
In the embodiment, a 0.9mm gap exists between an inner hole of the floating ring test piece 4-17 and an outer circle of the rotor 4-19, a 0.2mm diameter gap exists between the outer circle of the floating ring test piece 4-17 and the inner wall of the floating ring test cavity, when the floating ring test cavity is filled with a high-pressure working medium, the motion track of the floating ring test piece 4-17 can be changed under the driving of the rotor 4-19 rotating at a high speed, and the motion track of the floating ring test piece 4-17 is measured through a pressure-resistant eddy current displacement sensor.
The fourth concrete implementation mode: the embodiment is described with reference to fig. 1, fig. 2 and fig. 6, the water circulation system of the embodiment includes a water supply pump 6, a water storage tank 7 and a water return pump 9, an inlet pipe of the water supply pump 6 is connected with the water storage tank 7, an outlet pipe of the water supply pump 6 is connected with a pressure-bearing water tank 8, an inlet pipe of the water return pump 9 is respectively connected with a left water collection chamber 4-8 and a right water collection chamber 4-18 through a three-way valve, an outlet pipe of the water return pump 9 is connected with the water storage tank 7, the water supply pump 6 pressurizes the working medium in the water storage tank 7 and then conveys the working medium to the pressure-bearing water tank 8, the pressure-bearing water tank 8 is connected with the right end of a hollow water supply hole 4-19.1 of a rotor 4-19 in the floating ring testing and pressurizing integrated device 4, and the working medium is discharged into the water storage tank 7 through the water return pump 9 after the floating ring sealing test, thereby realizing the circulation of the working medium. According to the arrangement, the working medium in the water storage tank 7 is pressurized and injected into the pressure-bearing water tank 8 through the water supply pump 6, and axially reaches the position of the rotor wheel disc through the hollow liquid supply holes 4-19.1 of the rotors 4-19, the working medium is thrown to the outer edge of the wheel disc through the liquid throwing holes 4-19.2 in the rotary wheel disc and is discharged at high flow rate and high pressure, and after the working medium is decelerated and pressurized in the high-pressure cavity, the working medium leaks into the left water collecting cavity 4-8 and the right water collecting cavity 4-18 through the pair of symmetrically installed floating ring test pieces 4-17 and is pumped back into the water storage tank 7 through the water return pump 9, so that the circulation of the working medium is realized. Other compositions and connection relationships are the same as in the first, second or third embodiment.
The fifth concrete implementation mode is as follows: the embodiment is described with reference to fig. 2, the floating ring testing and pressurizing integrated device 4 of the embodiment further comprises water tank end packing seals 4-22 and two water collecting cavity end packing seals 4-7, axial seals are respectively realized between the left water collecting cavity 4-8 and the rotor 4-19 and between the right water collecting cavity 4-18 and the rotor 4-19 through the two water collecting cavity end packing seals 4-7, and axial seals are realized between the pressure-bearing water tank 8 and the rotor 4-19 through the water tank end packing seals 4-22. According to the arrangement, the water tank end filler seals 4-22 are arranged between the rotor and the high-pressure tank body of the pressure-bearing water tank 8, and the labyrinth seals 4-21 are arranged between the rotor and the peripheral tank body of the pressure-bearing water tank 8, so that the rotor is connected with the pressure-bearing water tank 8 in a sealing manner, and the problem of leakage of working media is avoided. Other compositions and connection relationships are the same as those in the first, second, third or fourth embodiment.
The sixth specific implementation mode: the embodiment is described with reference to fig. 2, the data acquisition and control system 5 of the embodiment further includes four second eddy current displacement sensors 4-9 for measuring the movement tracks of the rotors 4-19, two displacement sensor mounting holes are respectively processed on the outer arc surfaces of the left water collection cavity 4-8 and the right water collection cavity 4-18 in a circumferential direction of 90 °, the second eddy current displacement sensors 4-9 are mounted in the displacement sensor mounting holes and sealed by a sealant, and probes of the second eddy current displacement sensors 4-9 point to the rotors 4-19. By the arrangement, the second eddy current displacement sensor 4-9 is used for monitoring the movement track of the rotor 4-19, the second eddy current displacement sensor 4-9 is a conventional eddy current displacement sensor, and the size of a probe can meet the requirement of rotor test installation. Other compositions and connection relationships are the same as in the first, second, third, fourth or fifth embodiment.
