CN102840137A - Steam drive type compression device - Google Patents
Steam drive type compression device Download PDFInfo
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- CN102840137A CN102840137A CN2012102070616A CN201210207061A CN102840137A CN 102840137 A CN102840137 A CN 102840137A CN 2012102070616 A CN2012102070616 A CN 2012102070616A CN 201210207061 A CN201210207061 A CN 201210207061A CN 102840137 A CN102840137 A CN 102840137A
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- dynamic formula
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- 230000006835 compression Effects 0.000 title claims abstract description 43
- 238000007906 compression Methods 0.000 title claims abstract description 43
- 238000010795 Steam Flooding Methods 0.000 title claims abstract description 41
- 238000009423 ventilation Methods 0.000 claims abstract description 56
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 7
- 238000001514 detection method Methods 0.000 abstract 1
- 230000030279 gene silencing Effects 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 2
- 101150064138 MAP1 gene Proteins 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 235000019628 coolness Nutrition 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
- F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
- F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C13/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01C13/04—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby for driving pumps or compressors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/22—Fluid gaseous, i.e. compressible
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/30—Casings or housings
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Positive-Displacement Air Blowers (AREA)
- Control Of Turbines (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a steam drive type compression device (1), which does not reverse on stop. The steam drive type compression device comprises a steam expansion machine (2) for converting expansion force of steam into rotation force; compressors (4, 5) driven by the steam expansion machine (2) to compress an object gas; an output path (9) for outputting the compressed object gas from the compressor (5), and provided with a check valve (8); and a ventilation path (12) branched from the output path (9) on the upstream side of the check valve (8), and opening outwards through a ventilation valve (10). The steam drive type compression device is characterized by comprising a steam control valve (14) for controlling the flow amount of the steam of the steam expansion machine (2); an output pressure detector (13) for detecting the pressure of the output path (9) on the upstream side of the check valve (8); and a stop control device (15) for opening the ventilation valve (10) until the detection value of the output pressure detector (13) is below the given setting pressure when the compressors (4, 5) stop driving.
Description
Technical field
The present invention relates to steam flooding dynamic formula compression set.
Background technique
In the device that uses the steam that produces by boiler, generally speaking, after middle pressure (for example 1.2-1.6MPa) the steam utilization reduction valve decompression with the boiler generation, low pressure (for example 0.8-0.9MPa) steam is supplied to the equipment that needs.If by reduction valve steam is reduced pressure, the energy that then is equivalent to the pressure difference of steam goes out of use, therefore, and the expectation recovered energy.
In patent documentation 1, put down in writing a kind of steam flooding dynamic formula compression set; It is through utilizing steam driven screw rod steam expansion machine (steam motor or steam terminal); Make the pressure energy of steam be transformed to rotating force and reclaim; And the rotating force that utilizes this steam expansion machine comes drive screw compressor (head, air end), thereby pressurized air.The steam flooding dynamic formula compression set of patent documentation 1 is provided with steam control valve in stream from steam to the steam expansion machine that supply with; Through this control valve being carried out PID control the pressure of the output stream of helical-lobe compressor is remained necessarily, thus the rotating speed of control steam expansion machine.
In such steam flooding dynamic formula compression set, stopping under the situation of its running, through making the steam control valve full cut-off, make the steam expansion machine not produce driving torque.Yet in the running halted state, under the high situation of the pressure of the output stream of helical-lobe compressor, the pressure of this output stream produces the torque of the rotor reverse that makes helical-lobe compressor.That is to say that if the pressure of output stream is high, helical-lobe compressor will move and reverse as screw expander.Under the state of steam control valve locking, the steam expansion machine does not produce torque, can not prevent the rotation of helical-lobe compressor.Therefore, traditionally steam flooding dynamic formula compression set is because the pressure of output stream and can not prevent that helical-lobe compressor from reversing.
According to the formation of steam flooding dynamic formula compression set, sometimes can not allow the reverse of such helical-lobe compressor.For example, in the oil free type helical-lobe compressor, adopt the seal construction that is called spiral seal sometimes, wherein, on rotor shaft or seal body, be provided with thread, utilize the rotation of rotor shaft that bearing oil or air are applied the pressure that moves to bearing from rotor chamber.In such helical-lobe compressor, if rotor shaft reverses, then spiral seal is expelled to the outside with the bearing oil of inside through being located near the atmosphere opening hole spiral seal etc.
