CN109469602A - The control method of compressed gas feedway and compressed gas feedway - Google Patents
The control method of compressed gas feedway and compressed gas feedway Download PDFInfo
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- CN109469602A CN109469602A CN201710804518.4A CN201710804518A CN109469602A CN 109469602 A CN109469602 A CN 109469602A CN 201710804518 A CN201710804518 A CN 201710804518A CN 109469602 A CN109469602 A CN 109469602A
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- compressor
- load factor
- compressed gas
- specific rotation
- gas feedway
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/06—Combinations of two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
- F04B49/065—Control using electricity and making use of computers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2203/00—Motor parameters
- F04B2203/02—Motor parameters of rotating electric motors
- F04B2203/0209—Rotational speed
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Computer Hardware Design (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The present invention provides the control method of a kind of compressed gas feedway and compressed gas feedway, has good followability relative to load change, and can cut down energy consumption.This application involves the compressed gas feedways that one kind can supply the compressed gas being discharged from multiple compressors.The device includes multiple compressors of parallel configuration；Detect the load factor test section of the load factor of compressed gas feedway；The control unit of the specific rotation of compressor is controlled based on load factor.Control unit is configured to, in co- controlling region, it is controlled in a manner of making multiple compressors that there is common specific rotation, in separate control area, it is independently controlled in a manner of making specific rotation of the specific rotation of at least one compressor less than other compressors, in independent control area, stops at least one compressor and control the specific rotation of other compressors.
Description
Technical field
The present invention relates to one kind can supply from multiple compressors be discharged compressed gas compressed gas feedway and
The control method of compressed gas feedway.
Background technique
The known compressed gas feedway with multiple compressors for generating compressed gas.It is supplied in this compressed gas
In device, for example, the multiple compressors of parallel configuration and relative to party in request, compressed air needed for demand and supply side.Separately
Outside, this compressed gas feedway has in the case where specific compressor breaks down can utilize others
Standby of the compressor to party in request's sustainable supply compressed gas.In such compressed gas feedway, by suitably controlling
The working condition of each compressor is made, to realize energy conservation.
Such as following content is described in patent document 1: in the multiple pressures that can carry out revolving speed control using converter
In compressed gas feedway made of contracting machine parallel configuration, by the way that the compressor of variable control revolving speed is limited to only one,
Energy conservation is realized to make power consumption minimize.In the publication, it is carried out in any one compressor in multiple compressors
The variable control of revolving speed, if along with load reduce and revolving speed reaches lower limit rotating speed, make the compressor stop, next according to
The secondary revolving speed that other compressors are changeably controlled.
In addition, describing following content in patent document 2: in the multiple pressures that can carry out revolving speed control using converter
In compressed gas feedway made of contracting machine parallel configuration, by all multiple compressors in operating condition by revolving speed
Be changeably controlled for equality always, to reduce useless consumption electric power.
Citation
Patent document 1: Japanese Unexamined Patent Publication 11-343986 bulletin
Patent document 2: Japanese Unexamined Patent Publication 2002-122078 bulletin
Summary of the invention
The compressor used in compressed gas feedway declines along with revolving speed and efficiency is reduced with conic section.This
It is because revolving speed is lower, gas compressed is more revealed in discharge chambe, more easily causes recompression.In common compressor,
The lower limit value of practical revolving speed is about 30% or so of rated speed.
In above patent document 1, only it is changeably controlled in multiple compressors that compressed gas feedway is included
One revolving speed, other compressors carry out specified operating without exception.In such control, in the compression that revolving speed is changeably controlled
In machine, change, the operating in low rotary area because of a wide range of between rated speed and lower limit rotating speed of revolving speed
Become more, is difficult to obtain good efficiency.
In addition, being equality always by the revolving speed control of multiple compressors in operating in above patent document 2.If
Along with load change, the revolving speed of these compressors reaches lower limit rotating speed, then specific compressor stops.At this point, in others
In compressor, revolving speed, which has to increase, stops a considerable amount with specific compressor.For example, if relative to rated speed with
One of two compressors that 50% revolving speed is operating stop, then the revolving speed of another compressor have to suddenly from
50% increases to 100%.But in actual compressed gas feedway, because not catching up with variation violent in this way,
There is a phenomenon where cause the discharge rate of compressed gas temporarily insufficient.
At least one embodiment of the invention is made in view of the foregoing, it is intended that providing a kind of pressure
The control method of contracting machine gas supply device and compressed gas feedway has good follow relative to load change
Property, and energy consumption can be reduced.
(1) in order to solve the above problems, the compressed gas feedway of at least one embodiment of the invention can be for
To the compressed gas being discharged from multiple compressors, comprising: multiple compressors of parallel configuration；The compressed gas is detected to supply
To the load factor test section of the load factor of device；It is controlled respectively based on the load factor detected by the load factor test section
Make the control unit of the specific rotation of multiple compressors.The control unit (i) is being total to for first threshold or more in the load factor
With in control area, controlled in a manner of making multiple compressors that there is common specific rotation, (ii) is in the load
Rate is in the separate control area until from the first threshold to the second threshold for being less than the first threshold, so that multiple institutes
The mode for the specific rotation that the specific rotation for stating at least one compressor in compressor is less than other compressors is independently controlled
System, (iii) stop at least one described compressor in the independent control area that the load factor is less than the second threshold
And control the specific rotation of other compressors.