The seventh embodiment: the data acquisition and control system 5 of the present embodiment further includes turbine flow meters 4 to 23 for measuring the leakage amount of the floating ring, and the turbine flow meters 4 to 23 are installed between the water supply pump 6 and the pressurized water tank 8. Other compositions and connection relationships are the same as in the first, second, third, fourth, fifth or sixth embodiment.
The specific implementation mode is eight: the data acquisition and control system 5 of the present embodiment further includes four pressure sensors 4-10, two pressure sensors 4-10 are respectively installed in the left high-pressure cavity 4-13 and the right high-pressure cavity 4-15, wherein one pressure sensor 4-10 is used for monitoring the fluid pressure at the top of the inner disk of the left high-pressure cavity 4-13 or the right high-pressure cavity 4-15, and the other pressure sensor 4-10 is used for monitoring the fluid pressure at the installation position of the floating ring test piece 4-17 in the left high-pressure cavity 4-13 or the right high-pressure cavity 4-15. Other compositions and connection relationships are the same as those of embodiment one, two, three, four, five, six or seven.
The specific implementation method nine: referring to fig. 1, the data acquisition and control system 5 of the present embodiment further includes a rotation speed measuring instrument 4-25 for measuring the rotation speed of the rotor 4-19, wherein the rotation speed measuring instrument 4-25 is installed at one end of the rotor 4-19 close to the driving mechanism. Other compositions and connection relations are the same as those of the first embodiment, the second embodiment, the third embodiment, the fourth embodiment, the fifth embodiment, the sixth embodiment, the seventh embodiment or the eighth embodiment.
The specific implementation mode is ten: the embodiment is described by combining fig. 1, a supporting component 3 of the embodiment comprises a bearing seat, a bearing closing cover 4-3, a bearing lock nut 4-4, a bearing closing chamber 4-6, two bearing end covers 4-2 and two angular contact bearings 4-5, wherein a circular through hole is processed on the bearing seat, two oil guide ring grooves are processed on the inner wall of the circular through hole of the bearing seat along the circumferential direction, oil outlet holes are processed on the left end surface of the bearing seat of the oil guide ring grooves along the axial direction, the oil outlet holes are respectively communicated with the two oil guide ring grooves through two oil passages, the bearing closing chamber 4-6 is coaxially installed in the circular through hole of the bearing seat, a shaft hole which is rotatably matched with a rotor 4-19 is processed on one side end surface of the bearing closing chamber 4-6 close to a left water collecting cavity 4-8, and the bearing closing cover 4-3 is installed on one side end part of the bearing closing chamber 4-6 close to a driving mechanism, an oil pipe assembling hole is processed on the bearing sealing cover 4-3, two angular contact bearings 4-5 arranged side by side are coaxially arranged in a bearing sealing chamber 4-6, the angular contact bearings 4-5 and the bearing sealing chamber 4-6 are integrally sleeved on the rotor 4-19, one end of each angular contact bearing 4-5 is axially positioned by a coaxial shaft shoulder, the other end of each angular contact bearing 4-5 is axially positioned by a bearing locking nut 4-4, two bearing end covers 4-2 positioned at two sides of each bearing seat are sleeved on the rotor 4-19, each bearing end cover 4-2 is connected with each bearing seat by a connecting screw, an oil pipe joint 4-1 sequentially penetrates through the bearing end covers 4-2 and the bearing sealing covers 4-3 and a bearing sealing cavity formed by the bearing sealing chamber 4-6 and the bearing sealing covers 4-3 The bodies are connected. According to the arrangement, the rotors 4 to 19 are supported by two pairs of angular contact bearings 4 to 5 which are arranged back to back, the cooling and lubricating system 10 is communicated with the oil outlet and the oil pipe joint 4 to 1 to cool and lubricate the bearings, the cooling and lubricating system 10 is used for providing cooling and lubricating for the gear box 2 and the supporting assembly 3, the lubricating and cooling system 10 conveys lubricating oil to lubricated equipment through an oil pump and an oil pipeline, and the lubricating oil is recycled. Other compositions and connections are the same as those of the first, second, third, fourth, fifth, sixth, seventh, eighth or ninth embodiments.
