CN109654040B - Dual-power and speed-raising type gas compression equipment - Google Patents
Dual-power and speed-raising type gas compression equipment Download PDFInfo
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- CN109654040B CN109654040B CN201910046274.7A CN201910046274A CN109654040B CN 109654040 B CN109654040 B CN 109654040B CN 201910046274 A CN201910046274 A CN 201910046274A CN 109654040 B CN109654040 B CN 109654040B
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- 230000006835 compression Effects 0.000 title claims description 17
- 238000007906 compression Methods 0.000 title claims description 17
- 239000000446 fuel Substances 0.000 claims abstract description 19
- 239000007788 liquid Substances 0.000 claims description 37
- 239000000314 lubricant Substances 0.000 claims description 19
- 238000007789 sealing Methods 0.000 claims description 11
- 230000009977 dual effect Effects 0.000 claims description 7
- 230000001050 lubricating effect Effects 0.000 claims description 6
- 238000007667 floating Methods 0.000 claims description 4
- 238000005096 rolling process Methods 0.000 claims description 4
- 230000000694 effects Effects 0.000 abstract description 6
- 238000000034 method Methods 0.000 abstract description 5
- 239000007789 gas Substances 0.000 description 29
- 238000005461 lubrication Methods 0.000 description 11
- 239000012530 fluid Substances 0.000 description 4
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 3
- 239000001257 hydrogen Substances 0.000 description 3
- 229910052739 hydrogen Inorganic materials 0.000 description 3
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 230000003071 parasitic effect Effects 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
Classifications
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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
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/04—Units comprising pumps and their driving means the pump being fluid-driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/08—Adaptations for driving, or combinations with, pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/14—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours using industrial or other waste gases
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M8/00—Fuel cells; Manufacture thereof
- H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
- H01M8/04082—Arrangements for control of reactant parameters, e.g. pressure or concentration
- H01M8/04089—Arrangements for control of reactant parameters, e.g. pressure or concentration of gaseous reactants
- H01M8/04111—Arrangements for control of reactant parameters, e.g. pressure or concentration of gaseous reactants using a compressor turbine assembly
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M8/00—Fuel cells; Manufacture thereof
- H01M8/06—Combination of fuel cells with means for production of reactants or for treatment of residues
- H01M8/0662—Treatment of gaseous reactants or gaseous residues, e.g. cleaning
-
- 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
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/30—Hydrogen technology
- Y02E60/50—Fuel cells
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Sustainable Energy (AREA)
- Sustainable Development (AREA)
- Manufacturing & Machinery (AREA)
- Life Sciences & Earth Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Electrochemistry (AREA)
- General Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The cathode exhaust of the fuel cell has certain pressure and energy, and flows into the pneumatic turbine shell through the air inlet to push the exhaust turbine to rotate, and meanwhile, the direct current motor is electrified to drive the power shaft to rotate, so that the cathode exhaust of the fuel cell and the direct current motor jointly drive the power shaft to rotate, the low-flow-rate exhaust energy can be recovered to save the driving energy actually consumed by the supercharging equipment, and the energy-saving effect is achieved. At the same time, the power capacity, size and cost of the supercharging equipment motive power device can be remarkably reduced. The restriction of high rotation speed of the power shaft on mechanical and electrical process bottlenecks of the direct current motor is avoided, the technical difficulty in supporting the power shaft is reduced, the reliability is remarkably improved, and the cost is reduced.
Description
Technical Field
The invention relates to the technical field of air inlet pressurization, in particular to a double-power and speed-raising type gas compression device.
Background
Centrifugal gas compression techniques have particular advantages and find wide application, such as exhaust gas turbochargers for internal combustion engines, air intake compressors for hydrogen fuel cells, industrial-scale high-flow air compressors, and the like. The principle is that the motive power machine drives the centrifugal air compressing impeller to rotate at high speed, so that the centrifugal air compressing impeller acts on the air inlet and generates rotation and centrifugal movement to form a supercharging effect. The rotation speed of the centrifugal air compressing impeller is usually as high as tens of thousands of revolutions per minute to hundreds of thousands of revolutions per minute, so that the design and production of the product have high technical difficulty.
