CN102072186B - Volume control method for multistage centrifugal compressor - Google Patents
Volume control method for multistage centrifugal compressor Download PDFInfo
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Abstract
The invention provides a volume control method for a multistage centrifugal compressor, in the volume control method of the multistage centrifugal compressor provided with inlet guiding blades disposed at a suction part in each stage of the multistage centrifugal compressor, a ratio of the angle of the inlet guiding blades in each stage relative to an angle of referential inlet guiding blades are controlled, making each stage be at a preset fixed ratio. Further, the fixed ratio in every stage is set to become smaller with the rear stage directing toward a downstream side. According to the volume control method for the multistage centrifugal compressor, pressure wave can be prevented via simple and effective control of the inlet guiding blades, and operation range is enlarged via enlargement of throttling range of volume.
Description
Technical field
The present invention relates to a kind of capacity control method of multistage centrifugal compressor of the inlet guide vane with each section sucting place that is arranged on the multistage centrifugal compressor, more specifically, relate to that pressure wave is avoided in a kind of simple control that can utilize above-mentioned inlet guide vane and the capacity control method that enlarges the multistage centrifugal compressor of operating range.
Background technique
In the various device of chemical device etc., for the raw air compression with and the pressurized gas of the volumes such as manufacturing works' air-source or various high pressurized gas, use the multistage centrifugal compressor.Have in the multistage centrifugal compressor of the suction pipe that sucks gas in the suction side of compressor body, in the past since, the capacity control mechanism that flow, pressure are changed is at suction pipe ingress inlet porting guide vane.
But, usually have the pressure wave phenomenon in centrifugal compressor, so the capacity regulating scope is restricted.Therefore, expectation can have wider capacity regulating scope.On the other hand, also need to be devoted to make the efficient under sub load to improve.At first, carry out following explanation for the capacity control method for the centrifugal compressor of the prior art of last expectation.
in the capacity control method of the described centrifugal compressor of Japanese JP 8-14279 communique, on the blade angle plane that is determined by the angle of inlet guide vane and diffuser (デ イ Off ユ ザ) blade, preset the also pressure swash in store predetermined pressure wave zone, therefore measure above-mentioned inlet guide vane and diffuser vane when lower angle and these are when in lower angle enters fixed by above-mentioned pressure wave wire gauge above-mentioned pressure wave zone, eliminate as pressure wave and obtain with blade angle operation amount vector the vector that following vector is the Normal direction of above-mentioned pressure swash, outside above-mentioned pressure wave zone, it is the operation amount of the angle of the adjustment inlet guide vane necessary in order to go out from the pressure wave zone and diffuser vane.
on the other hand, above-mentioned near lower angle is positioned at the extra-regional above-mentioned pressure swash of above-mentioned pressure wave when what measure, and the blade angle operation amount vector that is used for the head for target flow and determines is in above-mentioned pressure wave zone the time, remove the Normal direction composition of above-mentioned pressure swash based on above-mentioned pressure swash from above-mentioned blade angle operation amount vector and try to achieve along the pressure wave of above-mentioned pressure swash direction and avoid with blade angle operation amount vector, eliminate with blade angle operation amount vector or pressure wave based on above-mentioned pressure wave and avoid the above-mentioned inlet guide vane that determines with blade angle operation amount vector and the angle of diffuser vane, control the flow of above-mentioned centrifugal compressor.
But, in order to carry out above-mentioned control, need a plurality of senior arithmetic units and be used for mensuration as the measuring appliance of the various measured values of the input value of this arithmetic unit, need very large expense.In addition, there is tentative wrong action in control, needs certain hour so divide a word with a hyphen at the end of a line to steady state.
Then, be directed to the capacity control method of No. 2000-291597 described multistage centrifugal compressor of TOHKEMY of an above-mentioned rear expectation in following explanation with reference to accompanying drawing 9.Fig. 9 means the sectional view of structure example of the used for refrigerator multistage compressor of the prior art.
In capacity control device in the used for refrigerator multistage compressor of the prior art of Fig. 9, there is no the significantly very low hot gas by-pass collar of installation efficiency in order to provide a kind of, can have high energy saving and can have capacity control device in the used for refrigerator multistage compressor of wide volume controlled, have following function.Namely, this used for refrigerator multistage compressor has following structure: centered by motor 18 and configure respectively at its two ends possess more than one impeller 22,23,32 low band side compression unit 20 and high section layer compression unit 30, and this two compression unit 20, the running shaft of 30 impeller and the running shaft 19 of this motor 18 directly link.