In the embodiment, a pair of angular contact bearings 4-5 is arranged in a bearing closed chamber 4-6, then sleeved on a bearing positioning surface of a rotor 4-19 and axially compressed through a lock nut 4-4, the bearing closed cover 4-3 is sleeved and then integrally placed on a test bed base 4-24, a disc spring 4-20 is axially arranged on the side of a rotor water tank to provide axial force for a rotor system, and a bearing end cover 4-2 is fixed on the test bed base 4-24 through an inner hexagonal bolt and is connected with an oil pipe joint 4-1.
In the embodiment, a disc spring 4-20 is arranged between a right bearing end cover 4-2 of the support assembly 3 close to one side of the pressure-bearing water tank 8 and a bearing closing chamber 4-6, the disc spring 4-20 is axially installed on the rotor 4-19 water tank side to provide axial force for a rotor system, and because the installation position of the disc spring 4-20 is interfered with an oil pipe joint 4-1, an oil inlet hole is also processed on a bearing seat close to one side of the pressure-bearing water tank 8 to replace the oil pipe joint on the side; and a thermocouple is arranged in the bearing closed chamber 4-6 and is used for monitoring the temperature of the bearing.
Principle of operation
With reference to fig. 1 to 6, the floating ring seal test bench with large pressure difference and high rotating speed of the invention is used for a floating ring seal test, and the specific operation steps are as follows:
step one, assembling a test bed:
sleeving a pair of floating ring test pieces 4-17 with the same structure on rotors 4-19, assembling the test beds into a whole in sequence, installing a sensor required by a floating ring sealing test, connecting the sensor to a cooling and lubricating system 10, and connecting the sensor to a water circulation system; step two, preparation before testing:
checking whether the foundation bolts, the couplers and the connecting pieces of the test bed are loosened, opening the data acquisition and control system 5, and starting an oil pump to cool and lubricate the gear box 2 and the supporting component 3;
step three, filling stage:
setting a water supply pump 6 to be started in advance at a lower pressure value, and when water is discharged from water return pipelines passing through the high-pressure cavity, the left water collection cavity 4-8 and the right water collection cavity 4-18, opening a water return pump 9 to complete water path circulation and check whether a test bed leaks;
step four, a test stage:
adjusting a water supply pump 6 frequency converter to control a floating ring test and pressurization integrated device 4, adjusting a rotor frequency converter to control the rotating speed of a rotor 4-19 to reach the pressure and the rotating speed required by the floating ring test, and acquiring and recording test data of each test point in real time after the rotating speed and the pressure are stabilized for 30 s;
step five, the test finishing stage:
after the test is finished, the driving motor 1 is firstly closed, after the rotating speed of the rotor 4-19 stops, the water supply pump 6 is closed, the water return pump 9 is closed, the lubricating and cooling system is closed, and the measurement of the group of floating ring test pieces is finished.
