WO1999051883A1 - Systeme de diagnostic destine a un mecanisme a fluide - Google Patents

Systeme de diagnostic destine a un mecanisme a fluide Download PDF

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Publication number
WO1999051883A1
WO1999051883A1 PCT/JP1999/001661 JP9901661W WO9951883A1 WO 1999051883 A1 WO1999051883 A1 WO 1999051883A1 JP 9901661 W JP9901661 W JP 9901661W WO 9951883 A1 WO9951883 A1 WO 9951883A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid machine
flow rate
head
power consumption
operating
Prior art date
Application number
PCT/JP1999/001661
Other languages
English (en)
Japanese (ja)
Inventor
Masakazu Yamamoto
Yoshio Miyake
Junya Kawabata
Keita Uwai
Yoshiaki Miyazaki
Katsuji Iijima
Hiromi Tamai
Original Assignee
Ebara Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ebara Corporation filed Critical Ebara Corporation
Priority to AU30537/99A priority Critical patent/AU3053799A/en
Priority to JP2000542580A priority patent/JP3343245B2/ja
Priority to EP99912058A priority patent/EP1072795A4/fr
Publication of WO1999051883A1 publication Critical patent/WO1999051883A1/fr

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Classifications

    • 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
    • F04B51/00—Testing machines, pumps, or pumping installations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0088—Testing machines
    • 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

Definitions

  • the present invention relates to a diagnostic system for a fluid machine, and more particularly, to a system for grasping wasteful energy consumed around a fluid machine. Understand-is about a system for verification. Background art
  • General-purpose pumps are not essential criteria. In other words, instead of manufacturing a pump according to the essentials (flow rate and head), select a pump that exceeds the essentials from the inventory.
  • the design parameters are generally calculated at the maximum flow rate with a margin for the flow rate, and the margin and aging of the pipe loss are expected. Therefore, the actual operation involves valve adjustment to suppress the excessive flow rate, which is wasteful. In other words, even if the pump is selected according to the calculation formula, it will be much smaller and more wasteful.
  • the decisive factor in energy saving is to match the essentials of the “true” (minimum necessary flow rate and head, which can only be found by operating the pump at the site) and to operate the pump efficiently without waste. For example, if it seems that there is too much capacity in the pumps after operation at the site, it is possible to save energy by the following method.
  • the inverter can easily and reversibly adjust the pump performance, so that drastic energy saving operation can be realized each time.
  • the flow-pressure characteristic (Q-H characteristic) of a centrifugal pump is represented by a single curve with the horizontal axis representing the flow rate (discharge rate) and the vertical axis representing the total head (pressure). It was displayed and, if appropriate, the pump shaft power (output), pump efficiency, pump suction performance (required (Requ ired) NPSH), and current value (for motor pump) were also described.
  • general-purpose pumps are not based on the essential criteria, that is, they do not manufacture pumps according to the essential requirements (flow rate and head), but plan from stock. In most cases, pumps that exceed the requirements (larger pumps) are selected and used.
  • the crucial factor in energy saving is the “true” requirements (the minimum necessary flow rate that can be found only after operation at the site ⁇ Head The goal is to match the operating points of the pumps to achieve efficient operation without waste. Therefore, an extremely large energy saving effect can be obtained by decelerating the pump with the inverter.
  • FIG. 43A shows a partially enlarged view
  • FIG. 43B shows an entire view.
  • a first object of the present invention is to provide a diagnostic system for a fluid machine that can grasp wasteful energy consumed around the fluid machine.
  • Another object of the present invention is to provide an energy-saving pre-diagnosis system for a fluid machine capable of easily calculating the energy-saving amount brought by the rotation speed adjustment utilizing an inverter (frequency converter) or the like. Purpose.
  • a third object of the present invention is to provide a method for indicating the characteristics of a fluid machine and a display object capable of comprehending the information and thereby making it possible to penetrate the market with energy saving.
  • the diagnostic system for a fluid machine of the present invention employs the modes listed in (1) to (4).