Patent documentation 1 TOHKEMY 2009-250196 communique.
Summary of the invention
In view of foregoing problems, the steam flooding dynamic formula compression set that problem of the present invention does not reverse when being a kind of stopping to be provided.
In order to solve aforementioned problems, steam flooding dynamic formula compression set of the present invention has: the steam expansion machine that the expansive force of steam is transformed to rotating force; Drive the compressor of compressed object gas by said steam expansion machine; Export the output stream of compressed said object gas from said compressor, said output stream possesses safety check; At the upstream side of the said safety check ventilation stream from said output stream branch, said ventilation stream is opened to the outside through ventilation valve; It is characterized in that possessing: the steam control valve of flow that can control the said steam of said steam expansion machine; Detect the delivery pressure detector of the pressure of said output stream at the upstream side of said safety check; Stop control, when the driving of said compressor stopped, said stop control made said ventilation valve open, became below the given setting pressure up to the checkout value of said delivery pressure detector.
Constitute according to this, when compressor stops, opening ventilation valve the pressure of the output stream of compressor is reduced fully, therefore when the driving torque of screw expander disappeared, decompressor can not reverse owing to the pressure of output stream.
In addition, in steam flooding dynamic formula compression set of the present invention also can be, when the driving of said compressor stops, on one side said stop control reduces the aperture of said steam control valve gradually, Yi Bian the aperture of said ventilation valve is increased gradually.In this case, become given setting pressure when following, preferably make said steam control valve and said ventilation valve full cut-off at once at the checkout value of said delivery pressure detector.
According to this formation, make steam control valve locking gradually, make the driving torque that produces reduce gradually, make ventilation valve open gradually, make the pressure of output stream reduce gradually.Thus, the rotating speed of steam expansion machine and compressor is reduced smoothly.In addition, under the situation that the pressure of exporting stream fully reduces, make steam control valve and ventilation valve full cut-off at once, running is stopped fully, do not consume steam without rhyme or reason.
In addition; In steam flooding dynamic formula compression set of the present invention also can be; When the driving of said compressor stops; Said stop control makes said steam control valve locking so that said steam control valve becomes full cut-off with certain speed behind given set time, behind said set time, makes said ventilation valve open so that said ventilation valve becomes standard-sized sheet with certain speed simultaneously.In this case, preferably become given setting pressure and make said steam control valve and said ventilation valve full cut-off when following at once at the checkout value of said delivery pressure detector.
Constitute according to this, the minimizing of driving torque and the pressure of output stream can take place on the time span that equates more evenly reduce, therefore, the rotating speed of steam expansion machine and compressor is reduced smoothly.
Description of drawings
Fig. 1 is the summary pie graph of the steam flooding dynamic formula compression set of first mode of execution of the present invention.
Fig. 2 is the figure that the aperture of steam control valve and the ventilation valve of the running of the steam flooding dynamic formula compression set of illustrated view 1 when stopping to change.
Fig. 3 be the aperture of steam control valve and the ventilation valve of the running of the steam flooding dynamic formula compression set of displayed map 1 when stopping to change and illustration the figure of output pressure ratio situation about earlier descending shown in Figure 2.
Fig. 4 is the figure that changes with Fig. 2 and different aperture shown in Figure 3 of steam control valve and the ventilation valve of the running of the steam flooding dynamic formula compression set of illustrated view 1 when stopping.
Fig. 5 is the summary pie graph of the steam flooding dynamic formula compression set of second mode of execution of the present invention.
Label declaration
1,1a steam flooding dynamic formula compression set
2 steam expansion machines
4 first sections compressors
5 second sections compressors
8 safety check
9 output streams
10,16 ventilation valves
11,17 silencing apparatuss
12,18 ventilation streams
13 delivery pressure detectors
14 steam control valves
15 stop controls
19 intermediate pressure detectors.
Embodiment
Below will mode of execution of the present invention be described with reference to accompanying drawing.At first, the steam flooding dynamic formula compression set 1 that has shown first mode of execution of the present invention among Fig. 1.Steam flooding dynamic formula compression set 1 is with the compressed air production device of air as the object gas that will compress.
