CN101275564A - Rotary compressor unit and method of controlling operation thereof - Google Patents
Rotary compressor unit and method of controlling operation thereof Download PDFInfo
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- CN101275564A CN101275564A CNA2008100830204A CN200810083020A CN101275564A CN 101275564 A CN101275564 A CN 101275564A CN A2008100830204 A CNA2008100830204 A CN A2008100830204A CN 200810083020 A CN200810083020 A CN 200810083020A CN 101275564 A CN101275564 A CN 101275564A
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- 238000000034 method Methods 0.000 title claims description 10
- 239000002699 waste material Substances 0.000 claims description 12
- 235000002020 sage Nutrition 0.000 abstract 1
- 230000006835 compression Effects 0.000 description 18
- 238000007906 compression Methods 0.000 description 18
- 238000010276 construction Methods 0.000 description 4
- 210000000078 claw Anatomy 0.000 description 3
- 239000000470 constituent Substances 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 235000019628 coolness Nutrition 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000006386 neutralization reaction Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000001360 synchronised 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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
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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
- F04C23/001—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 of similar working principle
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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
- F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
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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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/123—Rotary-piston pumps specially adapted for elastic fluids 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 radially or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth
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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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/05—Speed
- F04C2270/051—Controlled or regulated
-
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/05—Speed
- F04C2270/052—Speed angular
- F04C2270/0525—Controlled or regulated
-
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/18—Pressure
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Control Of Positive-Displacement Air Blowers (AREA)
Abstract
The compressor unit having at least two compressors, for example a low pressure stage compressor 11 and a high pressure stage compressor 12 connected in series, of which the low pressure sage compressor 11 and high pressure stage compressor 12 are driven by driving devices 13 and 14 respectively separately or driven by a single driving device 41 via variable speed gears 43 and 44 respectively connected to each of the compressors, and rotation speed of the low pressure stage compressor 11 and that of the high pressure stage compressor 12 are controlled independently in accordance with various operating conditions of the compressor unit so that optimal load balancing of the compressors 11 and 12 is always achieved.
Description
Technical field
The present invention relates to comprise the rotary compressor unit and the control method of operation thereof of the low pressure stage compressor and the high pressure section compressor of series connection, this unit is made the suitable load balance that can have each compressor and turns round, thereby realizes effective running of this unit.
Background technique
Usually, tooth-like rotary compressor comprises two rotors, male rotor and female rotor, and each rotor all has claw type tooth or blade.They rotate and do not contact each other along opposite direction when rotor rotation, are captured in the gas in the pressing chamber that forms between the internal surface of blade and compressor case with compression.Because rotor does not contact each other and the internal surface of compressor case, thereby rotor does not does not wear and tear and has the very long life-span.In addition,, do not need the lubricant oil of rotor, and can obtain the clean pressurized gas that does not have to pollute last lubricant oil because the non-contact of rotor cooperates.The obtainable compression ratio of such compressor is relatively low, thereby comprises that by formation the two stage compressor unit of the low pressure stage compressor of series connection and high pressure section compressor obtains the higher compression ratio of needs expeditiously in many cases.The work of tooth-like compressor will be described with reference to figure 4a to Fig. 4 d hereinafter.
In Fig. 4 a, the male rotor 02 with claw type blade cooperates in compressor case 01 with the female rotor 03 with claw type blade and has a gap closely.When rotor 02 and 03 when the direction shown in the arrow is rotated, will be inhaled into from suction opening 04 by compressed gas g.In Fig. 4 b, suction opening 04 is closed by rotor 02,03, and the gas g that sucks is limited in around the chamber of the blade of female rotor 03 and indoor around the blade of male rotor 02.In Fig. 4 c, these two chambers are connected, and the total measurement (volume) of two chambers reduces when rotor rotates with pressurized gas.In Fig. 4 d, pressurized gas c passes exit opening 05 and discharges, and exit opening 05 is arranged on the both sides of compressor case 01, and when rotor rotates by the side opening of female rotor 03.
Traditionally, use low pressure stage compressor and these two compressors of high pressure section compressor of single motoring two stage compressor unit as shown in Figure 5, be used to save the space and reduce factory cost.In Fig. 5, the actuation gear 08 that is connected to the output shaft 07a of motor 07 meshes with the gear 09a of the rotating shaft 06a of the male rotor 02a that is connected to the low pressure stage compressor and the gear 09b of the rotating shaft 06a of the male rotor 02b that is connected to the high pressure section compressor.