As one type of application scenario, a high-speed motor is used as a motive power for driving a centrifugal compressor, and more energy is consumed. Such as an electrically powered air compressor associated with a hydrogen fuel cell system, consumes approximately 20% of the power output from the fuel cell system. The air compressor becomes the largest parasitic energy consuming component of the fuel cell system, thus reducing the energy consumed by the gas compression apparatus, while having a compact, reliable and low cost air management system with significant energy saving and economic benefits.
The off-gas discharged from the high pressure gas output from the gas compression apparatus after use by downstream devices typically contains some residual energy. In a charge air intake system such as a hydrogen fuel cell, after the compressed air has consumed a portion of the oxygen in the interior of the stack, the remaining exhaust gas is discharged from the stack at a pressure corresponding to about 70% of the charge air pressure. How to recover the energy of the exhaust gas with lower flow rate is the key for realizing the energy saving of the compressor.
Disclosure of Invention
In order to overcome the defects of the technology, the invention provides a new scheme for recovering the tail gas energy, and the double-power and speed-raising type gas compression equipment which can recover the exhaust energy and obviously reduce the energy consumption under the constraint condition of not obviously increasing the exhaust back pressure.
The technical scheme adopted for overcoming the technical problems is as follows:
A dual power and speed raising mode gas compression apparatus comprising:
A housing having a cavity therein;
the power shaft is rotatably installed in the cavity of the shell through a bearing;
The direct current motor is arranged in the cavity of the shell, the motor stator is connected with the inner wall of the shell, and the motor rotor is coaxially and fixedly arranged with the power shaft;
the air turbine shell is arranged at one end of the shell and is provided with an air inlet and an air outlet, and the air inlet is connected with a cathode exhaust channel of the fuel cell;
the exhaust turbine is arranged in the pneumatic turbine shell, flowing gas entering the air inlet pushes the exhaust turbine to rotate, and the exhaust turbine is coaxially connected with the power shaft;
The compressor shell is arranged at the other end of the shell and is provided with a compressed air outlet which is connected with a cathode air inlet channel of the fuel cell; and
The compressor impeller is arranged in the compressor shell, the rotating shaft I is arranged in the compressor shell, one end of the rotating shaft I is coaxially connected with the compressor impeller, the other end of the rotating shaft I is connected with the power shaft through the speed increasing mechanism, and the speed increasing mechanism enables the rotating speed of the rotating shaft I to be larger than that of the power shaft.
Further, the bearing is a rolling bearing.
Further, the bearing is a floating bearing.
Further, the speed increasing mechanism comprises a support arranged on the shell, a rotary ring coaxially connected with the power shaft and N planetary gears circumferentially arranged on the periphery of the rotary shaft I in a surrounding manner by taking the axis of the rotary shaft I as the center, the planetary gears are rotatably arranged on the support through the rotary shaft II, the axes of the planetary gears are parallel to the axis of the rotary shaft I and the axis of the power shaft, the cylindrical surface of the outer side end of the planetary gears is in contact with the circular inner wall of the rotary ring, and the cylindrical surface of the inner side end of the planetary gears is in contact with the outer end face of the rotary shaft I.
In order to improve lubricity, the lubricating device further comprises a lubricant channel I arranged at the upper end of the shell and a lubricant channel II arranged at the lower end of the shell, wherein the inlet end of the lubricant channel I is connected with the outlet end of the lubricating pump, the outlet end of the lubricant channel I is arranged at the bearing, the inlet end of the lubricant channel II is arranged at the bearing, and the outlet end of the lubricant channel II is connected with the inlet end of the lubricating pump.
In order to improve the tightness, sealing rings I are respectively arranged between the shells at two sides of the bearing and the power shaft.
Preferably, N is 3.
In order to improve lubricity, the traction liquid pump is characterized by further comprising a traction liquid channel I arranged on the compressor support and a traction liquid channel II arranged in the rotating shaft I, wherein the inlet end of the traction liquid channel I is connected with the traction liquid pump, one outlet end of the traction liquid channel I faces the cylindrical surface of the planet wheel, the other outlet end of the traction liquid channel I is connected with the inlet end of the traction liquid channel II, the outlet end of the traction liquid channel II is arranged between the interface of the rotating shaft I and the planet wheel, and a traction liquid outlet for backflow of traction liquid is arranged on the shell.