The above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (10)
1. A large-pressure-difference high-rotation-speed floating ring sealing test bench comprises a floating ring testing and pressurizing integrated device (4), a driving mechanism for providing power for the floating ring testing and pressurizing integrated device (4), a data acquisition and control system (5) for acquiring measurement parameters required by the floating ring testing, a pressure-bearing water tank (8), a water circulation system for providing testing media for the floating ring testing, two supporting assemblies (3) and a cooling and lubricating system (10) for cooling and lubricating the supporting assemblies (3) and the driving mechanism; the method is characterized in that: the floating ring testing and pressurizing integrated device (4) comprises a floating ring testing cavity, a left water collecting cavity (4-8), a right water collecting cavity (4-18), a rotor (4-19) and two floating ring testing pieces (4-17), wherein the left side and the right side of the floating ring testing cavity are respectively connected with the left water collecting cavity (4-8) and the right water collecting cavity (4-18), the left end of the rotor (4-19) sequentially and axially penetrates through the left half part and the left water collecting cavity (4-8) of the floating ring testing cavity and is fixedly connected with the output end of a driving mechanism, the right end of the rotor (4-19) sequentially and axially penetrates through the right half part and the right water collecting cavity (4-18) of the floating ring testing cavity and is rotatably connected with a pressure-bearing water tank (8), two supporting assemblies (3) for supporting the rotor (4-19) are respectively arranged between the left water collecting cavity (4-8) and a driving mechanism, two conical contact surfaces of the right water collecting cavity (4-18) and the pressure bearing water tank (8), a wheel disc is respectively arranged on the middle part of the rotor (4-19), a wheel disc is machined with a conical contact surface of the floating ring, the floating ring testing cavity, the floating ring and two floating ring testing pieces (17) are respectively arranged on the outer edge of the floating ring testing cavity, the floating ring (4-17), the wall surface of a sealing cavity of the floating ring testing cavity is used for a stator end wall contacted with a floating ring boss; the center of the right end face of the rotor (4-19) is axially provided with a hollow water supply hole (4-19.1) with the depth reaching the center of the wheel disc, the right end of the hollow water supply hole (4-19.1) is communicated with the pressure-bearing water tank (8), a plurality of water throwing holes (4-19.2) tangent to the hollow water supply hole (4-19.1) are uniformly processed in the wheel disc along the circumferential direction, a plurality of balance holes corresponding to the water throwing holes (4-19.2) one by one are processed on the outer edge face of the wheel disc along the circumferential direction, two ends of each water throwing hole (4-19.2) are respectively communicated with the corresponding hollow water supply hole (4-19.1) and the balance hole, and the left water collecting cavity (4-8) and the right water collecting cavity (4-18) are subjected to working medium circulation with the pressure-bearing water tank (8) through a water circulation system.
2. The large pressure differential, high rotational speed floating ring seal test rig of claim 1, wherein: the floating ring testing cavity comprises a left high-pressure cavity (4-13), a spring sealing ring (4-14), a right high-pressure cavity (4-15), a test bed base (4-24) and a plurality of double-headed through bolts (4-16), wherein the left high-pressure cavity (4-13) and the right high-pressure cavity (4-15) are arranged above the test bed base (4-24) side by side and are oppositely arranged, the left high-pressure cavity (4-13) and the right high-pressure cavity (4-15) are fixedly connected through the plurality of double-headed through bolts (4-16), the left high-pressure cavity (4-13) and the right high-pressure cavity (4-15) are sealed through the spring sealing ring (4-14), and the left high-pressure cavity (4-13) and the right high-pressure cavity (4-15) are respectively and fixedly connected with the test bed base (4-24).
3. The large differential pressure, high rotational speed floating ring seal test bench of claim 2, characterized in that: the data acquisition and control system (5) comprises four first eddy current displacement sensors (4-12) used for measuring the movement track of a floating ring test piece (4-17), four thread sleeves (4-11) and four displacement sensor locking nuts, the first eddy current displacement sensors (4-12) are pressure-resistant eddy current displacement sensors, two high-pressure cavity connecting threaded holes are respectively machined on the outer arc surfaces of a left high-pressure cavity (4-13) and a right high-pressure cavity (4-15) in a 90-degree circumferential direction, the floating ring test cavity further comprises four thread sleeves (4-11) and four displacement sensor locking nuts, the outer cylindrical surfaces of the thread sleeves (4-11) are integrally machined into external threads, the thread sleeves (4-11) are spirally installed in the high-pressure cavity connecting threaded holes and fixed on the floating ring test cavity through the displacement sensor locking nuts, the inner parts of the thread sleeves (4-11) are machined into reducing through holes, the lower half of the reducing through holes are machined into displacement sensor connecting threaded holes and provided with seam allowance positioning, the upper half of the reducing through holes are machined into through holes, the pressure-resistant eddy current displacement sensors are spirally installed in the connecting threaded holes and seal the floating ring test cavity, and the floating ring test probe extends to the external eddy current displacement sensors through the pressure-resistant eddy current displacement sensors (17).