The male rotor 02a of low pressure stage compressor and the male rotor 02b of high pressure section compressor are driven together by single motor 07.The male rotor of each compressor and female rotor are synchronous via timing gear 010a and 020b respectively.
The rotary compressor that has by single electric motor driven two compressors shifts to an earlier date among the Japanese publication application No.4-6349 (patent documentation 2) in advance of publication application No.1-193089 (patent documentation 1) neutralization open in Japan.
Comprise in the rotary compressor unit of low pressure stage compressor and high pressure section compressor that in design the air displacement of each compressor is specified to and makes that the driving force of each compressor is almost equal when turning round under the specified discharge pressure of unit in the unit usually.The air displacement of each compressor can not change in the running of unit.The rotational speed of the rotational speed of low pressure stage compressor and high pressure section compressor is determined by the number of teeth ratio of the rotational speed of motor 07 and gear 09a and gear 08 and the number of teeth ratio of gear 09b and gear 08.Usually, these ratios are defined as equating, make two compressors all with identical rotational speed rotation.
The rotational speed of motor can be changed according to various operating condition controls by inverter (inverter).For example, shift to an earlier date to disclose a kind of driving scroll of using a plurality of motoring scroll compressors among the publication application No.2002-39079 (patent documentation 3) in Japan, wherein motor is controlled by inverter.Shift to an earlier date among the publication application No.2004-360464 (patent documentation 4) to disclose a kind of oil free screw compressor in Japan, its rotational speed is controlled by inverter.
As mentioned above, for as shown in Figure 5 have low pressure stage compressor and high pressure section compressor and by single electric motor driven compressor unit, the rotational speed of each compressor can not separately be controlled.The running of this compressor unit will be with reference to Fig. 6 explanation that P-V figure (P represents that pressure and V represent the specific volume (specific volume) of gas) is shown.In Fig. 6, gas at first by the low pressure stage compressor compresses to 0.2MPa, pressurized gas passes interstage cooler and is subjected to cooling to reduce specific volume, shown in arrow x then.The gas that compresses then and cool off for example further is compressed to 0.7MPa by the high pressure section compressor.
Yet compressor unit does not always turn round with the specified discharge pressure of generation unit.Specified discharge pressure is that the compressor unit of 0.7MPa can turn round to produce the discharge pressure of 0.5MPa, shown in x wire y, or the discharge pressure of instantaneous generation 0.8MPa, shown in x wire z among Fig. 6.By above-mentioned inverter control, the rotational speed of motor is controlled by inverter, and the rotational speed of the rotational speed of low pressure stage compressor and high pressure section compressor can not separately be controlled.
Be lower than with generation in compressor unit operational under the situation of discharge pressure of specified discharge pressure of unit, shown in x wire y, most compression work is finished by the low pressure stage compressor, and the high pressure section compressor has been finished the fraction compression work of compressor unit.Thereby, between low pressure stage compressor and high pressure section compressor, produced laod unbalance, and the rising of temperature becomes and rises greatly than temperature in the high pressure section compressor in the low pressure stage compressor, the compression efficiency of low pressure stage compressor reduces, cause the compression efficiency of compression unit to reduce, and on the serviceability of compressor unit, cause other ill-effect.
In order to realize the suitable load balance of low pressure stage compressor and high pressure section compressor, need reduce the rotational speed of low pressure stage compressor and increase the rotational speed of high pressure section compressor, yet this conventional ADS driving system for compressor unit is impossible.
Under the situation of compressor unit operational with the generation discharge pressure bigger than the specified discharge pressure of unit, shown in x wire z, with respect to the load of low pressure stage compressor, it is bigger relatively that the load of high pressure section compressor becomes, thereby cause the imbalance of load between these two compressors.Thereby the temperature in the temperature-rise ratio low pressure stage compressor in the high pressure section compressor rises bigger, causes the compression efficiency of high pressure section compressor to reduce.Thereby the compression efficiency of compressor unit reduces, and causes other ill-effect on the serviceability of compressor unit.In order to realize the load balance of low pressure stage and high pressure section compressor, the rotational speed that needs to increase the rotational speed of low pressure stage compressor and reduce the high pressure section compressor, however this conventional ADS driving system for compressor unit is impossible.