  • a first specification method for specifying the characteristics of the fluid machine represented by the flow-head characteristics Operating the fluid machine to be diagnosed, and inputting a measurement result of an operating pressure (head), an operating flow rate, a power consumption, or an operating current value of the fluid machine at the time of the operation.
  • Second specifying means for specifying the operating flow rate or operating pressure of the fluid machine based on the relationship between the measured characteristics of the fluid machine and the measured operating pressure or operating flow rate of the fluid machine; and the fluid machine to be diagnosed.
  • a processing means for calculating a change in the operating flow rate, operating pressure, or power consumption when the rotation speed is changed, and displaying the calculation result.
  • the function to specify the characteristics of the fluid machine represented by the flow-head characteristics and the operation of the fluid machine to be diagnosed By inputting the measurement result of the operating pressure (head), operating flow rate, power consumption, or operating current value of the fluid machine during operation, the characteristics of the specified fluid machine and the measured operating pressure of the fluid machine are obtained. Or a function to specify the operating flow rate or operating pressure of the fluid machine based on the relationship with the operating flow rate, and calculate the change in operating flow rate, operating pressure, or power consumption when the rotational speed of the fluid machine to be diagnosed is changed.
  • a fluid machine diagnostic system comprising: a conversion unit; and a processing unit configured to calculate a change in an operating point when the rotation speed of the fluid machine to be diagnosed is changed, and to display a calculation result.
  • the amount of energy saved by the rotation speed adjustment using an inverter (frequency converter) or the like is reduced before the rotation speed adjustment is performed. Can be estimated.
  • Each means or step of the present invention is executed by a computer such as a programmed personal computer. It should be noted that the embodiment of the present invention described in the above (4) includes a case where some steps are not executed by a computer but are executed by other means (manual work or the like).
  • another aspect of the present invention is a method for controlling a fluid machine, which is based on the diameter and the number of impeller stages, and the rated output and the rated rotation speed of a motor that drives the fluid machine.
  • the head and shaft power at each flow rate are calculated by determining the representative points of the fluid mechanical characteristics including the head and representative shaft power, and the ratio of the head and shaft power to the representative head and representative shaft power other than the representative flow rate. Assuming provisional characteristics of the fluid machine, and at least the present conditions, correcting the provisional characteristics based on measurement data including the head and power consumption during operation, and correcting the provisional characteristics, and the operating point including the operating flow rate. And a fluid mechanical characteristic specifying method.
  • one embodiment of the present invention relates to a flow rate-pressure (head) and flow rate-power consumption data of a fluid machine with a motor when driven by an AC commercial power supply, and data on the equipment side.
  • Another aspect of the present invention relates to data on flow rate-pressure (head) and flow rate-power consumption of a fluid machine with a motor when driven by an AC commercial power supply, and planning requirements on the equipment side (flow rate-pressure).
  • the present invention adopts the modes listed in (1) to (5).
  • information related to power consumption can be obtained at a glance simultaneously in accordance with the flow rate-pressure characteristic of a fluid machine that varies depending on the number of revolutions, so that, for example, when an inverter is introduced (added) You can easily understand the return on investment.
  • a display object displaying the characteristics of the fluid machine using the method for displaying the characteristics of the fluid machine described in (1).
  • Such display materials include sales materials represented by catalogs and the like.
  • FIG. 1 is a block diagram showing a hardware configuration of a diagnostic system for a fluid machine according to the present invention.
  • FIG. 2 is a diagram illustrating a diagnostic procedure in the diagnostic system for a fluid machine according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.
  • FIGS. 3A and 3B are diagrams for explaining a diagnostic procedure in the fluid machine diagnostic system according to the present invention, and are diagrams showing characteristic curves of the fluid machine.
  • FIGS. 4A and 4B are diagrams for explaining a diagnosis procedure in the diagnosis system for a fluid machine according to the present invention, and are diagrams showing characteristic curves of the fluid machine.
  • FIGS. 5A and 5B are diagrams illustrating a diagnostic procedure in the diagnostic system for a fluid machine according to the present invention, and are diagrams illustrating characteristic curves of the fluid machine.
  • FIG. 6 illustrates a diagnosis procedure in the fluid machine diagnosis system according to the present invention.