Steam flooding dynamic formula compression set 1 has steam expansion machine 2 and first section compressor 4 and second section compressor 5; Steam expansion machine 2 is transformed to rotating force with the expansive force of steam; First section compressor 4 and second section compressor 5 are driven by steam expansion machine 2 through gear 3, and air is compressed.Steam expansion machine 2 is in housing, to hold public female a pair of screw rotor, makes the screw expander of screw rotor rotation through making steam expansion in the confined space in the teeth groove of screw rotor.First section compressor 4 and second section compressor 5 are in housing, to hold public female a pair of screw rotor, through rotation drive screw rotor, compressed-air actuated helical-lobe compressor in the confined space in the teeth groove of screw rotor.
In steam flooding dynamic formula compression set 1, first section compressor 4 and second section compressor 5 are connected in series through intercooler 6.That is to say that the air of first section compressor 4 compression output utilizes second section compressor 5 further to compress after by intercooler 6 coolings.The pressurized air of second section compressor 5 output is sent to not shown storage through output stream 9, is supplied to the destination that needs from storage, wherein, in output stream 9, is provided with aftercooler 7 and safety check 8.Other air compression plant also can be connected to storage parallelly connectedly.
In addition, steam flooding dynamic formula compression set 1 has ventilation stream 12 between aftercooler 7 and safety check 8, and this ventilation stream 12 is connected to silencing apparatus 11 from output stream 9 branches through ventilation valve 10.That is to say that the end of ventilation stream 12 that is provided with silencing apparatus 11 is to atmosphere opening.
Further, in steam flooding dynamic formula compression set 1,, in more detail, between aftercooler 7 and ventilation stream 12, possesses the delivery pressure detector 13 that detects compressed-air actuated pressure P d at the upstream side of the safety check 8 of exporting stream 9.Further, in steam flooding dynamic formula compression set 1, in the stream that steam is supplied to steam expansion machine 2, be provided with and regulate the steam control valve 14 of controlling steam flow through aperture.
And steam flooding dynamic formula compression set 1 possesses stop control 15, and this stop control 15 is transfused to the checkout value Pd of delivery pressure detector 13, the aperture of control ventilation valve 10 and steam control valve 14.In addition, shut down in order to indicate steam flooding dynamic formula compression set 1, the stop signal that operations of operators produces or not shown peripheral control unit is exported is transfused to stop control 15.
As shown in Figure 2, in case be transfused to stop signal, stop control 15 little by little diminishes the aperture of steam control valve 14 with certain speed behind predetermined set time (for example 5 seconds), makes steam control valve 14 become full cut-off.Simultaneously, after set time, that is to say that when steam control valve 14 became full cut-off, stop control 15 became greatly the aperture of ventilation valve 10 with certain speed gradually, makes ventilation valve 10 become standard-sized sheet.
In addition, if the checkout value of delivery pressure detector 13 becomes below the given setting pressure (for example 0.01MPa), then stop control 15 makes ventilation valve 10 full cut-offs at once.This setting pressure is set to fully low pressure, even make that the driving torque of steam expansion machine 2 is zero, first section compressor 4 and second section compressor 5 can not reverse because of the pressure of output stream 9 yet, not that is to say and can be driven as the steam expansion machine.
In this mode of execution, because the pressure that makes ventilation valve 10 be open into output stream 9 reduces fully, therefore first section compressor 4 and second section compressor 5 can not reverse owing to the pressure of output stream 9.
In addition, because stop control 15 little by little changes the aperture of steam control valve 14 and ventilation valve 10, so the load torque of the driving torque of steam expansion machine 2 or first section compressor 4 and second section compressor 5 can not change sharp.Therefore, in steam flooding dynamic formula compression set 1, the rotating speed of steam expansion machine 2, first section compressor 4 and second section compressor 5 is not stopped on drastic change ground smoothly.
In addition; Checkout value through delivery pressure detector 13 before the set time becomes under the situation below the setting pressure, and stop control 15 can that is to say through after the set time; Becoming full cut-off and ventilation valve 10 from steam control valve 14 becomes after the standard-sized sheet; Make ventilation valve 10 lockings, also can be as shown in Figure 3, do not wait until through preset time to make steam control valve 14 full cut-offs at once and make ventilation valve 10 full cut-offs at once.