In order to improve the tightness, a sealing ring II is arranged between the support and the rotating shaft I, and the sealing ring II is positioned between the speed increasing mechanism and the compressor impeller.
The beneficial effects of the invention are as follows: the cathode exhaust of the fuel cell has certain pressure and energy, and flows into the pneumatic turbine shell through the air inlet to push the exhaust turbine to rotate, and meanwhile, the direct current motor is electrified to drive the power shaft to rotate, so that the cathode exhaust of the fuel cell and the direct current motor jointly drive the power shaft to rotate, the driving energy actually consumed by the supercharging equipment can be obviously saved, and the energy-saving effect is achieved. At the same time, the power capacity, size and cost of the supercharging equipment motive power device can be remarkably reduced. The power shaft rotates to drive the rotating shaft I to rotate through the speed increasing mechanism, so that the compressor impeller rotates, and the compressor impeller pressurizes gas and then outputs the gas to be pressed into a cathode air inlet channel of the fuel cell through a compressed air outlet. The restriction of high rotation speed of the power shaft on mechanical and electrical process bottlenecks of the direct current motor is avoided, the technical difficulty in supporting the power shaft is reduced, the reliability is remarkably improved, and the cost is reduced. Compared with the scheme of high rotation speed of the power shaft 7, the back pressure resistance effect formed by the low rotation speed exhaust turbine of the double-power and speed-increasing type gas compression device on the exhaust gas of the downstream device is obviously reduced, and the energy of the lower flow speed exhaust gas exhaust link can be utilized. Meanwhile, the restriction of mechanical and electrical process bottlenecks brought by high rotation speed of the power shaft to the direct current motor is avoided, the technical difficulty in supporting the power shaft is reduced, the reliability is remarkably improved, and the cost is reduced.
Drawings
FIG. 1 is a schematic view of a cross-sectional front view of a rolling bearing of the present invention;
FIG. 2 is a schematic cross-sectional front view of a floating bearing according to the present invention;
FIG. 3 is a schematic cross-sectional view of a portion of the speed increaser of the present invention;
In the drawings, 1 casing 2, pneumatic turbine casing 3, air inlet 4, air outlet 5, compressor casing 6, compressed air outlet 7, power shaft 8, rolling bearing 9, exhaust turbine 10, compressor wheel 11, lubricant passage I12, lubricant passage II 13, motor stator 14, motor rotor 15, seal ring I16, swivel 17, planet wheel 18, support 19, shaft I20, seal ring II 21, floating bearing 22, shaft II 23, traction fluid passage I24, traction fluid passage II 25, traction fluid outlet.
Detailed Description
The invention will be further described with reference to fig. 1,2 and 3.
A dual power and speed raising mode gas compression apparatus comprising: a housing 1 having a cavity therein; a power shaft 7 rotatably mounted in the cavity of the housing 1 through a bearing; the direct current motor is arranged in the cavity of the shell 1, the motor stator 13 is connected with the inner wall of the shell 1, and the motor rotor 14 is fixedly arranged coaxially with the power shaft 7; a gas turbine housing 2 mounted at one end of the housing 1 and provided with an air inlet 3 and an air outlet 4, the air inlet 3 being connected to a cathode exhaust passage of the fuel cell; an exhaust turbine 9 mounted in the air turbine housing 2, the flowing gas entering in the air inlet 3 pushing the exhaust turbine 9 to rotate, the exhaust turbine 9 being coaxially connected with the power shaft 7; a compressor housing 5 mounted at the other end of the housing 1 and provided with a compressed air outlet 6, the compressed air outlet 6 being connected to a cathode air intake passage of the fuel cell; and the compressor impeller 10 is arranged in the compressor shell 5, the rotating shaft I19 is arranged in the compressor shell 5, one end of the rotating shaft I19 is coaxially connected with the compressor impeller 10, and the other end of the rotating shaft I19 is connected with the power shaft 7 through a speed increasing mechanism, so that the rotating speed of the rotating shaft I19 is greater than that of the power shaft 7. The cathode exhaust gas of the fuel cell has certain pressure and energy, and