Summary of the invention
The present invention makes according to prior art problems, and the objective of the invention is to make the possible operation rotary compressor unit, this rotary compression element comprises the compressor of at least two series connection and separately drives, and, always can have compression efficiency with the irrelevant optimization of the discharge pressure of compressor unit by can independently controlling the rotational speed of each compressor.
In order to reach this purpose, the present invention proposes the method for running that a kind of control comprises the rotary compressor unit of the low pressure stage compressor of series connection and high pressure section compressor, wherein:
Described low pressure stage and high pressure section compressor are driven by drive unit, each drive unit drives a compressor, perhaps drive by single drive unit via the variable speed gear, each variable speed gear is connected to a compressor and is driven by described single drive unit, and
The rotational speed of each described compressor is controlled independently according to the various operating conditions of compressor unit, makes the load balance of compressor.
According to method of operation of the present invention, by being driven respectively by the drive unit that separates or driving every grade compressor by single drive unit respectively via the variable speed gear that separates, the rotational speed of each compressor can be controlled independently.Thereby, can realize the optimum load balance of compressor making each compressor of compressor unit under all operating conditions of compressor unit, under almost same load, turn round.Therefore, compressor unit can always have the running of optimum efficiency ground, and the serviceability of compressor unit can improve in addition.
For example, when discharge pressure is lower than the specified discharge pressure of unit, compressor unit is operated, with rotational speed that reduces the low pressure stage compressor and the rotational speed that increases the high pressure section compressor, thereby realize the optimum load balance of low pressure stage and high pressure section compressor, make each compression built-in temperature rise almost equal, and when discharge pressure is higher than the specified discharge pressure of unit, compressor unit is operated, with rotational speed that increases the low pressure stage compressor and the rotational speed that reduces the high pressure section compressor, thereby realize the optimum load balance of two compressors, make each compression built-in temperature rise almost equal.
Among the present invention preferably the waste side gas pressure of high pressure section compressor detected, or the waste side gas pressure of the waste side gas pressure of high pressure section compressor and low pressure stage compressor is all detected, and, control the rotational speed of each compressor independently based on detected force value or both force value.
In order to put into practice method of operation of the present invention, proposed a kind of low pressure stage compressor of series connection and rotary compressor unit of high pressure section compressor of comprising and invented as first of compressor unit, wherein:
Each described low pressure stage compressor and high pressure section compressor have the drive unit that is used for driving respectively each compressor, and each drive unit is provided with the inverter circuit of the frequency of the power supply that is used to change to described each drive unit, and
Controller is set, with according to the various operating conditions of compressor unit rotational speed, makes the load balance of described compressor via described each drive unit of described each inverter circuit control.
Compressor unit as first invention, its formation makes each compressor by motoring, motor is provided with inverter circuit and is connected respectively to each compressor, control to the frequency of each power of compressor via each inverter circuit by controller, the rotational speed of each compressor can be controlled independently.
The invention allows for the rotary compressor unit as second invention of compressor unit, it comprises the low pressure stage compressor and the high pressure section compressor of series connection, and comprises:
Be used to drive the single drive unit of described low pressure stage and high pressure section compressor,
The variable speed gear that is connected to described low pressure stage compressor and drives by described single drive unit,
The other variable speed gear that is connected to described high pressure section compressor and drives by described single drive unit and
Controller is used for controlling the rotational speed of each described compressor according to the operating condition of the variation of compressor unit independently via each described variable speed gear, makes the load balance of compressor.
The compressor unit of second invention is provided with only single motor, and controls by single electric motor driven each variable speed gear by controller, and the rotational speed of each compressor is controlled independently.
Compressor unit according to first and second inventions, the rotational speed that constitutes each compressor of compressor unit can be controlled, the feasible load balance of realizing compressor, thereby compressor unit running, the serviceability of compressor unit can improve in addition. with can always having optimal compression efficiency
In the compressor unit of first and second inventions, preferably be provided for detecting the pressure transducer of the waste side gas pressure of high pressure section compressor, or except the described pressure transducer of the waste side gas pressure that is provided for detecting the high pressure section compressor, be provided for detecting the pressure transducer of the waste side gas pressure of low pressure stage compressor, and based on the pressure that is detected by pressure transducer, the rotational speed of each compressor is controlled independently.