  • FIG. 4 is a diagram illustrating a characteristic curve of a fluid machine.
  • FIG. 7 is a diagram illustrating a diagnostic procedure in the diagnostic system for a fluid machine according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.
  • FIG. 8 is a diagram illustrating a diagnostic procedure in the diagnostic system for a fluid machine according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.
  • FIG. 9 is a diagram for explaining a diagnosis procedure in the diagnosis system for a fluid machine according to the present invention, and is a diagram showing a characteristic curve of the fluid machine.
  • FIG. 10 is a diagram illustrating a diagnostic procedure in the fluid machine diagnostic system according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.
  • FIG. 11 is a diagram illustrating a diagnostic procedure in the fluid machine diagnostic system according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.
  • FIG. 12 is a diagram illustrating a diagnostic procedure in the fluid machine diagnostic system according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.
  • FIG. 13 is a schematic process flowchart showing an outline of a process flow in the fluid machine diagnostic system shown in FIGS. 1 to 12.
  • FIG. 14 is a side view showing a first mode of mounting work when using the performance adjusting device for a fluid machine.
  • FIG. 15 is a side view showing a second mode of mounting work when using the performance adjusting device for a fluid machine.
  • FIG. 1 6 A and FIG. 1 6 B is a diagram showing details of performance adjustment apparatus shown in FIG. 1 4, 1 6 A partially sectional been front view, FIG. 1 6 B is a side view c FIG. 17 is a sectional view taken along the line XVII—XVII of FIG. 16A.
  • FIG. 1 8 A and FIG. 1 8 B is a diagram showing details of performance adjustment apparatus shown in FIG. 1 5, 1 8 A partially sectional been front view, FIG. 1 8 B is a plan view t FIG. 19 is a sectional view taken along line XIX-XIX of FIG. 18A.
  • FIG. 20A and FIG. 20B are diagrams showing a third mode of mounting work when using the performance adjusting device for a fluid machine, FIG. 20A is a side view, and FIG. 20B is FIG. 20A.
  • FIGS. 21A and 21B show another embodiment of the performance adjusting device main body shown in FIGS. 14 to 20.
  • FIG. 21A is a front view
  • FIG. 21B is a side view.
  • FIG. 22 is a diagram illustrating a diagnostic procedure in the fluid machine diagnostic system according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.
  • FIG. 23 is a schematic diagram showing an example of equipment brought to the operation site of the fluid machine to be diagnosed.
  • Figure 24 shows the dimensionless characteristics of the pump, which shows the characteristics of the pump with respect to the specific speed (flow-head, flow-axis power) in a dimensionless manner.
  • FIG. 25 is a graph showing specific speed-pump efficiency characteristics.
  • FIG. 3 is a diagram showing an assumed stage, a pump operation point (flow rate) specification, and a temporary characteristic correction stage.
  • FIG. 3 is a diagram showing a stage of assuming a temporary pump characteristic, a stage of specifying a pump operating point (flow rate), and a stage of correcting the temporary characteristic when correcting with power consumption.
  • Figures 28A to 28D show the tentative characteristics, the flow rate calculated using the head and power consumption under the current operation, the assumed values of the fluid machine efficiency and the motor efficiency, and the head during the valve fully open operation.
  • pump tentative characteristics correction of pump operating point (flow rate) and correction of tentative characteristics It is a figure showing a floor.
  • FIG. 4 is a diagram showing a stage of assuming a temporary pump characteristic, a stage of specifying a pump operating point (flow rate), and a stage of correcting the temporary characteristic when correcting the head and power consumption during operation.
  • Fig. 3 OA to Fig. 30D show the assumption stage of the pump temporary characteristics and the pump when the operating point (flow rate) is specified from the temporary characteristics and the head during the current operation, and the temporary characteristics are corrected with the current power consumption. It is a figure which shows the specification stage of an operating point (flow rate), and the correction of a temporary characteristic.
  • FIG. 3 is a diagram showing a stage of assuming temporary pump characteristics and a stage of specifying a pump operating point (flow rate) and correcting temporary characteristics.
  • FIG. 32 is a diagram illustrating a diagnosis procedure in the energy-saving pre-diagnosis system for a fluid machine according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.