Under the situation that the pressure of exporting stream 9 reduces fully, owing to there is not the worry of the reverse of decompressor 4,5, can make steam control valve 14 full cut-offs immediately, suppress steam consumption for no reason.
In addition, the rotating speed of not worrying steam expansion machine 2, first section compressor 4 and second section compressor 5 changes because of conditions such as the inertial force of the screw rotor of steam expansion machine 2, first section compressor 4 and second section compressor 5 etc. or running pressure sharp.In this case, also can make steam control valve 14 full cut-offs and make ventilation valve 10 standard-sized sheets in the moment of input stop signal.
For example, as shown in Figure 4, if also can constitute input stop signal then ventilation valve 10 switches to full cut-off from standard-sized sheet at once.In this case; Compare with the situation that the aperture that makes ventilation valve 10 shown in Figure 3 gradually changes with Fig. 2; The load torque of first section compressor 4 and second section compressor 5 produces a little change, can adopt cheap electromagnetic opening and closing valve can make the advantage that constitutes simplification as ventilation valve 10 grades but have.
In addition, the steam flooding dynamic formula compression set 1a that in Fig. 5, has shown second mode of execution of the present invention.Therefore the steam flooding dynamic formula compression set 1 of this steam flooding dynamic formula compression set 1a and first mode of execution gives identical symbol for identical constituting component all identical aspect the formation of majority, omits repeat specification.
The steam flooding dynamic formula compression set 1a of this mode of execution has ventilation stream 18, this ventilation stream 18 from the intermediate flow passage that connects first section compressor 4 and second section compressor 5, in the downstream side of intercooler 6 branch, be connected to silencing apparatus 17 through ventilation valve 16.The end of end and ventilation stream 12 of ventilation stream 18 that is provided with silencing apparatus 17 is likewise to atmosphere opening.
In addition, steam flooding dynamic formula compression set 1a possesses intermediate pressure detector 19, and this intermediate pressure detector 19 is used to detect the delivery pressure of first section compressor 4, promptly connects the pressure P m of the intermediate flow passage of first section compressor 4 and second section compressor 5.And the checkout value Pm of this intermediate pressure detector 19 is input to stop control 15.
If the stop control of this mode of execution 15 is transfused to stop signal, then makes little by little locking of steam control valve 14, and make ventilation valve 10 and ventilation valve 16 little by little open.In this mode of execution, the checkout value Pd of delivery pressure detector 13 and the checkout value Pm of intermediate pressure detector 19 are set at respectively is used to the setting value of judging that pressure fully reduces.
And ventilation valve 10 is reduced under the situation below the setting value and becomes full cut-off being transfused to the checkout value Pd that begins through preset time or delivery pressure detector 13 from stop signal.In addition, ventilation valve 16 is reduced under the situation below the setting value and becomes full cut-off being transfused to the checkout value Pm that begins through preset time or intermediate pressure detector 19 from stop signal.Further, steam control valve 14 is reduced to below the setting value or the checkout value Pm of intermediate pressure detector 19 is reduced under the situation of any one state below the setting value and becomes full cut-off being transfused to the checkout value Pd that begins through preset time or delivery pressure detector 13 from stop signal.
Like this, distinguish the delivery pressure that fully reduces each section compressor, can prevent more reliably that steam flooding dynamic formula compression set from reversing when stopping through open ventilation valve.
In addition, in the present invention, the formation of above-mentioned mode of execution and the detail section of controlling method also can be applicable to other mode of execution respectively.
Claims (4)
1. steam flooding dynamic formula compression set has:
The expansive force of steam is transformed to the steam expansion machine of rotating force;
Drive the compressor of compressed object gas by said steam expansion machine;
Export the output stream of compressed said object gas from said compressor, said output stream possesses safety check;
At the upstream side of the said safety check ventilation stream from said output stream branch, said ventilation stream is opened to the outside through ventilation valve;
It is characterized in that possessing:
Can control the steam control valve of flow of the said steam of said steam expansion machine;
Detect the delivery pressure detector of the pressure of said output stream at the upstream side of said safety check;
Stop control, when the driving of said compressor stopped, said stop control made said ventilation valve open, became below the given setting pressure up to the checkout value of said delivery pressure detector.