4. The large differential pressure, high rotational speed floating ring seal test rig of claim 1 or 3, wherein: the water circulation system comprises a water supply pump (6), a water storage tank (7) and a water return pump (9), wherein a water inlet pipeline of the water supply pump (6) is connected with the water storage tank (7), a water outlet pipeline of the water supply pump (6) is connected with a pressure-bearing water tank (8), a water inlet pipeline of the water return pump (9) is respectively connected with a left water collecting cavity (4-8) and a right water collecting cavity (4-18) through a three-way valve, a water outlet pipeline of the water return pump (9) is connected with the water storage tank (7), a working medium in the water storage tank (7) is pressurized by the water supply pump (6) and then conveyed into the pressure-bearing water tank (8), the pressure-bearing water tank (8) is connected with the right end of a hollow water supply hole (4-19.1) of a rotor (4-19) in the floating ring testing and pressurizing integrated device (4), and is discharged into the water storage tank (7) through the water return pump (9) after the floating ring sealing test, so that the circulation of the working medium is realized.
5. The large pressure differential, high rotational speed floating ring seal test rig of claim 4, wherein: the floating ring testing and pressurizing integrated device (4) further comprises a water tank end packing seal (4-22) and two water collecting cavity end packing seals (4-7), axial sealing is achieved between the left water collecting cavity (4-8) and the rotor (4-19) and between the right water collecting cavity (4-18) and the rotor (4-19) through the two water collecting cavity end packing seals (4-7), and axial sealing is achieved between the pressure-bearing water tank (8) and the rotor (4-19) through the water tank end packing seals (4-22).
6. The large differential pressure, high rotational speed floating ring seal test rig of claim 1 or 5, wherein: the data acquisition and control system (5) further comprises four second eddy current displacement sensors (4-9) used for measuring the movement tracks of the rotors (4-19), two displacement sensor mounting holes are respectively machined on the outer arc surfaces of the left water collecting cavity (4-8) and the right water collecting cavity (4-18) in a circumferential direction of 90 degrees, the second eddy current displacement sensors (4-9) are mounted in the displacement sensor mounting holes and sealed through sealing glue, and probes of the second eddy current displacement sensors (4-9) point to the rotors (4-19).
7. The large differential pressure, high rotational speed floating ring seal test bench of claim 6, characterized in that: the data acquisition and control system (5) further comprises turbine flow meters (4-23) used for measuring the leakage amount of the floating ring, and the turbine flow meters (4-23) are installed between the water supply pump (6) and the pressure-bearing water tank (8).
8. The large differential pressure, high rotational speed floating ring seal test rig of claim 7, wherein: the data acquisition and control system (5) further comprises four pressure sensors (4-10), two pressure sensors (4-10) are respectively installed in the left high-pressure cavity (4-13) and the right high-pressure cavity (4-15), one of the pressure sensors (4-10) is used for monitoring the fluid pressure at the top of the inner disk of the left high-pressure cavity (4-13) or the right high-pressure cavity (4-15), and the other pressure sensor (4-10) is used for monitoring the fluid pressure at the installation position of the floating ring test piece (4-17) in the left high-pressure cavity (4-13) or the right high-pressure cavity (4-15).