And, capacity control device in the used for refrigerator multistage compressor of the prior art is, suction blade 24,33 is installed respectively at suction port 31a place at the suction port 21a of low band side compression unit 20 and high band side compression unit 30, via controlling motor 27,36 and by the switching from the control signal control and suck blade 24,33 of control panel 44.Be provided in that temperature controllers in above-mentioned control panel 44 are used to from the detected temperatures of temperature detection end and open and close signals to control motor 27 outputs of low band side.In addition, the potentiometer in the control motor 27 of low band side is to the balance adjustment mechanism output aperture signal that is provided in above-mentioned control panel 44.Above-mentioned balance adjustment mechanism opens and closes signal in order to be identical aperture with the aperture signal of low band side to control motor 36 outputs of high band side.
For the capacity control device in the used for refrigerator multistage compressor of the prior art of Fig. 9, when carrying out the Flow-rate adjustment of compressor, the suction blade 24,33 of low pressure stage and high pressure section is controlled to be has identical aperture, but in the time will utilizing this method to reduce the control of flow, exist the section of a side only at first to enter pressure wave zone, the problem that narrows down of the minimizing scope of flow sometimes.
Summary of the invention
Therefore, the object of the present invention is to provide a kind of capacity control method of multistage centrifugal compressor, in the capacity control method of the multistage centrifugal compressor of the inlet guide vane with each section sucting that is arranged on the multistage centrifugal compressor, can avoid pressure wave by simply and effectively controlling above-mentioned inlet guide vane, expand jumbo throttling band and make operating range more strengthen.
The controlling method of the present invention that is used for realizing above-mentioned purpose is a kind of capacity control method of multistage centrifugal compressor of the inlet guide vane with each section sucting that is arranged on the multistage centrifugal compressor, wherein, control the angle of above-mentioned inlet guide vane of each section with respect to the ratio of benchmark inlet guide vane angle, make the predefined fixed ratio of each Duan Douwei.
According to such method, each section can both carry out leaving from the pressure swash running of the allowance of par, only can prevent specific section at first near the situation of pressure swash, and can increase the throttling band of capacity.
In the capacity control method of multistage centrifugal compressor of the present invention, preferably the above-mentioned fixed ratio of each section is set as along with towards the back segment in downstream side and diminish.
According to such method, can effectively and reliably regulate when the setting of the volume controlled of carrying out above-mentioned compressor.
Description of drawings
Fig. 1 is the schematic configuration diagram that schematically represents the structure of embodiments of the present invention 1 or 3 described four sections centrifugal compressors.
Fig. 2 is embodiments of the invention, is in general multistage centrifugal compressor, the angle of guide vane to be represented the performance chart of the variation of flow-pressure characteristic as parameter.
Fig. 3 means the figure of an example of the flow-pressure characteristic of the pressurized gas in the equipment that multistage centrifugal compressor shown in Figure 2 supplies with.
Fig. 4 is comparative example of the present invention, is illustrated in the operation point of each section when carrying out volume controlled in the multistage centrifugal compressor of the performance with Fig. 2, the operation point of figure (a) expression first paragraph compressor, the operation point of figure (b) expression second segment compressor.
Fig. 5 is comparative example of the present invention, and expression has the operation point of each section when carrying out volume controlled in the multistage centrifugal compressor of performance of Fig. 2, the operation point of the 3rd section compressor of figure (c) expression, the operation point of the 4th section compressor of figure (d) expression.
Fig. 6 is embodiments of the invention, and expression has the operation point of each section when carrying out volume controlled in the multistage centrifugal compressor of performance of Fig. 2, the operation point of figure (a) expression first paragraph compressor, the operation point of figure (b) expression second segment compressor.
Fig. 7 is embodiments of the invention, and expression has the operation point of each section when carrying out volume controlled in the multistage centrifugal compressor of performance of Fig. 2, the operation point of the 3rd section compressor of figure (c) expression, the operation point of the 4th section compressor of figure (d) expression.
Fig. 8 is the schematic configuration diagram of structure that schematically represents four sections centrifugal compressors of embodiments of the present invention 2.
Fig. 9 means the sectional view of structure example of the used for refrigerator multistage compressor of prior art.
Embodiment
At first, as the example of four sections centrifugal compressors that are applied to the booster engine internally-arranged type, the capacity control method of the described multistage centrifugal compressor of embodiments of the present invention 1 is carried out following explanation with reference to Fig. 1.Fig. 1 is the schematic configuration diagram that schematically represents the structure of the described four sections centrifugal compressors of embodiments of the present invention 1.