According to the present invention, the rotational speed of each compressor of comprise series connection and the low pressure stage compressor that separately drives and high pressure section compressor compressor unit can be controlled independently, can realize the optimum load balance of compressor for the various operating conditions of compressor unit, thereby compressor unit running, the serviceability of compressor unit can improve in addition. with can always having optimum efficiency according to the various operating conditions of compressor unit
The present invention may be used on also having one or more compressor units that are connected in series to the intermediate pressure section compressor of low pressure stage and high pressure section compressor, and can realize the load balance of compressor.
Description of drawings
Fig. 1 shows the schematic general construction of the first embodiment of the present invention.
Fig. 2 shows the schematic general construction of the second embodiment of the present invention.
Fig. 3 shows the schematic general construction of the third embodiment of the present invention.
Fig. 4 a to 4d shows the view of the work of explanation tooth type rotary compressor.
Fig. 5 shows the schematic structure of the driving mechanism of the traditional compressor unit with low pressure stage compressor and high pressure section compressor.
Fig. 6 shows the P-V figure of the traditional compressor unit with low pressure stage compressor and high pressure section compressor.
Embodiment
The preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.Yet desired is except explanation especially, and it only is illustrative that the size of the constituent elements among the embodiment, material, relative position etc. should be interpreted as, not as the restriction of scope of the present invention.
(first embodiment)
The first embodiment of the present invention will describe with reference to figure 1.Fig. 1 shows the schematic general construction of the rotary compressor unit with for example tooth-like low pressure stage compressor and high pressure section compressor.With reference to figure 1, rotary compressor unit comprises low pressure stage compressor (after this being called the LP compressor) 11, high pressure section compressor (after this being called the HP compressor) 12, be directly connected to the LP compressor driving motor (after this being called the LP motor) 13 of LP compressor 11 and be directly connected to the HP compressor driving motor (after this being called the HP motor) 14 of HP compressor 12.In addition, be provided with LP motor control inverter circuit (after this being called the LP inverter circuit) 15, it is used for the rotational speed by the frequency shift LP motor 13 of the power supply that changes to LP motor 13, and being provided with HP motor control inverter circuit (after this being called the HP inverter circuit) 16, it is used for the rotational speed by the frequency shift HP motor 14 of the power supply that changes to HP motor 14.
The gas g that will be inhaled into LP compressor 11 is compressed to for example 0.2MPa by LP compressor 11.Cool off by the intercooler 18 that is arranged in the discharge flow path 17 from the pressurized gas of LP compressor 11 dischargings, be drawn into HP compressor 12 then, further to be compressed to for example 0.7MPa.
Pass HP compressor 12 and from its pressurized gas that gives off by being arranged on aftercoolers 20 coolings in the discharge flow path 19, be fed to customer equipment then.Pressure transducer 21 is arranged on the downstream side of aftercooler 20, to survey the discharge pressure of HP compressor 12.In addition, be provided with controller 22, to control LP inverter circuit 15 and HP inverter circuit 16 based on the discharge pressure that detects by pressure transducer 21.
Exhausting air pressure by the pressure transducer 21 detected HP compressors 12 that are connected to discharge flow path 19 is input to controller 22.Controller 22 control LP inverter circuit 15 and HP inverter circuits 16, the feasible optimum load balance that realizes LP compressor 11 and HP compressor 12 by the rotational speed of controlling each compressor independently.
When the running compressor unit produces discharge pressure less than rated pressure, for example when the specified discharge pressure of running be that the compressor unit of 0.7MPa is when producing the discharge pressure of the 0.5MPa shown in x wire y among Fig. 6, controller 22 control makes the rotational speed of HP compressor 12 greater than the rotational speed of LP compressor 11, to realize the load balance of compressor 11 and 12, make the interior temperature that causes by compression of each compressor rise almost equal.
May exist compressor unit operational to produce the situation of the discharge pressure of the 0.8MPa shown in x wire z among Fig. 6.In the case, controller 22 control makes the rotational speed of LP compressor 11 greater than the rotational speed of HP compressor 12, to realize the load balance of compressor 11 and 12, makes the temperature that is caused by compression in each compressor rise almost equal.
The rotational speed by controlling LP compressor 11 in this way independently and the rotational speed of HP compressor 12, even when compressor unit operational produced the discharge pressure of the specified discharge pressure that is different from the unit, the load balance of LP compressor 11 and HP compressor 12 always can be realized.Thereby the running of compressor unit always has the irrelevant compression efficiency of discharge pressure of requirement best and compressor unit, thereby can always realize effective running of compressor unit, in addition, can improve the serviceability of compressor unit.