According to the structure of above-mentioned (1), corresponding with load factor three kinds of control areas (co- controlling region, independent control are distinguished
Region processed and independent control area) and control the revolving speed for constituting each compressor of compressed gas feedway.(i) in co- controlling
In region, in the case where load factor is first threshold or more, the revolving speed of multiple compressors in operating is coequally controlled.Cause
This, the revolving speed of each compressor is not involved in the low rotation speed area of efficiency deterioration, and obtains good running efficiency.(ii) only
In vertical control area, so that the revolving speed of at least one compressor stopped when being transferred to back to back independent control area is less than
The mode of the revolving speed of other compressors is independently controlled.As a result, in the reduction along with load factor and from independent control
When zone-transfer is to independent control area, variation when other compression revolving speeds can will be made to increase inhibit to obtain very little, inhibit
It is equivalent to the amount of at least one compressor stopping.As a result, can be improved and hold when reducing the number of units of the compressor in operating
The followability of the revolving speed for the compressor that reforwarding turns, and the temporary insufficient phenomenon of discharge rate that compressed gas can be alleviated.
(2) in several embodiments, on the basis of the structure of above-mentioned (1), the control unit is so that the independent control
The specific rotation of at least one compressor in region processed is greater than the co- controlling relative to the change degree of the load factor
The mode of the change degree in region is controlled.
Stopped at least when for being transferred to independent control area in separate control area according to the structure of above-mentioned (2)
For one compressor, increase the change degree relative to load factor.As a result, from separate control area to independent control area
When transfer, reduce the revolving speed of the compressor of stopping, capable of further suppressing and be generated when stopping the compressor in other compressors
Revolving speed variation.As a result, continuous running can be further increased when reducing the number of units of the compressor in operating
The followability of the revolving speed of compressor.
(3) in several embodiments, on the basis of the structure of above-mentioned (1) or (2), the control unit is in the load
In the case that rate is in reduction trend, in the separate control area, the specific rotation of at least one compressor is maintained
It is constant.
According to the structure of above-mentioned (3), in separate control area, the pressure of continuous running when transferring to independent control area
The revolving speed of contracting machine is maintained constant.According to the verifying of the present application person, discovery is supplied by carrying out such control, compressed gas
Good efficiency is integrally obtained to device.
(4) in several embodiments, on the basis of above-mentioned (1) any structure into (3), the control unit is because of institute
It states load factor to reduce in the case where being transferred to the independent control area from the separate control area, be existed with the load factor
It is condition that the independent control area, which is kept for the stipulated time, stops at least one described compressor.
According to the structure of above-mentioned (4), independent control area is being transferred to from separate control area due to load factor reduces
In the case of, in the case where load factor is kept for the stipulated time in independent control area, implement the stopping control of at least one compressor
System.Thereby, it is possible to avoid continually weighing because load factor is continually travelled to and fro between separate control area and independent control area
The case where stopping and starting of compound compression machine.
(5) in several embodiments, on the basis of above-mentioned (1) any structure into (4), the control unit is adjoint
The reduction of the load factor and in the case where stopping at least one described compressor, by the rotation of other compressors
Rate control is maximum specific rotation.
According to the structure of above-mentioned (5), stopping at least one and being transferred to independent control area from separate control area
When a compressor, by being maximum specific rotation by the specific rotation control of the compressor of other continuous runnings, effect can be transferred to
The best state of rate.
(6) in several embodiments, on the basis of above-mentioned (1) any structure into (5), the control unit is described
In the case that load factor is in increase tendency, in the separate control area, at least one described pressure is made according to the load factor
The specific rotation of contracting machine increases, and reduces the specific rotation of other compressors according to the load factor.
According to the structure of above-mentioned (6), due to load factor increases from independent control area be transferred to separate control area from
And in the case where increasing the number of units of compressor, so that the compressor in halted state is started with lower limit specific rotation, and adjoint
The increase of load factor and increased mode is controlled.At this point, the specific rotation of other compressors is controlled as, with starting
The specific rotation increase of compressor comparatively reduces.
(7) in several embodiments, on the basis of above-mentioned (1) any structure into (6), the control unit is because of institute
It states load factor to increase in the case where being transferred to the separate control area from the independent control area, be existed with the load factor
It is condition that the separate control area, which is kept for the stipulated time, makes at least one described compressor start.
According to the structure of above-mentioned (7), separate control area is being transferred to from independent control area due to load factor increases
In the case of, in the case where load factor is kept for the stipulated time in separate control area, so that the side of at least one compressor start
Formula is implemented.Thereby, it is possible to avoid due to load factor is continually to and between separate control area and independent control area
The case where frequently repeating the stopping and starting of compressor.