  • FIG. 33 is a diagram illustrating a diagnosis procedure in the energy-saving pre-diagnosis system for a fluid machine according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.
  • FIG. 34 is a diagram showing an example of outputting a result of a diagnosis performed by the energy saving preliminary diagnosis system for a fluid machine according to the present invention.
  • FIG. 35 is a diagram showing a portion A of FIG.
  • FIG. 36 is a schematic diagram showing an example of an energy-saving pre-diagnosis system for a fluid machine using a personal computer.
  • FIG. 37 is a diagram showing the characteristics of the fluid machine according to the first embodiment of the method for displaying the characteristics of the fluid machine and the display object according to the present invention.
  • Figure 38 is a diagram attached to an explanation of an example of a simple calculation of the return on investment by introducing an inverter.
  • FIG. 39 is a diagram showing the characteristics of the fluid machine according to the second embodiment of the method for displaying the characteristics of a fluid machine and the display object according to the present invention.
  • FIG. 40 is a diagram showing the characteristics of the fluid machine according to the third embodiment of the fluid machine characteristic display method and the display object according to the present invention.
  • FIG. 41 is a schematic processing flow chart showing an outline of the processing flow in the calculation / drawing system.
  • FIG. 42 is a diagram showing an example of a conventional display example of pump characteristics.
  • FIGS. 43A and 43B are diagrams showing other examples of display examples of other conventional pump characteristics. BEST MODE FOR CARRYING OUT THE INVENTION
  • the fluid machine diagnostic system includes a first specifying means for specifying the characteristics of the fluid machine represented by the flow-head characteristic by inputting predetermined information of the fluid machine to be diagnosed; By operating the target fluid machine and inputting the measurement results of the operating pressure (head), operating flow rate, power consumption, or operating current value of the fluid machine at the time of operation, the characteristics and measurement of the specified fluid machine can be performed.
  • Second specification means for specifying the operating flow rate or operating pressure of the fluid machine based on the relationship with the operating pressure or operating flow rate of the fluid machine, and the operating flow rate when the rotational speed of the fluid machine to be diagnosed is changed or operating pressure or by calculating a change in power consumption c Figure 1 comprising a processing means for displaying the calculation result, the hardware configuration of the diagnostic system of the fluid machine according to the present embodiment FIG.
  • a pump will be described as an example of a fluid machine.
  • the diagnostic system for a fluid machine includes a main control unit 1 that integrally controls the entire system, and a main storage device 2 that is connected to the main control unit 1.
  • the main control unit 1 includes a control device 3 and a computing device 4.
  • the main control unit 1 is connected to an input device 5 including a keyboard and a mouse, and an output device 6 including a printer and a display.
  • thick arrows indicate the flow of data and programs
  • thin arrows indicate the flow of control signals.
  • the main control unit 1 has a control program for the operating system, etc., a program that defines the diagnostic procedures for the fluid machinery, and an internal memory for storing required data.
  • the first specifying means, the second specifying means and the processing means are realized.
  • the main storage device 2 is composed of a hard disk, a flexible disk, an optical disk, or the like, and stores data of various pumps currently on the market.
  • This data does not necessarily have to be accurate data of each pump. That is, average data for specifying the characteristics of the pump to some extent by inputting the values of the bore and the output, or element data modeled in advance may be used.
  • the characteristics of the motor pump to be diagnosed can be specified by the first specifying means incorporated in the main control unit 1 ( specifically, for example,
  • the first specification method specifies the flow-to-head characteristics and the flow-to-power consumption characteristics of the pump based on these data. This specification is performed, for example, by selecting a close data from the data stored in the main storage device 2.
  • the information (data) to be input to the input device 5 includes, in addition to the above, essential information on the nameplate of the pump, the name of the pump, the number of stages of the pump impeller, the outer diameter of the impeller of the pump, the test data of the pump, and the like. Is included.
  • FIG. Fig. 2 is a diagram showing the flow rate-head characteristics and flow-power consumption characteristics of the pump.
  • the horizontal axis shows the flow rate (Q), and the vertical axis shows the head (H) or power consumption (W).