9. The large differential pressure, high rotational speed floating ring seal test rig of claim 8, wherein: the data acquisition and control system (5) also comprises a rotating speed measuring instrument (4-25) used for measuring the rotating speed of the rotor (4-19), and the rotating speed measuring instrument (4-25) is arranged at one end of the rotor (4-19) close to the driving mechanism.
10. A high differential pressure, high speed floating ring seal test rig according to claim 1, 2, 3, 5, 7, 8 or 9, wherein: the bearing assembly (3) comprises a bearing seat, a bearing closing cover (4-3), a bearing locking nut (4-4), a bearing closing chamber (4-6), two bearing end covers (4-2) and two angular contact bearings (4-5), wherein a circular through hole is processed on the bearing seat, two oil guide ring grooves are processed on the inner wall of the circular through hole of the bearing seat along the circumferential direction, oil outlet holes are processed on the left end surface of the oil guide ring groove bearing seat along the axial direction, the oil outlet holes are respectively communicated with the two oil guide ring grooves through two oil ways, the bearing closing chamber (4-6) is coaxially installed in the circular through hole of the bearing seat, an oil pipe assembly hole is processed on one side end surface of the bearing closing chamber (4-6) close to a left water collecting cavity (4-8) and rotatably matched with a rotor (4-19), the end part of one side of the bearing closing chamber (4-6) close to a driving mechanism is provided with the bearing closing cover (4-3), oil pipe assembly holes are processed on the bearing closing cover (4-3), the two angular contact bearings (4-5) which are arranged side by side are installed in the bearing closing chamber (4-6) inside the bearing closing chamber (4-6), the bearing closing chamber (4-6) and the axial direction, the axial direction of the bearing closing chamber (4-5) is sleeved on the other end of the bearing (4-5), and the axial direction of the bearing closing chamber (4-6), and the axial direction of the bearing (4-6) is realized by axial angular contact bearing (4-5), two bearing end covers (4-2) positioned at two sides of the bearing seat are sleeved on the rotor (4-19), the bearing end covers (4-2) are connected with the bearing seat through connecting screws, and the oil pipe joint (4-1) sequentially penetrates through the bearing end covers (4-2) and the bearing sealing cover (4-3) and is communicated with a bearing sealing cavity formed by the bearing sealing chamber (4-6) and the bearing sealing cover (4-3).
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2589955A1 (en) * | 1985-11-08 | 1987-05-15 | Sealol | TURBOPOMPE SEALING DEVICE |
| CN101506526A (en) * | 2006-08-26 | 2009-08-12 | Ksb股份公司 | Delivery pump |
| CN111636981A (en) * | 2020-06-12 | 2020-09-08 | 哈尔滨工业大学 | Test bench for testing floating ring seal of rocket turbopump |
| CN111753380A (en) * | 2020-06-12 | 2020-10-09 | 哈尔滨工业大学 | Modeling method for gap sealing model of rocket engine liquid oxygen turbine pump |
| CN213775555U (en) * | 2020-09-27 | 2021-07-23 | 蓝箭航天技术有限公司 | Low-temperature high-rotating-speed floating ring sealing test device for rocket engine turbine pump |
-
2022
- 2022-07-15 CN CN202210835991.XA patent/CN115182829B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2589955A1 (en) * | 1985-11-08 | 1987-05-15 | Sealol | TURBOPOMPE SEALING DEVICE |
| CN101506526A (en) * | 2006-08-26 | 2009-08-12 | Ksb股份公司 | Delivery pump |
| CN111636981A (en) * | 2020-06-12 | 2020-09-08 | 哈尔滨工业大学 | Test bench for testing floating ring seal of rocket turbopump |
| CN111753380A (en) * | 2020-06-12 | 2020-10-09 | 哈尔滨工业大学 | Modeling method for gap sealing model of rocket engine liquid oxygen turbine pump |
| CN213775555U (en) * | 2020-09-27 | 2021-07-23 | 蓝箭航天技术有限公司 | Low-temperature high-rotating-speed floating ring sealing test device for rocket engine turbine pump |
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