In the described four sections centrifugal compressors of embodiments of the present invention 1, drive input shaft 5 by motor 6, via booster engine 16 transferring power, first paragraph compressor 1, second segment compressor 2, the 3rd section compressor 3 and the 4th section compressor 4 are by speedup.The suction port place of above-mentioned the first～four section compressor 1～4 is respectively arranged with inlet guide vane 7～10 and is used for these guide vane operator 11～14 of operation.
The gas that is inhaled into via the inlet guide vane 7 of the sucting that is arranged on above-mentioned first paragraph compressor 1 is after being compressed by above-mentioned first paragraph compressor 1, be discharged to not shown first paragraph and discharge stream, then the inlet guide vane 8 via the sucting that is arranged on second segment compressor 2 is imported into second segment compressor 2.And the gas that is inhaled into via above-mentioned inlet guide vane 8 utilizes above-mentioned second segment compressor 2 to be further compressed, and is discharged to afterwards not shown second segment and discharges stream, is directed to the 3rd section compressor 3 via inlet guide vane 9.
And then, the gas that repeatedly carries out above-mentioned identical compression process continuously and be compressed to high pressure in above-mentioned the 3rd section compressor 3 and the 4th section compressor 4 is discharged to not shown the 4th section of the 4th section compressor 4 and discharges stream, and finally supplies to the 4th section and discharge the demand end (equipment etc.) that stream is communicated with.
On the other hand, have controller 15 in the 4th section centrifugal compressor, taken in advance in this controller 15: arithmetical organ, by consisting of based on a plurality of program schemas of the angle of the above-mentioned inlet guide vane 7～10 of command signal computing; And control mechanism, can export control signals to above-mentioned guide vane operator 11～14 respectively based on the operation result of this arithmetical organ.
And, if the command signal from equipment side to these controller 15 inputs " carrying the gas of how much pressure of how many flows " based on this command signal, is tried to achieve the angle of inlet guide vane 7～10 by above-mentioned arithmetical organ.At this moment, the angle of above-mentioned inlet guide vane of selecting to make each section for each section program schema of pre-set fixed ratio all, is carried out the computing based on this program with respect to the ratio of benchmark inlet guide vane angle.The value of these fixed ratios just can not change as long as command signal is constant.Then, this operation result is imported into above-mentioned control mechanism, and this control mechanism is controlled to guiding vane operation device 11～14 output control signals respectively.
Namely, in the capacity control method of the multistage centrifugal compressor of embodiments of the present invention 1, utilization is accommodated in the angle of the above-mentioned inlet guide vane 7～10 of above-mentioned arithmetical organ computing in controller 15, and respectively export control signal from above-mentioned control mechanism to guiding vane operation device 11～14 based on this operation result, utilize this control signal operational guidance blade 11～14 respectively.
And, utilize the operation of above-mentioned guide vane operator 11～14, control respectively inlet guide vane 7～10 and carry out the capacity regulating of each section of compressor.Its result, each section can both carry out having apart from the pressure swash running of the allowance of par, can prevent that only specific section at first near the situation of pressure swash, can increase the throttling band of capacity.
In addition, in the capacity control method of the described multistage centrifugal compressor of mode of execution 1 of the invention described above, the situation of the centrifugal compressor of four sections has been described, but so long as the multistage centrifugal compressor of a plurality of sections that has more than two sections just can both use the present invention.In addition, the embodiment who is provided with guide vane and guide vane operator in whole sections of multistage centrifugal compressor has been described, but above-mentioned guide vane and guide vane operator might not arrange all in section all also.
[embodiment]
Then explanation has been used the comparative example of above-mentioned prior art 2 and has used embodiments of the invention in having inlet guide vane and having the general multistage centrifugal compressor of the compressor characteristics shown in Fig. 2,3.Fig. 2 is embodiments of the invention, mean the angle that makes guide vane in general multistage centrifugal compressor as parameter and the performance chart of the variation of flow rate pressure, Fig. 3 means the figure of an example of the flow-pressure characteristic of the pressurized gas in the equipment that multistage centrifugal compressor shown in Figure 2 supplies with.