  • the flow rate-head characteristic and the flow rate-power consumption characteristic of the pump are specified with a predetermined width by the first specification method based on the input result. That is, the area of the shaded area a is specified.
  • the dashed line indicates the upper and lower limits of the area of the shaded area a, and the solid line is the center line of the area of the shaded area a.
  • the result specified by the first specifying means is displayed on the output device 6 including a display such as LCD (liquid crystal).
  • the shaded area a is configured so that the accuracy is corrected by the input data and the range is narrowed. That is, for example, if the manufacturer and the machine name of the pump are known, the characteristics can be specified with higher accuracy, so that the area of the hatched portion a can be minimized as shown in FIG. 3B from the state of FIG. 3A.
  • the result specified by the first specifying means is further corrected for accuracy by inputting the power consumption of the fluid machine at the actual operating point. That is.
  • the power consumption of the motor during the actual operation is measured and the accuracy is corrected by inputting it to the input device 5, and as shown in Fig. 4B from the state of Fig. 4A, the shaded area a indicates the actual power consumption of the motor.
  • the shaded area a is modified to include the value of.
  • the accuracy of the result specified by the first specifying means is further corrected from the state of FIG. 5A by inputting the operating pressure and power consumption during the actual shutoff operation as shown in FIG. 5B. That is, the hatched area a is corrected so that the area of the hatched area a includes the operating pressure and the power consumption during the actual shutoff operation.
  • the results specified by the first specification means can be further corrected by inputting pump test data (flow-head, flow-power consumption) performed before the pump was shipped from the factory, etc.
  • pump test data flow-head, flow-power consumption
  • FIG. 6 the characteristics of the pump can be specified with extremely high accuracy.
  • you enter some of the above data without inputting pump test data it is possible to specify something similar to that shown in Figure 6.
  • FIG. 5B from the state where the accuracy is corrected as shown in FIG. 5B, by further selecting the center line of the area of the hatched area a, it is possible to perform the specification close to that of FIG.
  • the operating point of the pump in the facility can be specified.
  • the pump to be diagnosed is operated, and the actual operating pressure (head) or operating flow rate or power consumption is measured and input to the input device 5 to operate the second specifying means. .
  • the operating pressure (head) and operating flow can be specified as shown in Fig. 9 by finding the intersection of the flow rate-head characteristic curve and the flow rate-power consumption characteristic curve. At this time, the operating current value may be measured and input instead of the power consumption.
  • the operating pressure can be easily calculated simply by installing a compound gauge on the suction side of the pump and a pressure gauge on the discharge side of the pump.
  • the actual head can be more accurately grasped by using a controller described later.
  • the processing means functions as follows.
  • a curve 8 is a flow rate-head characteristic of the pump specified by the first specifying means.
  • the processing means sets a certain rotational speed ratio for these points. Now, when the rotational speed ratio between 0.9 5 moves to qt qi XO. 10 5, moves the h di h X 0. 9 5 2 .
  • Curve] 3 is the resistance curve on the equipment side (piping side) calculated by the method shown in Fig. 10 described above. Points indicated by 8 are actual operating points, and points 7 to ⁇ are calculated operating points when the rotational speed is changed.
  • Curve y 8 is a flow one power dissipation characteristics of the pump identified by first specifying means.
  • the processing means sets a certain rotational speed ratio for these points as described above. Assuming that the rotation speed ratio is 0.95, move to qdq 'XO. To move to the X 0. 9 5 3.
  • Curve y 8 to? The above is shown the power consumption corresponding to the operating point of 8 ⁇ 1 at point.
  • the points marked with diagonal lines are the design points of the equipment. In other words, it is a calculation point that when a flow rate of 350.01 in is required, the pipe resistance including the actual head will be 38.5 m. On the other hand, point ⁇ ⁇ is the actual operating point.
  • the processing means displays the appropriate pump speed for the design flow rate and the power consumption at that speed (operating point).
  • point 4 is the appropriate operating point.
  • Table 1 To
  • the design point flow rate was defined as an appropriate operating point.