(8) in addition, in order to solve the above problems, supplying dress for the compressed gas of at least one embodiment of the invention
For the control method set, compressed gas feedway can supply the compressed gas being discharged from multiple compressors of parallel configuration
Body, the control method of the compressed gas feedway include the load for detecting the load factor of the compressed gas feedway
Rate detects process；The control process for the revolving speed for controlling multiple compressors respectively based on the load factor detected.?
In the control process, (i) in the co- controlling region that the load factor is first threshold or more, so that multiple compressions
There is machine the mode of common specific rotation to be controlled, and (ii) is from the first threshold to less than described the in the load factor
In separate control area until the second threshold of one threshold value, so that the rotation of at least one compressor in multiple compressors
The mode that rate of rotation is less than the specific rotation of other compressors is independently controlled, and (iii) is less than described the in the load factor
In the independent control area of two threshold values, stops at least one described compressor and control the rotation of other compressors
Rate.
The method of above-mentioned (8) can be properly real by above-mentioned compressed gas feedway (including above-mentioned various modes)
It applies.
Invention effect
At least one embodiment according to the present invention, is capable of providing a kind of compressed gas feedway and compressed gas supplies
To the control method of device, there is good followability relative to load change, and energy consumption can be cut down.
Detailed description of the invention
Fig. 1 is the integrally-built mode for indicating the compressed gas feedway of at least one embodiment of the invention
Figure.
Fig. 2 is the control method that the compressed gas feedway implemented in the control device of Fig. 1 is indicated according to process
Flow chart.
Fig. 3 be indicate load factor reduce when compressor specific rotation relative to compressed gas feedway load factor control
The chart of example processed.
Fig. 4 is the measurement knot of the relationship between the specific rotation and efficiency indicated corresponding to the compressed gas feedway of Fig. 3
The chart of fruit.
Fig. 5 corresponds to the detail of each compressor of the specific rotation in the compressed gas feedway of Fig. 3.
Fig. 6 is the detail of each compressor of the specific rotation in the second comparative example.
Fig. 7 be indicate load factor increase when compressor specific rotation relative to compressed gas feedway load factor control
The chart of example processed.
Fig. 8 is the integrally-built ideograph for indicating the compressed gas feedway with three compressors.
Fig. 9 be indicate corresponding to Fig. 8 compressed gas feedway efficiency relative to specific rotation measurement result figure
Table.
Figure 10 corresponds to the detail of each compressor of the specific rotation in the compressed gas feedway of Fig. 8.
Figure 11 is the detail of each compressor of the specific rotation in the 6th comparative example.
Description of symbols:
1 compressed gas feedway；
2A, 2B compressor；
4A, 4B discharge pipe；
6 main discharges；
8 storage boxes；
10 parties in request
12 feed paths；
14 adjustment valves；
15 pressure sensors；
16A, 16B electric motor
18A, 18B converting means；
20A, 20B pressure sensor；
100 control devices；
102 load factor test sections；
104 control units.
Specific embodiment
Hereinafter, being illustrated referring to attached drawing to several embodiments of the invention.Wherein, as documented by embodiment
Inside the size, material, shape of structure member perhaps shown in the drawings, its relative configuration etc. are not to be defined in the scope of the present invention
This purport is only to illustrate example.
For example, the tables such as " in some directions ", " along certain direction ", " parallel ", " vertical ", "center", " concentric " or " coaxial "
Show that opposite or absolute configuration performance not only strictly indicates such configuration, be also represented by with tolerance or obtain identical function
Degree angle and/or distance and the state of relative displacement.
For example, " identical ", " equal " and " equalization " etc. indicates that the performance of the equal state of things not only strictly indicates phase
Deng state, be also represented by there are tolerance or obtain identical function degree difference state.
For example, indicating that the performance of the shapes such as quadrilateral shape and/or cylindrical shape not only indicates geometrically stricti jurise
The shapes such as quadrilateral shape and/or cylindrical shape are also manifested by the range of obtaining same effect comprising bump and/or corner portion
Deng shape.
On the other hand, " outfit ", " having ", " having ", "comprising" or " having " structural element are such shows not
It is the existing exclusive sex expression for excluding other structures element.
Fig. 1 is the integrally-built mode for indicating the compressed gas feedway 1 of at least one embodiment of the invention
Figure.Compressed gas feedway 1 has multiple compressors in shell (illustration omitted).In Fig. 1, illustrate with multiple pressures
The compressed gas feedway 1 of contracting machine 2A, 2B.In the present embodiment, multiple compressor 2A, 2B are to utilize to lead from outside respectively
The screw type air compressor that the gas entered generates compressed gas (in the case where being referred to as this two compressor, is properly termed as
" compressor 2 ").But in the present invention, each compressor is not limited to screw type air compressor, is also possible to such as Scrawl
Air compressor.
Compressor 2A, 2B are respectively provided with discharge pipe 4A, the 4B for excluding compressed gas generated.Discharge pipe 4A, 4B are under
Trip side interflow is connect in main discharge 6, and with the storage box 8 for storing compressed gas.In this way, multiple compressor 2A, 2B phases
It is connected in parallel with each other for storage box 8, the compressed gas being discharged from compressor 2A, 2B is stored in storage via main discharge 6
Case 8.It should be noted that in the present invention, storage box 8 may be embodied in shell, also can be only fitted to outside shell.