The performance of this multistage centrifugal compressor as shown in Figure 2, along with the angle of guide vane becomes large from-30 degree to 60 degree, discharge flow rate, head pressure all descend.In addition, in each guide vane angle, if the throttling discharge flow rate arrives the pressure swash shown in the dot and dash line in figure and produces the pressure wave phenomenon.In addition, generally speaking, if the flow of the pressurized gas that uses in equipment reduces, as shown in Figure 3, the head pressure of the compressor of trying to achieve has the tendency that reduces a little.In addition, sometimes with respect to the discharge flow rate Qd of specified operating condition, use under operating condition Q1, the Q2 of sub load.
＜comparative example 〉
At first, use the comparative example of prior art 2 with reference to Fig. 4,5 explanations in above-mentioned multistage centrifugal compressor.Fig. 4, the 5th, comparative example of the present invention, be illustrated in the operation point of each section when carrying out volume controlled in the multistage centrifugal compressor of the performance with Fig. 2, the operation point of Fig. 4 (a) expression first paragraph compressor, the operation point of Fig. 4 (b) expression second segment compressor, the operation point of the 3rd section compressor of Fig. 5 (c) expression, the operation point of the 4th section compressor of Fig. 5 (d) expression.
That is, Fig. 4,5 be illustrated in guide vane in the multistage centrifugal compressor with above-mentioned characteristic angle all section be all the situations that 30 degree ground are controlled.The operation point of first paragraph compressor is positioned near the pressure swash shown in dot and dash line as shown in Fig. 4 (a), and is very little apart from the flow allowance sm1 of pressure swash.That is, under the few discharge flow rate of specific discharge Q1, pressure wave can occur, can't turn round.
On the other hand, in the second～four section compressor, all the flow allowance sm1 than first paragraph compressor is large to each allowance sm2～sm4 of pressure swash, also has nargin with respect to the running of small flow more as can be known.That is, be expressed as more by the larger tendency of back segment apart from the flow allowance of pressure swash, arrive at the first paragraph compressor under the discharge flow rate of pressure swash, the flow allowance sm4 of the 4th section compressor also also has sufficient allowance.
＜embodiment 〉
Then with reference to Fig. 6,7 applications embodiments of the invention.Fig. 6, the 7th, embodiments of the invention, be illustrated in the operation point of each section in the situation of having carried out volume controlled in the multistage centrifugal compressor of the performance with Fig. 2, the operation point of Fig. 6 (a) expression first paragraph compressor, the operation point of Fig. 6 (b) expression second segment compressor, the operation point of the 3rd section compressor of Fig. 7 (c) expression, the operation point of the 4th section compressor of Fig. 7 (d) expression.
Namely, in having used embodiments of the invention, in having the multistage centrifugal compressor of above-mentioned characteristic, the set angle of controlling the inlet guide vane 7～10 that makes each section is all predefined fixed ratio in each section with respect to benchmark inlet guide vane angle.That is, be controlled to be the value shown in following formula (1)～(4).
f(1st)＝a×f(base) (1)
f(2nd)＝b×f(base) (2)
f(3rd)＝c×f(base) (3)
f(4th)＝d×f(base) (4)
At this, f (base): guide vane benchmark set angle
F (1st): first paragraph compressor guide vane set angle
F (2nd): second segment compressor guide vane set angle
F (3rd): the 3rd section compressor guide vane set angle
F (4th): the 4th section compressor guide vane set angle
A, b, c, d: proportionality constant
Command signal (requiring flow etc.) from equipment is imported into controller 15, and utilization is accommodated in the arithmetical organ in above-mentioned controller 15 and calculates above-mentioned f (base) based on this command signal.Value with respect to the optimal f of the flow that requires (base) depends on the characteristic of equipment and the characteristic of compressor.Therefore, for example try to achieve optimal f (base) value corresponding with requiring flow in experiment in advance, and it is kept in arithmetical organ.
Then, calculate the angle of the guide vane of each section of compressor from following formula (1)～(4), utilization is accommodated in the control mechanism in above-mentioned controller 15 and exports control signals to the guide vane operator 11～14 of each section.
During operation point Q1 in Fig. 6,7, if be set as a=1.15, b=1.05, c=0.95, d=0.85, f (base)=30[degree] time,
F (1st)=34.5[degree]
F (2nd)=31.5[degree]
F (3rd)=28.5[degree]
F (4th)=25.5[degree]
As shown in Fig. 6,7, the flow allowance sm1～sm4 apart from the pressure swash of each of operation point Q1 section is par, yet has allowance at this operation point Q1 place apart from the pressure swash, even if also can turn round under the operation point Q2 of the further throttling of flow.That is, according to the present invention, can realize the increase of the flow control scope of compressor.