When the discharge pressure of HP compressor 12 is detected by pressure transducer 21, and when the rotational speed of LP and HP compressor 11,12 was controlled independently via LP and HP inverter circuit 15,16, the load balance of LP compressor 11 and HP compressor 12 can have pinpoint accuracy ground according to the various discharge pressures of HP compressor 12 to be realized.
(second embodiment)
Next, the second embodiment of the present invention will describe with reference to figure 2.In Fig. 2, the usefulness same reference number identical with the constituent element of Fig. 1 marks, and omits its explanation.Second embodiment among Fig. 2 and the difference of first embodiment among Fig. 1 are: be provided with intermediate pressure sensor 31 in discharge flow path 17, to detect the discharge pressure of LP compressor 11.Other first embodiment with among Fig. 1 is identical.Except the force value that detects by pressure transducer 21, be input to controller 22 by intermediate pressure sensor 31 detected force value, and via LP and HP inverter circuit 15,16, the rotational speed of LP and HP compressor 11,12 is controlled based on two force value that detect.
This structure for second embodiment, not only in discharge flow path 19, detect the discharge pressure of HP compressor 12, and in discharge flow path 17, detect the discharge pressure of LP compressor 11, based on two discharge pressures of LP compressor and HP compressor, can realize the optimum load balance of LP compressor 11 and HP compressor 12.Thereby more effective running of compressor unit can realize.
(the 3rd embodiment)
Next, the third embodiment of the present invention will describe with reference to figure 3.In Fig. 3, the usefulness same reference number identical with the constituent element of Fig. 2 marks, and omits its explanation.The 3rd embodiment among Fig. 3 is with the different of second embodiment among Fig. 2: adopt single motor 41 with compressor unit, variable speed gear (after this being called the LP speed changer) 43 is set is used to change the rotational speed of LP compressor 11, variable speed gear (after this being called the HP speed changer) 44 is set is used to change the rotational speed of HP compressor 12, and gear-box 42 is connected to motor 41, thereby via LP speed changer 43 and HP speed changer 44, LP compressor 11 and HP compressor 12 are activated respectively.Other second embodiment with among Fig. 2 is identical.
For the 3rd embodiment's compressor unit, the rotation of motor 41 is via gear-box 42 and be transferred to LP and HP compressor 11,12 via LP and HP speed changer 43,44 respectively.LP speed changer 43 and HP speed changer 44 are by controller 22 controls.Thereby the rotational speed of LP compressor 11 and HP compressor 12 can be controlled independently.
Because the rotational speed of LP compressor and the rotational speed of HP compressor can be controlled independently, compressor unit can be controlled, make that the optimum load balance of LP compressor 11 and HP compressor 12 always can realize when compressor unit operational produces the discharge pressure of the specified discharge pressure that is different from the unit.Thereby compressor unit is running effectively always, and the serviceability of compressor unit can improve in addition.
By survey the discharge pressure of HP compressor 12 and LP compressor 11 by pressure detector 21 and intermediate pressure sensor 31, and, can have the accuracy ground maintenance of height according to the optimum load balance of various discharge pressure LP compressors 11 and HP compressor 12 based on the pressure control HP compressor of surveying 12 and the rotational speed of LP compressor 11.In addition, when compressor unit is driven by single motor 41, the expense that can save the installing space device.
Although the example of compressor unit comprises two compressors, the i.e. low pressure stage and the high pressure section compressor of the series connection of describing hereinbefore, can understand easily when the one or more intermediate pressure section compressors that separately drive are connected with low pressure stage and high pressure section compressor, can obtain similar effects.
Industrial applicibility
According to the present invention, comprise controlled the making so that each pressure of compressor unit of a plurality of compressors of series connection The rotary speed of contracting machine can change independently, obtains the optimum load balance of compressor, thereby can be effectively Carry out the running of compressor unit.
Claims (7)
1. a control comprises the method for running of the rotary compressor unit of the low pressure stage compressor of series connection and high pressure section compressor, wherein:
Described low pressure stage compressor and high pressure section compressor are driven by drive unit, each described drive unit drives a described compressor, perhaps drive by single drive unit via the variable speed gear, each described variable speed gear is connected to a described compressor and is driven by described single drive unit, and
The rotational speed of each described compressor is controlled independently according to the various operating conditions of described compressor unit, makes the load balance of described compressor.