It is provided in storage box 8 for the feed path 12 to 10 supplying compressed gas of party in request.It is set in feed path 12
It is equipped with the adjustment valve 14 that can control aperture.Compressed gas feedway 1 is adjusted and energy by the aperture to adjustment valve 14
It is enough to supply defined compressed gas to party in request 10.In addition, being provided in storage box 8 for detecting the pressure in storage box 8
Pressure sensor 15.It should be noted that in the present invention, adjustment valve 14 may include in shell, shell also can be only fitted to
In vitro.In addition, in the present invention, storage box 8 may be embodied in shell, also it can be only fitted to outside shell, therefore, for setting
For the pressure sensor 15 of storage box 8 similarly, it may be embodied in shell, also can be only fitted to outside shell.
Compressor 2A, 2B be respectively provided with electric motor 16A, 16B as power source, can control electric motor 16A,
Converting means 18A, 18B of the revolving speed of 16B.Converting means 18A, 18B can infinitely control turning for electric motor 16A, 16B
Speed adjusts the output of compressor 2A, 2B via the revolving speed control of electric motor 16A, 16B.It is configured to as a result, each other solely
On the spot adjust the revolving speed of compressor 2A, 2B.
It should be noted that in the present embodiment, showing the case where compressor 2A, 2B specification having the same
Example, but the present invention can also be suitable for compressor 2A, 2B and have the case where specification different from each other.In the following description, in order to
Be suitably used independent of the common explanation of the specification of compressor 2A, 2B instead of the specific rotation of compressor 2A, 2B
It is defined as specific rotation (that is, rated speed be equivalent to specific rotation 100%) of the specific rotation relative to the ratio of rated speed.
In addition, in the present embodiment, for compressor 2A, 2B with same size, illustrating and revolving the upper limit
The case where rate of rotation is defined as 100% and lower limit specific rotation is defined as 30%.Lower limit specific rotation can be defined as compressor
2A, 2B mechanically movable lower limit value, the efficiency that can also be defined as compressor 2A, 2B are lower than the lower limit value of a reference value.
Compressor 2A, 2B are provided with pressure sensor 20A, 20B for detecting respective discharge pressure.It will be by pressure
The pressure that sensor 20A, 20B are detected is sent to for example aftermentioned control device 100, and is pre-stored within control device 100
The setting pressure as target compare.The pressure detected be less than setting pressure in the case where, converting means 18A, 18B with
The mode for increasing the load factor of electric motor 16A, 16B controls electric motor 16A, 16B.It is setting pressure in the pressure detected
In the case where more than power, converting means 18A, 18B control electronic horse in a manner of reducing the load factor of electric motor 16A, 16B
Up to 16A, 16B.
In addition, compressed gas feedway 1 has control device 100.Control device 100 is compressed gas feedway 1
Controller, such as be configured to by the way that regulated procedure to be installed on electronic computer as computer in advance, so as to
It is enough to play defined function.For example, control device 100 adjusts turning for compressor 2A, 2B by control converting means 18A, 18B
Speed.In addition, control device 100 is adjusted by the aperture to adjustment valve 14, the pressure of storage box 8 is controlled always as demand
Pressure required by side 10.
In Fig. 1, typically illustrate it is in the internal structure of such control device 100, in aftermentioned control
Hold associated functional block.Control device 100 includes load factor test section 102, detects the load of compressed gas feedway 1
Rate L；Control unit 104 controls multiple compressor 2A, 2B based on the load factor L detected by load factor test section 102 respectively
Revolving speed.
Then, the control method of the compressed gas feedway 1 carried out to control device 100 is specifically described.Fig. 2
It is the flow chart that the control method for the compressed gas feedway 1 implemented in the control device 100 of Fig. 1 is indicated according to process.
Firstly, load factor test section 102 obtains respectively is respectively arranged at two pressures that compressed gas feedway 1 has
The detected value (step S1) of pressure sensor 20A, 20B of contracting machine 2A, 2B.Then, load factor test section 102 is based on passing from pressure
The pressure that sensor 20A, 20B are obtained calculates the load factor L (step S2) of compressed gas feedway 1.
Here, load factor is defined as, load relative to nominal load (operate electric motor with rated speed, and
Obtain specification pressure when load) ratio.In step s 2, such as by being based on being detected by pressure sensor 20A, 20B
The respective pressure of compressor 2A, 2B measured value load divided by prespecified compressor 2A, 2B nominal load, thus
Calculate the respective load factor of compressor 2A, 2B.Then, load factor test section 102 is each by compressor 2A, the 2B that will be calculated in this way
From load factor be added, calculate compressed gas feedway 1 load factor L (for example, being respectively 100% in compressor 2A, 2B
In the case where load factor, 200%) load factor of compressed gas feedway 1 is.
Then, load factor of the control unit 104 based on the compressed gas feedway 1 detected by load factor test section 102
L controls the revolving speed (step S3) of multiple compressor 2A, 2B respectively.Compressor 2A, 2B's that such control unit 104 is carried out
Control is carried out by controlling corresponding converting means 18A, 18B.