  • the design point flow is not always an appropriate operating point. It is more common to determine the design point flow rate a little more with a margin than the actual required flow rate. In this case, the number of rotations can be further reduced, and the power can be further saved.
  • FIG. 13 is a schematic processing port diagram schematically showing a processing flow in the fluid machine diagnosis system shown in FIGS. 1 to 12 and described in detail.
  • step 1 information to specify the characteristics of the fluid machine that is actually operating, which is the object to be diagnosed (pump diameter, motor rating) Output, etc.) to the input device 5.
  • step 2 information (measured values such as operating pressure or operating flow rate) for specifying the operating point of the fluid machine that is actually operating is input to the input device 5.
  • step 3 information (such as actual head) for specifying the resistance characteristics of the equipment is input to the input device 5.
  • step 4 the change of the operating point of the fluid machine when the rotation speed of the fluid machine is changed is calculated by the calculating device 4 and displayed on the output device 6.
  • the amount of wasteful energy consumed around the pump can be grasped without bringing the inverter or the like to the site. Therefore, for example, the return on investment when introducing an inverter etc. becomes clear, and the effect of spreading energy saving to the market can be expected.
  • the present invention further proposes a controller having a frequency converter as a main component as a means for eliminating the grasped waste.
  • the present applicant proposes a performance adjusting device for a fluid machine as one of the most suitable controllers to be combined with the present invention.
  • a performance adjusting device for a fluid machine suitable for combination with the present invention provides a technique capable of easily adjusting the performance of a pump and achieving energy saving. It is possible to adjust the performance of the pump simply by adding an inverter without any change.
  • FIG. 14 shows a first embodiment of the mounting operation when the performance adjusting device for a fluid machine according to the present invention is used.
  • Reference numeral 101 denotes a pump unit, and a pump The unit 101 has a configuration in which a pump 103 and an electric motor 104 are provided above a common base 102.
  • the fluid guided from the suction pipe 105 passes through the suction-side gate valve 106 and the short pipe 107, is sucked into the pump 103 from the pump suction port 103a, and is pressurized. Exhausted from pump outlet 103 b.
  • the discharged fluid further passes through the check valve 108 and the discharge-side gate valve 109 and is guided to the discharge pipe 110.
  • the performance adjusting device for fluid machinery (hereinafter referred to as the adjusting device) is attached to the short pipe 1 7 via the heat dissipating means 112 made of aluminum alloy with good thermal conductivity.
  • the heat radiating means 112 is fixed to the adjusting device 111 by bolts (not shown), and is also fixed to the short pipe 107 by U bolts (not shown).
  • the power supplied from the control panel 1 13 is guided from the input side cable 1 14 which is the input means of the adjusting device 1 11 to the frequency converter housed in the adjusting device 1 1 1 and the frequency is converted. .
  • the electric power whose frequency has been converted is supplied to the electric motor 104 from the output-side cable 115 serving as the output means of the adjusting device 111.
  • the frequency conversion in the adjustment device 111 involves heat loss, but in this embodiment, the heat loss is radiated to the pump handling fluid via the heat radiating means 112 and the short pipe 107.
  • FIG. 15 shows a second embodiment of the mounting work when using the adjusting device according to the present invention.
  • Reference numeral 101 denotes a pump unit, and the pump unit 101 has a configuration in which a pump 103 and an electric motor 104 are provided above a common base 102.
  • the fluid led from the suction pipe 105 passes through the suction-side gate valve 106 and the short pipe 107, and is drawn into the pump 103 from the pump suction port 103a, and after being pressurized, It is discharged from the pump outlet 103 b. Spitting The discharged fluid further passes through the check valve 108 and the discharge-side gate valve 109 and is guided to the discharge pipe 110.
  • the power supplied from the control panel 1 13 is guided from the input side cable 1 14 which is the input means of the adjusting device 1 11 to the frequency converter housed in the adjusting device 1 1 1 and the frequency is converted. .
  • the power whose frequency has been converted is supplied to the electric motor 104 from the output-side cable 115 serving as the output means of the adjusting device 111.