2. the method for the running of control rotary compressor unit as claimed in claim 1, the waste side gas pressure of wherein said high pressure section compressor is detected, or the waste side gas pressure of the waste side gas pressure of described high pressure section compressor and described low pressure stage compressor is all detected, and, control the rotational speed of each described compressor independently based on detected one or more force value.
3. one kind comprises the low pressure stage compressor of series connection and the rotary compressor unit of high pressure section compressor, wherein:
Each described low pressure stage compressor and high pressure section compressor have the drive unit that is used for driving respectively each described compressor, and each described drive unit is provided with the inverter circuit of the frequency of the power supply that is used to change to described each drive unit, and
Controller is set, with according to the various operating conditions of described compressor unit, via the rotational speed of described each drive unit of described each inverter circuit control, makes the load balance of described compressor.
4. one kind comprises the low pressure stage compressor of series connection and the rotary compressor unit of high pressure section compressor, comprising:
Single drive unit, it is used to drive described low pressure stage compressor and high pressure section compressor;
The variable speed gear, it is connected to described low pressure stage compressor and is driven by described single drive unit;
Other variable speed gear, it is connected to described high pressure section compressor and is driven by described single drive unit; With
Controller, be used for according to described compressor unit various operating conditions, control the rotational speed of each described compressor independently via each described variable speed gear, make the load balance of described compressor.
5. as claim 3 or 4 described rotary compressor units, wherein be provided for detecting the pressure transducer of the waste side gas pressure of described high pressure section compressor, or except the described pressure transducer of the waste side gas pressure that is provided for detecting described high pressure section compressor, be provided for detecting the pressure transducer of the waste side gas pressure of described low pressure stage compressor, and based on the pressure that is detected by described one or more pressure transducer, the rotational speed of each described compressor is controlled independently.
6. the method for the running of control rotary compressor unit as claimed in claim 1 or 2, also comprise the intermediate pressure section compressor that one or more and described low pressure stage compressor and high pressure section compressor are connected, described one or more intermediate pressure section compressor is activated by the drive unit that separates or a plurality of drive unit or by described single drive unit dividually via the variable speed gear that separates or a plurality of gear, and rotational velocity is controlled independently, the feasible load balance of realizing all compressors.
7. as each described rotary compressor unit in the claim 3 to 5, also comprise the intermediate pressure section compressor that one or more and described low pressure stage compressor and high pressure section compressor are connected, described one or more intermediate pressure section compressor is activated by the drive unit that separates or a plurality of drive unit or by described single drive unit dividually via the variable speed gear that separates or a plurality of gear, and rotational velocity is controlled independently, the feasible load balance of realizing all compressors.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007095584A JP5071967B2 (en) | 2007-03-30 | 2007-03-30 | Rotary compressor and operation control method thereof |
| JP095584/07 | 2007-03-30 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101275564A true CN101275564A (en) | 2008-10-01 |
Family
ID=39629130
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2008100830204A Pending CN101275564A (en) | 2007-03-30 | 2008-03-18 | Rotary compressor unit and method of controlling operation thereof |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20080240953A1 (en) |
| EP (1) | EP1975415A3 (en) |
| JP (1) | JP5071967B2 (en) |
| CN (1) | CN101275564A (en) |
Cited By (5)
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| CN102330687A (en) * | 2011-05-25 | 2012-01-25 | 宁波奥克斯电气有限公司 | Method for controlling compressor load during normal operation of screw type compression multi-split air conditioner |