Here, the control content in the step S3 of Fig. 2 is described in detail.Firstly, with compressed gas feedway 1
Load factor L is from nominal load Lmax(200%) it is illustrated in case where diminishingly changing.Fig. 3 is to indicate load factor L
Chart of the specific rotation of compressor 2A, 2B relative to the control example of the load factor L of compressed gas feedway 1 when reduction.
It provides by load factor L in nominal load Lmax(200%) into the co- controlling region R1 of first threshold L1, with
The mode for making multiple compressor 2A, 2B have common specific rotation is controlled.That is, reduce along with load factor L, with
The mode for reducing the specific rotation of compressor 2A, 2B in the state of maintaining and being equal to each other carries out variable control.That is, controlling jointly
In region R1 processed, it is substantially equivalent to carry out the case where controlling the specific rotation of two compressors 2A, 2B with the common converting means of utilization
Control.
In the separate control area R2 that load factor is defined as to first threshold L1 to second threshold L2 (100%), so that
The specific rotation of at least one compressor in multiple compressor 2A, 2B is less than the mode of the specific rotation of another compressor independently
It is controlled.In the present embodiment, it is controlled in a manner of making specific rotation of the specific rotation of compressor 2B less than compressor 2A
System.Compressor 2A, 2B are independently controlled using converting means 18A, 18B, to realize such control.
In the R2 of separate control area, so that specific rotation is greater than co- controlling region R1's relative to the change degree of load factor
The mode of change degree controls compressor 2B.As shown in figure 3, the specific rotation passage of the compressor 2B in the R2 of separate control area is opposite
The specific rotation passage of compressor 2B in the rake ratio co- controlling region R1 of load factor L is steep relative to the inclination of load factor L.
On the other hand, in the R2 of separate control area, specific rotation is maintained constant mode and controls compressor 2A.?
In Fig. 3, the specific rotation at first threshold L1 is maintained steady state value A1 across separate control area R2.
In independent control area R3 of the load factor L less than second threshold L2, stop compressor 2B, is only compressed with one
Machine 2A carries out individual operation.Herein, it is specified that the second threshold on the boundary between separate control area R2 and independent control area R3
L2 be in the state that compressor 2A is maintained constant specific rotation A1, compressor 2B reach preset lower limit specific rotation
The load factor of (for example, 30%).In other words, second threshold L2 is defined as the load for stopping compressor 2B when being less than the value
Rate.Therefore, it is operated in separate control area R2 using two compressor 2A, 2B, but in independent control area R3, is passed through
Stop compressor 2B to reduce operating number.
In this, it is assumed that if it is considered that without separate control area R2 comparative example (that is, load factor L be nominal load rate
LmaxTo second threshold L2, identically as above-mentioned co- controlling region R1, so that compressor 2A, 2B have common specific rotation
The case where mode is controlled), at second threshold L2, stop by a compressor 2B, and be switched to only another compression
When machine 2A is operated, the target specific rotation of the compressor 2A of continuous running is uprushed as specified specific rotation 100%.But actual pressure
The specific rotation of contracting machine 2A does not follow the target specific rotation uprushed in this way, and causes to generate sluggishness, and lead to compressed gas
Discharge rate is temporarily insufficient.
In contrast, in the compressed gas feedway 1 of present embodiment, as shown in figure 3, in separate control area R2
In, the revolving speed of the compressor 2B stopped in independent control area R3 is less than the compressor 2A of continuous running.Therefore, it is reached in load factor
When to second threshold L2 by compressor 2B stopping, although increasing the specific rotation of compressor 2A, its variation very little.It is tied
The followability of specific rotation when fruit is the operating number variation for improving compressor 2 also can reduce discharge rate deficiency.
In addition, when load factor L reaches second threshold L2 and stops compressor 2B, although making the compressor of continuous running
The specific rotation of 2A increases, but the specific rotation of compressor 2A in this case is set to the maximum specific rotation (100%).It is right as a result,
For the compressor 2A being transferred to after independent control area R3, it can be operated in the good region of efficiency.
Monotonously reduce even if load factor L it should be noted that also considering and reach second threshold L2, later, because of load
The case where rate L changes and continually generates the transfer between separate control area R2 and independent control area R3.In such feelings
Under condition, if transfer all changes the number of units of compressor 2 every time, cause invalidly to consume energy, and deterioration may be developed etc..
It therefore, can be with load factor L when independent control area R3 keeps providing in the case where load factor L reaches second threshold L2
Between be condition, make compressor 2B stop.
Fig. 4 is the measurement knot of the relationship between the specific rotation and efficiency indicated corresponding to the compressed gas feedway 1 of Fig. 3
The chart of fruit.