In addition, even if the capacity control method of multistage centrifugal compressor of the present invention does not use the control of the complexity shown in above-mentioned prior art 1 can carry out sufficient flow control yet.Generally speaking, when requiring flow-pressure characteristic shown in Figure 2, above-mentioned constant a～d can more effectively control flow when setting in the mode that satisfies following formula (5).
a＞b＞c＞d (5)
Generally speaking, in multistage centrifugal compressor of the present invention, even if when the inlet pressure of its first paragraph compressor is most, the discharge flow rate variation also changes hardly.But the head pressure of trying to achieve reduces along with the minimizing of discharge flow rate as shown in Figure 3.Therefore, if the flow of the pressurized gas that uses in equipment reduces, the head pressure of the compressor of each section also reduces.The value of the ratio of the volume flowrate when specified of the volume flowrate of the inlet side of the second segment compressor of this moment is larger than this value of first paragraph compressor.After the value of above-mentioned ratio one section larger than the last period, this in the compressor of the 3rd section later high pressure section (back segment in downstream side) too.That is, have more by the back segment operation point apart from pressure swash tendency far away.If consider above situation, be set as that to satisfy above-mentioned formula (5) more effective.
The capacity control method of the multistage centrifugal compressor of embodiments of the present invention 2 then, is described with reference to accompanying drawing 8.
wherein, embodiments of the present invention 2 are with above-mentioned mode of execution 1 difference, embodiments of the present invention 1 are the multistage centrifugal compressor of booster engine internally-arranged type, with respect to this, it is the multistage centrifugal compressor of monaxon in mode of execution 2, in addition as described later, above-mentioned mode of execution 1 constitutes the guide vane of each section and is all controlled by different independently guide vane operators, with respect to this, in mode of execution 2, has the formation of a part of controlling the guide vane of multistage by public guide vane operator, be identical formation with above-mentioned mode of execution 1 beyond these are different, so difference is described following for the parts identical reference character of mark identical with above-mentioned mode of execution 1.
Namely, in above-mentioned mode of execution 1, guide vane 7～10 with each section is directed to the formation that vane operation device 11～14 is controlled independently, with respect to this, in mode of execution 2, constitute and utilize linkage mechanism etc., first and third section compressor 1,3 guide vane 7,9 by public guide vane operator 50, second, four section compressor 2,4 guide vane 8,10 by another public guide vane operator 51 operations.
And, the capacity control method of the multistage centrifugal compressor of embodiments of the present invention 2 is, the angle of the guide vane 7～10 that links in this wise is controlled to be the value shown in following formula (6), (7) in order to become the mode of equal angular with aforementioned link mechanism.
f(1st)＝f(3rd)＝a×f(base) (6)
f(2nd)＝f(4th)＝b×f(base) (7)
Therefore, the capacity control method of 2 described multistage centrifugal compressors according to the embodiment of the present invention is even if the multistage centrifugal compressor of the wider scope beyond above-mentioned mode of execution 2 also can be used capacity control method of the present invention.
The capacity control method of the multistage centrifugal compressor of embodiments of the present invention 3 then, is described with reference to front Fig. 1.
Wherein, embodiments of the present invention 3 are with above-mentioned mode of execution 1 difference, use above-mentioned (1)～(4) to calculate the set angle of inlet guide vane 7～10 in embodiments of the present invention 1, with respect to this, in mode of execution 3, shown in (8)～(11), be multiplication by constants after trigonometric function tan with the value transform of angle, recycling inverse trigonometrical function atan again conversion itself and calculate.As trigonometric function, except tan, can be also sin and cos.
f(1st)＝atan[a×tan{f(base)}] (8)
f(2nd)＝atan[b×tan{f(base)}] (9)
f(3rd)＝atan[c×tan{f(base)}] (10)
f(4th)＝atan[d×tan{f(base)}] (11)
Computing is complicated a little, but the capacity control method of mode of execution above-mentioned according to the characteristic of compressor 3 can make the range of flow of multistage centrifugal compressor become wider sometimes.The characteristic of such centrifugal compressor below is described.
At first, the pressure head of centrifugal compressor (pressure is closely related with discharging) H is proportionate relationship with the right as shown in following (12).