  • the heat radiating means 112 constitutes a water cooling jacket made of stainless steel, and is fixed to the adjusting device 111 by bolts (not shown), and at the same time, an L-shaped mounting bracket 111 is formed. 6 fastens the flange to the short tube 107 together.
  • the discharge side fluid of the pump is guided from the small pipe 1 17 to the radiating means 1 1 2, passes through the small pipe 1 1 8 and is bypassed to the suction side of the pump.
  • the heat loss due to the frequency conversion is radiated to the pump handling fluid by the heat radiating means 112 and the small pipes 117, 118.
  • a heat insulation treatment as shown by a broken line 1 19 in FIG. 15 is performed ; this is performed so as to prevent heat from transferring from the pipe surface to the atmosphere in a cold water circulation application or the like.
  • this mode it is difficult to adopt the first mode of FIG. 14, and this mode is effective.
  • FIGS. 16A and 16B are views showing details of the adjusting device shown in FIG. 14.
  • FIG. 16A is a partially sectional front view
  • FIG. 16B is a side view.
  • the heat radiating means 112 is fixed to the short pipe 107 with U bolts 120.
  • the input side cable 114 and the output side cable 115 ensure airtightness between the adjusting device 111 and the outside air, for example, in the same manner as the underwater cable used in a submersible motor pump.
  • the O-ring indicated by 1 2 1 The device was designed to prevent outside air from entering the device from the contact surface with the adjusting device.
  • the frequency converter body 48 is housed in a case composed of a base 46 and a cover 47.
  • the base 46 and the cover 47 are fixed by bolts (not shown) via a seal member 58 between them, thereby maintaining airtightness with the outside air.
  • the frequency converter body 48 is fixed to the base 46 with high adhesion, and transfers the heat generated to the base 46.
  • the base 46, the heat radiating means 112, the heat radiating means 112, and the short pipe 107 are also fixed with high adhesion.
  • the heat generated by the frequency converter is appropriately dissipated to the fluid being handled, eliminating the need for an air-cooling fan used in general-purpose inverters. In other words, there is no fear of cooling failure due to fan failure.
  • the base 46 and the heat radiating means 112 are fastened by bolts 55. Further, as described above, since the inside of the case is isolated from the outside air, the frequency converter is unlikely to cause insulation deterioration due to wind, rain, and dew.
  • FIGS. 18A and 18B are views showing details of the apparatus shown in FIG. 15, FIG. 18A is a partially sectional front view, and FIG. 18B is a plan view.
  • the heat dissipating means 1 and 12 are made of a stainless steel water-cooled jacket, and have inlets and outlets for the fluid to be handled.
  • the input side cable, output side cable, and O-ring 122 have the same configuration as the example shown in FIG.
  • the frequency converter body 48 is housed in a case including a base 46 and a cover 47.
  • a base (not shown) is provided between the base 46 and the cover 47 via a sealing member 58. It is fixed by the air and keeps airtight with the outside air.
  • the frequency converter body 48 is fixed to the base 46 with high adhesion, and transfers the heat generated to the base 46.
  • the base 46 and the heat radiating means 112 are also fixed with high adhesion.
  • the heat generated by the frequency converter is suitably radiated to the fluid to be handled, so that an air-cooled fan used for a general-purpose inverter is unnecessary.
  • Ribs 1 2 3 have three roles. One of them is to improve the strength and rigidity so that the water-cooled jacket is not deformed by the pressure of the fluid to be handled. The other is to serve as a flow guide device for securing the residence time of the intake fluid in the jacket. Still another function is to improve the heat radiation effect by increasing the contact area with the intake fluid. According to this aspect, the apparatus can be easily and effectively cooled even if the periphery of the pipe is insulated as described above.
  • FIGS. 20A and 20B The basic configuration in the third embodiment is similar to the first and second embodiments as shown in FIG. 2OA. However, in the third mode, an air-cooled adjusting device 1 1 1 1 utilizing an air flow accompanying rotation of a power ring 1 2 6 connecting a pump 10 3 and a motor 10 4 is formed.
  • a coupling guard for preventing accidents is provided around the coupling 126 as shown in FIG. 20B (the arrow XX in FIG. 20A).
  • the coupling guard is provided.