It should be noted that merging the survey for indicating three comparative examples together with the measurement result of present embodiment in Fig. 4
Determine result.First comparative example is in load factor L from nominal load Lmax(200%) compressor 2A is tieed up until first threshold L1
It holds at specified operating (100% specific rotation), while compressor 2B is only changeably controlled according to load factor L, and less than
Stop the compressor 2B for reaching lower limit specific rotation when one threshold value L1, the example of compressor 2A is changeably controlled according to load factor L
(that is, one control example being only changeably controlled in multiple compressors 2).Second comparative example is in load factor L from volume
Fixed load Lmax(200%) until second threshold L2 (100%) in a manner of making compressor 2A, 2B that there is common specific rotation
Variable control is carried out, and when being less than second threshold L2 (100%), stops a compressor 2B, is only changeably controlled another
The example of one compressor 2A will be (that is, identically as the co- controlling region R1 of present embodiment, will be in operating condition
Whole compressors 2 specific rotation control be the identical example for reaching second threshold L2 until load factor L).Third comparative example is
The case where using only single compressor, in order to present embodiment and/or other comparative examples comparably compared with, it is double to indicate negative
The size of load rate and specific rotation.
As shown in figure 4, when the specific rotation of compressed gas feedway 1 is 170% or more, in present embodiment and first
To between third comparative example without apparent difference, but if the specific rotation of compressed gas feedway 1 less than 170%,
Present embodiment and the second comparative example all obtain good efficiency compared with the first comparative example.This is indicated, in co- controlling region
In R1, by being commonly controlled the specific rotation of two compressor 2A, 2B, a pressure is only changeably controlled like that with the first comparative example
The case where contracting machine, is compared, and good efficiency can be obtained.
In addition, if the specific rotation of compressed gas feedway 1 less than 100%, present embodiment and the second comparative example
Compared to the more good efficiency of acquisition.Here, Fig. 5 corresponds to each compression of the specific rotation in the compressed gas feedway 1 of Fig. 3
The detail of machine 2A, 2B, Fig. 6 are the detail of each compressor 2A, 2B of the specific rotation in the second comparative example.By comparing Fig. 5 and Fig. 6
It is found that in the present embodiment, compared with the second comparative example, the operating ratio in unfavorable low rotary area is effectively reduced,
As a result, obtaining good efficiency.
In addition, as it appears from the above, because of the compressor 2B's in the R2 of separate control area, stopped in independent control area R3
Revolving speed is less than the compressor 2A of continuous running, so when load factor reaches second threshold L2, along with the stopping of compressor 2B
Compressor 2A target specific rotation variation be less than other comparative examples.As a result, improving the operating platform for reducing compressor 2
It is insufficient also to can reduce the discharge rate temporarily generated for the followability of specific rotation when number.
In addition, as shown in figure 4, because in the present embodiment, until the specific rotation for reaching 30% can operate, so
Compared with third comparative example, capable of covering wider array of specific rotation, (in third comparative example, specific rotation 60% is transport maximum, phase
For this, in the present embodiment, specific rotation 30% is transport maximum).
Then, to make the load factor of compressed gas feedway 1 from lower limit load factor Lmin(30%) change with being gradually increased
In the case where the control content of specific rotation be specifically described.Fig. 7 is the rotation for indicating compressor 2A, 2B when load factor L increases
Chart of the rate of rotation relative to the control example of the load factor L of compressed gas feedway 1.
Firstly, in independent control area R3, so that the specific rotation of a compressor 2A monotonously increases according to load factor L
Mode controlled.At this point, not consuming useless energy because another compressor 2B is in halted state, press
Contracting gas supply device 1 is whole to obtain good efficiency.
If load factor L increases and reaches second threshold L2, compressor 2B starting.The rotation of compressor 2B when starting
Rate is set to, the prespecified lower limit specific rotation (30%) for specification.Then, in the R2 of separate control area, according to load
Rate L increases the specific rotation of compressor 2B, and reduces the specific rotation of compressor 2A according to load factor L.In the example of Fig. 3
In, the specific rotation of compressor 2A, 2B in the R2 of separate control area are controlled as, relative to load factor in a manner of quadratic function
It changes.
The specific rotation of compressor 2A, 2B for being independently controlled in the R2 of separate control area in this wise are controlled as, and are being made
The first threshold L1 on boundary between separate control area R2 and common control area R1 is consistent.Rotation at first threshold L1
Rate is set to, and the specific rotation of compressor 2A is maintained constant value in the R2 of separate control area with when reducing load factor L
A1 equal (referring to Fig. 3).
Then, in the R1 of co- controlling region so that compressor 2A, 2B have common specific rotation while, along with
Load factor increases and mode that specific rotation monotonously increases is controlled.
It should be noted that also considering that even if load factor L increases and reaches second threshold L2, later because load factor L changes
And the case where generating continually transfer between independent control area R3 and separate control area R2.In this case,
If transfer all changes the number of units of compressor 2 every time, energy is invalidly consumed, and deterioration may be developed.Therefore, it is loading
In the case that rate L reaches second threshold L2, it can be kept for the stipulated time as condition in separate control area R2 using load factor L, made
Compressor 2B starting.