flows into the pneumatic turbine housing 2 through the air inlet 3 to push the exhaust turbine 9 to rotate, meanwhile, the motor rotor 14 drives the power shaft 7 to rotate after the direct current motor is electrified, so that the exhaust turbine 9 actively rotates, the cathode exhaust gas of the fuel cell and the direct current motor jointly drive the power shaft 7 to rotate, and the driving energy actually consumed by the supercharging equipment can be remarkably saved, namely, the energy-saving effect is achieved. At the same time, the power capacity, size and cost of the supercharging equipment motive power device can be remarkably reduced. The power shaft 7 rotates to drive the rotating shaft I19 to rotate through the speed increasing mechanism, so that the compressor impeller 10 rotates, and the compressor impeller 10 pressurizes gas and then presses the gas into a cathode air inlet channel of the fuel cell through the compressed air outlet 6. Since the rotation speed of the rotating shaft I19 is far greater than that of the power shaft 7 after the speed is increased by the speed increasing mechanism, the rotation speed of the power shaft 7 can be even only one tenth of the magnitude of the rotation speed I19. The restriction of mechanical and electrical process bottlenecks brought by the high rotating speed of the power shaft 7 to the direct current motor is avoided, the technical difficulty in the aspect of supporting the power shaft 7 is reduced, the reliability is remarkably improved, and the cost is reduced. Compared with the scheme of high rotation speed of the power shaft 7, the low rotation speed exhaust turbine 9 of the double-power and speed-increasing type gas compression device has obviously reduced back pressure resistance effect on the tail gas, and is easy to meet the conditions required by the tail gas discharge link.
As shown in fig. 3, the speed raising mechanism comprises a bracket 18 mounted on the casing 1, a rotary ring 16 coaxially connected with the power shaft 7 and N planetary gears 17 circumferentially surrounding the rotary shaft i 19 with the axis of the rotary shaft i 19 as the center, the planetary gears 17 are rotatably mounted on the bracket 18 through a rotary shaft ii 22, the axis of the planetary gears 17 is parallel to the axis of the rotary shaft i 19 and the axis of the power shaft 7, the cylindrical surface of the outer side end of the planetary gears 17 is in contact with the circular inner wall of the rotary ring 16, and the cylindrical surface of the inner side end of the planetary gears 17 is in contact with the outer end surface of the rotary shaft i 19. The power shaft 7 drives the rotating ring 16 to rotate, the rotating ring 16 drives each planet wheel 17 to rotate by friction force, the rotating shaft I19 is driven by friction force to rotate when each planet wheel 17 rotates, so that the compressor impeller 10 rotates, the circumference of a round hole of the rotating ring 16 is larger than that of the planet wheel 17, the rotating speed of the planet wheel 17 is larger than that of the rotating ring 16 when the rotating ring 16 drives the planet wheel 17 to rotate, the outer diameter of the planet wheel 17 is larger than that of the rotating shaft I19, and the rotating speed of the planet wheel 17 is smaller than that of the rotating shaft I19 when the planet wheel 17 drives the rotating shaft I19 to rotate. Therefore, the 2-level speed increasing is realized, and the problem that the traditional gear meshing speed increasing mechanism cannot adapt to high rotating speed is solved through the driving route of the swivel 16-the planet wheel 17-the rotating shaft I19 because the rotating speed of the rotating shaft I19 is very high. N may be 3, with 3 planets 17 being provided as the optimal choice.
Further, the lubrication device further comprises a lubrication channel I11 arranged at the upper end of the shell 1 and a lubrication channel II 12 arranged at the lower end of the shell 1, wherein the inlet end of the lubrication channel I11 is connected with the outlet end of the lubrication pump, the outlet end of the lubrication channel I is arranged at the bearing, the inlet end of the lubrication channel II 12 is arranged at the bearing, and the outlet end of the lubrication channel II is connected with the inlet end of the lubrication pump. The lubrication pump pumps the lubricant into the lubricant channel I11, so that the bearing is lubricated, and the lubricated lubricant flows back to the lubrication pump through the lubricant channel II 12, so that circulation is realized.