H∝U2·Cu2-U1·Cu1 (12)
At this, U2 and U1 represent the peripheral velocity (peripheral speed) of impeller eye and outlet, if rotating speed one rule is irrelevant and identical with the angle of guide vane.Cu2 is all durection components of decision speed of the gas of impeller outlet, changes a little but does not have large variation according to flow condition etc.On the other hand, Cu1 is all durection components of absolute velocity of the gas of impeller eye, if the angle of guide vane is that 0 degree is also 0.Utilize this guide vane and control the value of above-mentioned Cu1 based on the flow control of guide vane, large if the value of Cu1 becomes, from following formula (12) as can be known the value of H diminish, head pressure reduces.Thus, make operation point change and what carry out Flow-rate adjustment is that guide vane is controlled.
If inflow velocity is identical, all durection components and tan{f (base) } proportional, the angle of guide vane is before 0～45 about degree, angle and tan{f (base) } the variation ratio equal, if but above-mentioned angle becomes 60 about degree, tan{f (base) } the increasing amount of increasing amount and angle self compare and become large.When the delicate variation of the angle under having such angle brings the multistage centrifugal compressor of compressor characteristics of very large impact to operation point, use the capacity control method of the embodiments of the present invention 3 of following formula (8)～(11) sometimes to become effective.
In such mode of execution 3, finally also to can be described as in each section be all predefined fixed ratio to the relation of the angle of the above-mentioned inlet guide vane of each section and benchmark inlet guide vane angle.
As described above, capacity control method according to multistage centrifugal compressor of the present invention, be certain ratio with the relative proportional control of each section of the angle of inlet guide vane, so each section can both carry out having apart from the pressure swash running of the allowance of par, only can prevent specific section at first near the pressure swash, and can increase the throttling band of capacity.In addition, capacity control method according to multistage centrifugal compressor of the present invention, the relative ratio of each section of above-mentioned angle is set as along with towards the back segment in downstream side and diminish, so can effectively and reliably regulate when the setting of the volume controlled of carrying out above-mentioned compressor.
Claims (1)
1. the capacity control method of a multistage centrifugal compressor, described multistage centrifugal compressor has the inlet guide vane of each section sucting that is arranged on the multistage centrifugal compressor,
Be the predefined fixed ratio of each Duan Douwei with the angle of the above-mentioned inlet guide vane of each section and the rate control of benchmark inlet guide vane angle,
The predefined fixed ratio of each section is set as along with towards the back segment in downstream side and diminish.
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| JP2009-267745 | 2009-11-25 | ||
| JP2009267745A JP4963507B2 (en) | 2009-11-25 | 2009-11-25 | Capacity control method of multistage centrifugal compressor |
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| CN102072186B true CN102072186B (en) | 2013-11-06 |
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| TWI507606B (en) * | 2012-01-20 | 2015-11-11 | Ind Tech Res Inst | Multiple capacity centrifugal compressor and control method thereof |
| JP5611253B2 (en) | 2012-02-23 | 2014-10-22 | 三菱重工業株式会社 | Compressor control device, control method therefor, and compressor system |
| JP7157589B2 (en) * | 2018-08-13 | 2022-10-20 | 三菱重工サーマルシステムズ株式会社 | Control device, refrigerator, control method and abnormality detection method |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0661426B1 (en) * | 1993-12-28 | 1998-05-20 | Hitachi, Ltd. | Gas turbine apparatus and method of operating same |
| CN1459573A (en) * | 2002-05-22 | 2003-12-03 | 日立产业有限公司 | Turbocompressor and volum controlling method thereof |
| CN1542290A (en) * | 2003-04-30 | 2004-11-03 | 奥尔塞特工程有限公司 | Compressor |
| CN1650105A (en) * | 2002-08-12 | 2005-08-03 | 日立产业有限公司 | Turbocompressor and its operation method |
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| JP2008121451A (en) * | 2006-11-09 | 2008-05-29 | Mitsubishi Heavy Ind Ltd | Turbo refrigeration device and method of controlling the same |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0661426B1 (en) * | 1993-12-28 | 1998-05-20 | Hitachi, Ltd. | Gas turbine apparatus and method of operating same |
| CN1459573A (en) * | 2002-05-22 | 2003-12-03 | 日立产业有限公司 | Turbocompressor and volum controlling method thereof |
| CN1650105A (en) * | 2002-08-12 | 2005-08-03 | 日立产业有限公司 | Turbocompressor and its operation method |
| CN1542290A (en) * | 2003-04-30 | 2004-11-03 | 奥尔塞特工程有限公司 | Compressor |
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| JP4963507B2 (en) | 2012-06-27 |
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