As described above, three kind control area (co- controlling region R1, independent control area corresponding with load factor L are distinguished
Domain R2 and independent control area R3) come control constitute compressed gas feedway 1 each compressor 2 revolving speed.(i) it is controlling jointly
In region R1 processed, in the case where load factor L is first threshold L1 or more, turning for multiple compressors in operating is coequally controlled
Speed.Therefore, the ratio that compressed gas feedway operates in the low rotation speed area that efficiency deteriorates is reduced, good effect is obtained
Rate.(ii) in the R2 of separate control area, at least one that will stop when being transferred to back to back independent control area R3 is pressed
The revolving speed of contracting machine 2B independently controls as less than the revolving speed of other compressor 2A.As a result, in the reduction along with load factor L
And when being transferred to independent control area R3 from separate control area R2, when the revolving speed of other compressor 2A can will be made to increase
Variation inhibits to obtain very little, inhibits the amount for being equivalent at least one compressor 2B stopping.As a result, reducing the pressure in operating
When the number of units of contracting machine 2, the followability of the revolving speed of the compressor 2 of continuous running can be improved, and can alleviate compressed gas
The temporarily insufficient phenomenon of discharge rate.
The case where having two compressor 2A, 2B to above-mentioned compressed gas feedway 1, is illustrated, but hereinafter, can
With the compressor 2 with more number of units.Fig. 8 is the overall structure for indicating the compressed gas feedway 1 with three compressors 2
Ideograph.In this example embodiment, for for Fig. 1 the case where, other than compressor 2A, 2B, also there is third compressor
2C, this three compressor 2 have mutually the same structure.
Compressor 2C has the electric motor 16C that revolving speed can be controlled by converting means 18C, by the compressed air of generation
It is discharged from discharge pipe 4C.Discharge pipe 4C collaborates together with discharge pipe 4A, 4B in main discharge 6.In addition, being configured to utilize pressure
The load of force snesor 20C detection compressor 2C.
Load factor test section 102 by obtain pressure sensor 20A, 20B, 20C detected value, obtain compressor 2A, 2B,
The load factor of 2C calculates the whole load factor L of compressed gas feedway 1 by adding up to them.In present embodiment
In, because compressed gas feedway 1 has three compressors 2, maximum load rate LmaxIt is 300%.
Load factor L of the control unit 104 based on the compressed gas feedway 1 calculated by load factor test section 102, control pressure
The specific rotation of contracting machine 2A, 2B, 2C.The specific rotation control of such compressor 2A, 2B, 2C can have above-mentioned two by extension
Specific rotation in the case where compressor 2A, 2B is controlled and is applied.That is, if it is considered that making load factor L from nominal load rate (300%)
The case where reduction, then drives compressor 2A, 2B, 2C to reach 200% until load factor L, but if reaching load factor 200%, then
Compressor 2C stops, and when being less than load factor 200%, only drives compressor 2A, 2B.So stopping pressing with load factor 200%
When contracting machine 2C, just so that three compressions until load factor reaches specified value (relative to first threshold L1) greater than 200%
There is the mode of common specific rotation to be controlled by machine 2A, 2B, 2C, be (to be equivalent to the from the specified value to 200% in load factor
Two load factor L2) when, it is independently controlled in a manner of making specific rotation of the specific rotation of compressor 2C less than compressor 2A, 2B.
At this point, the specific rotation of compressor 2A, 2B of continuous running can also be maintained constant even if load factor is less than 200%.As a result,
When load factor reaches 200% and stops compressor 2C, the specific rotation of compressor 2A, 2B are easy to follow target specific rotation, energy
Enough inhibit discharge rate insufficient.
It is and above-mentioned because the compressor 2 in operating is two it should be noted that when load factor is less than 200%
Embodiment is identical.
Fig. 9 be indicate corresponding to Fig. 8 compressed gas feedway 1 efficiency relative to specific rotation measurement result figure
Table.In Fig. 9, as the comparative example of present embodiment, the 5th comparative example (model for being 300% to 200% in load factor L is indicated
In enclosing, compressor 2A, 2B maintain 100% specific rotation and compressor 2C are only changeably controlled, load factor L be 200% to
In the range of 100%, compressor 2A maintains 100% specific rotation and compressor 2B is changeably controlled and stops compressor 2C,
When load factor L is less than 100%, compressor 2A is only changeably controlled and stops the example of compressor 2B, 2C), the 6th comparative example
(in the range of load factor L is 300% to 200%, in a manner of making three compressor 2A, 2B, 2C that there is common specific rotation
It is controlled, in the range of load factor L is 200% to 100%, so that two compressor 2A, 2B have common specific rotation
Mode controlled and stopped compressor 2C, when load factor L is less than 100%, only operates and compressor 2A and stop pressing
Contracting machine 2B, 2C), the 7th comparative example (compressor 2 is changeably controlled, only in order to same with other embodiments and/or comparative example
Etc. ground evaluation, the expression of specific rotation and load factor is sized to three times).
As shown in figure 9, present embodiment relative to the 5th~the 7th comparative example, obtains good efficiency in a wide range.
This represent, it is corresponding with said effect referring to Fig. 4, even if also obtaining identical effect in the case where increasing the number of units of compressor 2
Fruit.