Further, sealing rings I15 are respectively arranged between the housing 1 and the power shaft 7 at two sides of the bearing. The sealing ring i 15 improves the tightness to the bearing and prevents the lubricant from flowing into the housing 1.
Further, the device further comprises a traction liquid channel I23 arranged on the compressor bracket 18 and a traction liquid channel II 24 arranged in the rotating shaft I19, wherein the inlet end of the traction liquid channel I23 is connected with the traction liquid pump, one outlet end of the traction liquid channel I is towards the cylindrical surface position of the planet wheel 17, the other outlet end of the traction liquid channel I is connected with the inlet end of the traction liquid channel II 24, and the outlet end of the traction liquid channel II 24 is arranged between interfaces where the rotating shaft I19 and the planet wheel 17 are in contact. The traction liquid pump pumps traction liquid into the traction liquid channel I23, the traction liquid flows into a rotation connection area between the rotating shaft I19 and the air compressor shell 5 from the traction liquid channel II 24 to lubricate, the traction liquid flows into a space between the rotating shaft I19 and the planetary gears 17 to lubricate the planetary gears 17, and a traction liquid outlet 25 for backflow of the traction liquid is arranged on the shell 1. Traction liquid is discharged through a traction liquid outlet 25, so that recycling is realized.
Further, a sealing ring II 20 is arranged between the bracket 18 and the rotating shaft I19, and the sealing ring II 20 is positioned between the speed increasing mechanism and the compressor impeller 10. The sealing ring II 20 can prevent traction fluid from flowing into the compressor housing 5, so that the tightness is improved.
Claims (6)
1. A dual-power and speed-raising mode gas compression apparatus comprising:
a housing (1) having a cavity therein;
a power shaft (7) rotatably mounted in the cavity of the housing (1) through a bearing;
the direct current motor is arranged in the cavity of the shell (1), the motor stator (13) is connected with the inner wall of the shell (1), and the motor rotor (14) is coaxially and fixedly arranged with the power shaft (7);
A pneumatic turbine housing (2) mounted at one end of the housing (1) and provided with an air inlet (3) and an air outlet (4), the air inlet (3) being connected to a cathode exhaust passage of the fuel cell;
the exhaust turbine (9) is arranged in the pneumatic turbine shell (2), flowing gas entering the air inlet (3) pushes the exhaust turbine (9) to rotate, and the exhaust turbine (9) is coaxially connected with the power shaft (7);
the compressor shell (5) is arranged at the other end of the shell (1) and is provided with a compressed air outlet (6), and the compressed air outlet (6) is connected with a cathode air inlet channel of the fuel cell; and
The compressor impeller (10) is arranged in the compressor shell (5), the rotating shaft I (19) is arranged in the compressor shell (5), one end of the rotating shaft I (19) is coaxially connected with the compressor impeller (10), the other end of the rotating shaft I is connected with the power shaft (7) through the speed increasing mechanism, and the rotating speed of the rotating shaft I (19) is greater than that of the power shaft (7) through the speed increasing mechanism;
The bearing is a rolling bearing (8);
The bearing is a floating bearing (21);
The speed increasing mechanism comprises a support (18) arranged on the shell (1), a circular rotating ring (16) coaxially connected with the power shaft (7) and N planetary gears (17) circumferentially arranged on the periphery of the rotating shaft I (19) in a surrounding mode by taking the axis of the rotating shaft I (19) as the center, the planetary gears (17) are rotatably arranged on the support (18) through a rotating shaft II (22), the axis of the planetary gears (17) is parallel to the axis of the rotating shaft I (19) and the axis of the power shaft (7), the cylindrical surface of the outer side end of the planetary gears (17) is in contact with the circular inner wall of the rotating ring (16), and the cylindrical surface of the inner side end of the planetary gears (17) is in contact with the outer end face of the rotating shaft I (19).
2. The dual power and ramp-up mode gas compression apparatus of claim 1, wherein: the lubricating device is characterized by further comprising a lubricant channel I (11) arranged at the upper end of the shell (1) and a lubricant channel II (12) arranged at the lower end of the shell (1), wherein the inlet end of the lubricant channel I (11) is connected with the outlet end of the lubricating pump, the outlet end of the lubricant channel I is arranged at the bearing, the inlet end of the lubricant channel II (12) is arranged at the bearing, and the outlet end of the lubricant channel II is connected with the inlet end of the lubricating pump.