| CN107202011A (en) * | 2016-03-16 | 2017-09-26 | 株式会社日立产机系统 | Compound compressor |
| CN107605732A (en) * | 2017-09-04 | 2018-01-19 | 深圳市英威腾电气股份有限公司 | A kind of control method of double-stage compressor, control device and control system |
| CN108691768A (en) * | 2017-04-10 | 2018-10-23 | 加德纳·丹佛德国股份有限公司 | Method for controlling rotary screw compressor |
| CN112610522A (en) * | 2020-12-31 | 2021-04-06 | 浙江中控技术股份有限公司 | Control method of series compressor unit and related equipment |
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| KR101381085B1 (en) * | 2007-11-13 | 2014-04-10 | 엘지전자 주식회사 | 2 stage rotary compressor |
| BE1018096A3 (en) * | 2008-04-14 | 2010-05-04 | Atlas Copco Airpower Nv | Multi-stage compressor controlling method for compressed air system e.g. absorption dryer, involves controlling exhaust temperature of one compressor element or intermediate pressure between two linked compressor elements |
| JP4818410B2 (en) * | 2009-08-11 | 2011-11-16 | オリオン機械株式会社 | Claw pump exhaust structure and exhaust method |
| US8011191B2 (en) | 2009-09-30 | 2011-09-06 | Thermo Fisher Scientific (Asheville) Llc | Refrigeration system having a variable speed compressor |
| JP5584862B2 (en) * | 2010-03-19 | 2014-09-10 | オリオン機械株式会社 | Biaxial rotary pump and manufacturing method thereof |
| US9618242B2 (en) * | 2013-01-16 | 2017-04-11 | GM Global Technology Operations LLC | Method for controlling a thermal storage heat pump system |
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| JP2555464B2 (en) * | 1990-04-24 | 1996-11-20 | 株式会社東芝 | Refrigeration cycle equipment |
| DE9306559U1 (en) * | 1992-06-10 | 1993-07-01 | Siemens AG, 8000 München | Arrangement consisting of at least two liquid ring machines connected in series |
| JP3352187B2 (en) * | 1993-12-03 | 2002-12-03 | 株式会社神戸製鋼所 | Two-stage oil-free screw compressor |
| JP3767052B2 (en) * | 1996-11-30 | 2006-04-19 | アイシン精機株式会社 | Multistage vacuum pump |
| BE1012944A3 (en) * | 1999-10-26 | 2001-06-05 | Atlas Copco Airpower Nv | MULTISTAGE COMPRESSOR UNIT AND METHOD FOR CONTROLLING ONE OF EQUAL MORE stage compressor unit. |
| JP4071423B2 (en) | 2000-07-24 | 2008-04-02 | アネスト岩田株式会社 | Scroll fluid machine and its assembly method |
| GB2367332B (en) * | 2000-09-25 | 2003-12-03 | Compair Uk Ltd | Improvements in multi-stage screw compressor drive arrangements |
| JP3751208B2 (en) * | 2001-02-23 | 2006-03-01 | 株式会社神戸製鋼所 | Control method of multistage variable speed compressor |
| JP2002327690A (en) * | 2001-04-27 | 2002-11-15 | Daikin Ind Ltd | Two-stage compressor |
| JP2004360464A (en) | 2003-06-02 | 2004-12-24 | Hitachi Industrial Equipment Systems Co Ltd | Variable speed control type oil-less screw compression device |
| US7028491B2 (en) * | 2004-03-29 | 2006-04-18 | Tecumseh Products Company | Method and apparatus for reducing inrush current in a multi-stage compressor |
| CN101163887B (en) * | 2005-02-26 | 2013-05-22 | 英格索尔-兰德公司 | System and method for controlling a variable speed compressor during stopping |
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2007
- 2007-03-30 JP JP2007095584A patent/JP5071967B2/en active Active
-
2008
- 2008-02-18 EP EP08002967A patent/EP1975415A3/en not_active Withdrawn
- 2008-03-18 CN CNA2008100830204A patent/CN101275564A/en active Pending
- 2008-03-31 US US12/058,902 patent/US20080240953A1/en not_active Abandoned
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102330687A (en) * | 2011-05-25 | 2012-01-25 | 宁波奥克斯电气有限公司 | Method for controlling compressor load during normal operation of screw type compression multi-split air conditioner |
| CN102330687B (en) * | 2011-05-25 | 2014-06-04 | 宁波奥克斯电气有限公司 | Method for controlling compressor load during normal operation of screw type compression multi-split air conditioner |
| CN107202011A (en) * | 2016-03-16 | 2017-09-26 | 株式会社日立产机系统 | Compound compressor |
| CN108691768A (en) * | 2017-04-10 | 2018-10-23 | 加德纳·丹佛德国股份有限公司 | Method for controlling rotary screw compressor |
| CN107605732A (en) * | 2017-09-04 | 2018-01-19 | 深圳市英威腾电气股份有限公司 | A kind of control method of double-stage compressor, control device and control system |
| CN112610522A (en) * | 2020-12-31 | 2021-04-06 | 浙江中控技术股份有限公司 | Control method of series compressor unit and related equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1975415A3 (en) | 2012-05-23 |
| JP5071967B2 (en) | 2012-11-14 |
| EP1975415A2 (en) | 2008-10-01 |
| JP2008255799A (en) | 2008-10-23 |
| US20080240953A1 (en) | 2008-10-02 |
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Application publication date: 20081001 |