In addition, Figure 10 corresponds to each compressor 2A, 2B, 2C's of the specific rotation in the compressed gas feedway 1 of Fig. 8
Detail, Figure 11 are the detail of each compressor 2A, 2B, 2C of the specific rotation in the 6th comparative example.It is illustrated in Figure 10, this implementation
Compared with Figure 11, the operation range of low specific rotation narrows mode.This represent present embodiment is by cutting down the low low rotation of efficiency
Turn region, obtains good efficiency.
As described above, according to above embodiment, being capable of providing one kind relative to load change has good follow
Property, and the compressed gas feedway of energy consumption and the control method of compressed gas feedway can be reduced.
Claims (8)
1. a kind of compressed gas feedway can supply the compressed gas being discharged from multiple compressors,
Wherein,
The compressed gas feedway has:
Multiple compressors, their parallel configurations；
Load factor test section detects the load factor of the compressed gas feedway；And
Control unit controls multiple compressors based on the load factor detected by the load factor test section respectively
Specific rotation,
The control unit is configured to, in the co- controlling region that the load factor is first threshold or more, so that multiple described
There is compressor the mode of common specific rotation to be controlled, and be from the first threshold to less than described the in the load factor
In separate control area until the second threshold of one threshold value, so that the rotation of at least one compressor in multiple compressors
The mode that rate of rotation is less than the specific rotation of other compressors is independently controlled, and is less than the second threshold in the load factor
Independent control area in, stop at least one described compressor and control the specific rotation of other compressors.
2. compressed gas feedway as described in claim 1, wherein
The control unit is so that the specific rotation of at least one compressor in the separate control area is born relative to described
The mode that the change degree of load rate is greater than the change degree in the co- controlling region is controlled.
3. compressed gas feedway as claimed in claim 1 or 2, wherein
The control unit is in the case where the load factor is in reduction trend, in the separate control area, by described at least
The specific rotation of one compressor is maintained constant.
4. compressed gas feedway as claimed any one in claims 1 to 3, wherein
The control unit is being transferred to the independent control area from the separate control area due to load factor reduces
In the case of, it is kept for the stipulated time as condition in the independent control area using the load factor, makes at least one described compressor
Stop.
5. compressed gas feedway according to any one of claims 1 to 4, wherein
The control unit is in the case where the reduction along with the load factor stops at least one described compressor, by institute
The specific rotation control of other compressors is stated as maximum specific rotation.
6. the compressed gas feedway as described in any one of claims 1 to 5, wherein
The control unit is in the case where the load factor is in increase tendency, in the separate control area, according to described negative
Load rate increases the specific rotation of at least one compressor, and makes the rotation of other compressors according to the load factor
Rate of rotation reduces.
7. such as compressed gas feedway described in any one of claims 1 to 6, wherein
The control unit is being transferred to the separate control area from the independent control area due to load factor increases
In the case of, it is kept for the stipulated time as condition in the separate control area using the load factor, makes at least one described compressor
Starting.
8. a kind of control method of compressed gas feedway, the compressed gas feedway can be supplied from parallel configuration
The compressed gas of multiple compressor discharges,
Wherein,
The control method of the compressed gas feedway comprises the following steps:
Load factor detects process, in load factor detection process, detects the load factor of the compressed gas feedway；And
Process is controlled, in the control process, based on the load factor detected, controls turning for multiple compressors respectively
Speed,
In the control process, in the co- controlling region that the load factor is first threshold or more, so that multiple described
There is compressor the mode of common specific rotation to be controlled, and be from the first threshold to less than described the in the load factor
In separate control area until the second threshold of one threshold value, so that the rotation of at least one compressor in multiple compressors
The mode that rate of rotation is less than the specific rotation of other compressors is independently controlled, and is less than the second threshold in the load factor
Independent control area in, stop at least one described compressor and control the specific rotation of other compressors.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710804518.4A CN109469602B (en) | 2017-09-07 | 2017-09-07 | Compressed gas supply device and control method for compressed gas supply device |
| JP2019541023A JP6823186B2 (en) | 2017-09-07 | 2018-09-07 | Control method of compressed gas supply device and compressed gas supply device |
| PCT/JP2018/033204 WO2019049987A1 (en) | 2017-09-07 | 2018-09-07 | Compressed gas supply device and method for manufacturing compressed gas supply device |
Applications Claiming Priority (1)
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| CN201710804518.4A CN109469602B (en) | 2017-09-07 | 2017-09-07 | Compressed gas supply device and control method for compressed gas supply device |
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| CN109469602B CN109469602B (en) | 2021-07-02 |
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| JPH11343986A (en) * | 1998-06-02 | 1999-12-14 | Hitachi Ltd | Compressor control device |
| CN201666246U (en) * | 2009-05-26 | 2010-12-08 | 深圳市阿徕米罗科技有限公司 | Workstation energy-saving system of air compressor |
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Also Published As
| Publication number | Publication date |
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| WO2019049987A1 (en) | 2019-03-14 |
| CN109469602B (en) | 2021-07-02 |
| JP6823186B2 (en) | 2021-01-27 |
| JPWO2019049987A1 (en) | 2020-09-17 |
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