3. The dual power and ramp-up mode gas compression apparatus of claim 1, wherein: sealing rings I (15) are respectively arranged between the shell (1) at two sides of the bearing and the power shaft (7).
4. The dual power and ramp-up mode gas compression apparatus of claim 1, wherein: n is 3.
5. The dual power and ramp-up mode gas compression apparatus of claim 1, wherein: still including setting up traction liquid passageway I (23) on compressor support (18) and setting up traction liquid passageway II (24) in pivot I (19), the entry end of traction liquid passageway I (23) links to each other with traction liquid pump, and its one outlet end is towards the cylinder position of planet wheel (17), and its other outlet end links to each other with the entry end of traction liquid passageway II (24), and the exit end of traction liquid passageway II (24) sets up between the interface that pivot I (19) contacted with planet wheel (17), be provided with on casing (1) and be used for the traction liquid outlet (25) of traction liquid backward flow.
6. The dual power and ramp-up mode gas compression apparatus of claim 1, wherein: a sealing ring II (20) is arranged between the bracket (18) and the rotating shaft I (19), and the sealing ring II (20) is positioned between the speed increasing mechanism and the compressor impeller (10).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910046274.7A CN109654040B (en) | 2019-01-18 | 2019-01-18 | Dual-power and speed-raising type gas compression equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910046274.7A CN109654040B (en) | 2019-01-18 | 2019-01-18 | Dual-power and speed-raising type gas compression equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109654040A CN109654040A (en) | 2019-04-19 |
| CN109654040B true CN109654040B (en) | 2024-04-30 |
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| CN201910046274.7A Active CN109654040B (en) | 2019-01-18 | 2019-01-18 | Dual-power and speed-raising type gas compression equipment |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11920605B2 (en) | 2018-09-19 | 2024-03-05 | Borgwarner Inc. | Rotating machine and mating ring included therein |
| US11078807B2 (en) | 2018-09-19 | 2021-08-03 | Borgwarner Inc. | Turbocharger and mating ring included therein |
| US11384772B2 (en) | 2018-09-19 | 2022-07-12 | Borgwarner Inc. | Rotating machine and mating ring included therein |
| CN111503016A (en) * | 2020-04-16 | 2020-08-07 | 广东广顺新能源动力科技有限公司 | Throttling efficient compressed air system capable of controlling surge point |
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| US20060193739A1 (en) * | 2002-05-17 | 2006-08-31 | Normand Beaudoin | Retro mechanical post mechanical and bi-mechanical traction engines |
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| GB1009115A (en) * | 1962-08-03 | 1965-11-03 | Aktiebolget Volvo | Improvements in and relating to gas turbine plants |
| GB2103288A (en) * | 1981-05-01 | 1983-02-16 | George Basil Tsakiroglou | Rotary positive-displacement fluid-machines |
| RU2244138C2 (en) * | 2001-08-20 | 2005-01-10 | Чоповский Борис Петрович | Internal combustion engine (versions) |
| RU2243386C2 (en) * | 2002-02-18 | 2004-12-27 | Чоповский Борис Петрович | Internal combustion engine (versions) |
| WO2008045036A2 (en) * | 2006-10-05 | 2008-04-17 | Hinderks M V | Improved reciprocating devices |
| JP2016156300A (en) * | 2015-02-24 | 2016-09-01 | いすゞ自動車株式会社 | Bearing seal mechanism of mechanical supercharger for vehicle |
| CN205225435U (en) * | 2015-12-09 | 2016-05-11 | 刘银栓 | Internal -combustion engine air plenum and negative pressure exhaust structure |
| CN107893772A (en) * | 2017-10-09 | 2018-04-10 | 中国第汽车股份有限公司 | A kind of centrifugal fuel battery air compressor with energy recovery function |
| CN107946613A (en) * | 2017-11-15 | 2018-04-20 | 孙军 | A kind of fuel cell compressed air induction system of hydraulic drive |
| CN209510669U (en) * | 2019-01-18 | 2019-10-18 | 孙军 | A kind of double dynamical and raising speed mode gas compressing equipment |
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