2. steam flooding dynamic formula compression set as claimed in claim 1 is characterized in that, when the driving of said compressor stops, on one side said stop control reduces the aperture of said steam control valve gradually, Yi Bian the aperture of said ventilation valve is increased gradually.
3. steam flooding dynamic formula compression set as claimed in claim 1; It is characterized in that; When the driving of said compressor stops; Said stop control makes said steam control valve locking so that said steam control valve becomes full cut-off with certain speed behind given set time, behind said set time, makes said ventilation valve open so that said ventilation valve becomes standard-sized sheet with certain speed simultaneously.
4. like claim 2 or 3 described steam flooding dynamic formula compression sets, it is characterized in that,, make said steam control valve and said ventilation valve become full cut-off at once when the checkout value of said delivery pressure detector becomes given setting pressure when following.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011138822A JP5568518B2 (en) | 2011-06-22 | 2011-06-22 | Steam-driven compressor |
| JP2011-138822 | 2011-06-22 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102840137A true CN102840137A (en) | 2012-12-26 |
| CN102840137B CN102840137B (en) | 2015-04-01 |
Family
ID=47367794
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210207061.6A Active CN102840137B (en) | 2011-06-22 | 2012-06-21 | Steam drive type compression device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5568518B2 (en) |
| KR (1) | KR101319055B1 (en) |
| CN (1) | CN102840137B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105556196A (en) * | 2013-07-25 | 2016-05-04 | Corac能源技术有限公司 | System, method and apparatus |
| CN112983790A (en) * | 2020-06-29 | 2021-06-18 | 株式会社神户制钢所 | Stop control method for compressor unit and compressor unit |
| CN114483612A (en) * | 2022-03-04 | 2022-05-13 | 中国商用飞机有限责任公司 | Aerodynamic turbine compression system |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20150004590U (en) | 2014-06-17 | 2015-12-28 | 현대중공업 주식회사 | Apparatus for material transport |
| JP6513345B2 (en) * | 2014-07-03 | 2019-05-15 | ナブテスコ株式会社 | Air compressor |
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| JP4745812B2 (en) | 2005-12-15 | 2011-08-10 | 三菱重工業株式会社 | Combined power generation system and method of operating combined power generation system |
| BE1017600A3 (en) * | 2007-05-15 | 2009-01-13 | Atlas Copco Airpower Nv | METHOD FOR CONTROLLING A TURBO COMPRESSOR. |
| JP5415484B2 (en) * | 2011-06-22 | 2014-02-12 | 三浦工業株式会社 | Steam system |
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2011
- 2011-06-22 JP JP2011138822A patent/JP5568518B2/en active Active
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2012
- 2012-06-21 CN CN201210207061.6A patent/CN102840137B/en active Active
- 2012-06-21 KR KR1020120066835A patent/KR101319055B1/en active IP Right Grant
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| JPH0466796A (en) * | 1990-07-06 | 1992-03-03 | Hitachi Ltd | Method and device for control in compression equipment |
| JPH08219088A (en) * | 1995-02-16 | 1996-08-27 | Mitsubishi Heavy Ind Ltd | Multistage compression device and operation control method thereof |
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| CN112983790A (en) * | 2020-06-29 | 2021-06-18 | 株式会社神户制钢所 | Stop control method for compressor unit and compressor unit |
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| CN114483612B (en) * | 2022-03-04 | 2024-01-05 | 中国商用飞机有限责任公司 | Aerodynamic turbine compression system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013007285A (en) | 2013-01-10 |
| KR101319055B1 (en) | 2013-10-17 |
| KR20130000354A (en) | 2013-01-02 |
| JP5568518B2 (en) | 2014-08-06 |
| CN102840137B (en) | 2015-04-01 |
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Effective date of registration: 20220215 Address after: Tokyo, Japan Patentee after: Shengang Compressor Co.,Ltd. Patentee after: Three Pu Industrial Corporation Address before: Kobe City, Hyogo Prefecture, Japan Patentee before: Kobe Steel, Ltd. Patentee before: Three Pu Industrial Corporation |