  • Nggad is used as heat dissipation means.
  • the coupling guard (radiating means) 112 is made of an aluminum alloy, and a plurality of air cooling ribs (fins) 128 are provided in order to improve the air cooling effect by the above-mentioned air flow.
  • the structure around the case is the first and second Since it is the same as the embodiment described above, it can withstand outdoor wind and rain.
  • FIGS. 21A and 21B show another embodiment of the apparatus main body shown in FIGS. 14 to 20.
  • FIG. 21A is a front view
  • FIG. 21B is a side view. To put it simply, this embodiment is different only in that the output side cable 115 is provided on the base 46.
  • the structure is simpler.
  • the device of this embodiment can be applied to a water-cooled jacket type or an air-cooled type.
  • the screw-type cap indicated by reference numeral 124 is connected to the outside air through an O-ring (not shown). This is to ensure airtightness.
  • Output frequency adjusting means is provided in the cap. For example, it is a rotary step-type switch, and the rotation speed of the fluid machine can be adjusted appropriately.
  • a controller By incorporating the performance adjusting device (hereinafter referred to as a controller) of the fluid machine shown in FIGS. 14 to 21B into the system of the present invention, it is possible to grasp wasteful energy with higher accuracy.
  • This controller can set the output frequency in 8 steps, in 5% steps. This step is based on the processing means described above. Since it matches the speed ratio, the actual power consumption can be verified while the system is running. Further, in the above-described processing means, the loss of the inverter was ignored. However, if the inverter is actually driven, accurate power consumption can be calculated as measured data.
  • this controller is extremely effective not only as a means for grasping wasted energy but also as a means for eliminating the grasped wasted energy.
  • the reason for this is that the pump can be used outdoors where it is installed. There is no need to house it in the control panel, so special remodeling costs * No construction costs are required. In other words, when the controller is brought to the site and the return on investment is good, the controller can be mounted as it is.
  • the actual head can be accurately grasped. That is, as shown in Fig. 22, the rotational speed of the pump was changed, and the operating pressure (head) when the valve (gate valve) was opened at each rotational speed and the operating pressure when the valve was shut off were compared. The point at which the difference disappears indicates the actual head.
  • a recording medium storing a program for causing a computer to function is, for example, a notebook personal computer. It is integrated and can be easily brought to the point of use of the pump.
  • FIG. 23 is a schematic diagram showing an example of equipment brought to the operation site of the fluid machine to be diagnosed.
  • the above-mentioned equipment is a personal computer PC including an LCD constituting a part of the main control unit 1 (including the control unit 3 and the arithmetic unit 4), the main storage unit 2, the input unit 5, and the output unit 6 shown in FIG. And a floppy disk (FD) or CD-ROM as a recording medium on which the above program is recorded, and a printer PR constituting a part of the output device 6 shown in FIG.
  • the above-mentioned equipment is composed of a compound meter C PG attached to the suction side of a fluid machine such as a pump, a pressure gauge P c attached to the discharge side, and a power meter P C that measures the power consumption of the motor driving the fluid machine. Contains w.
  • controller performance adjusting device
  • the application of the present invention generally results in a decrease in the rotational speed of the fluid machine, so that an effect of extending the life of the bearing, the mechanical seal, and the like is expected.
  • a so-called “energy-saving diagnosis” can be performed without stopping the pump or changing the opening degree of the valve, that is, without affecting the user's equipment. In other words, it can be implemented during equipment operation (weekdays, not holidays).
  • fluid mechanical characteristic specifying method according to the present invention will be described using a centrifugal pump as an example.
  • the following fluid mechanical characteristic specifying method shows an example in which the first and second specifying means in the embodiment shown in FIGS. 1 to 13 are further embodied.
  • centrifugal pump In general, a centrifugal pump is designed for a model corresponding to the diameter, the motor output, and the number of revolutions.
  • the water volume range is determined by the diameter and the rated motor speed, and the head is generally determined by the motor output. Therefore, the centrifugal pump Specific speed of pump based on bore, impeller stage number, motor output and rotation speed
  • N s can be assumed.
  • the specific speed (N s) is a number used in the pump design stage and is defined by the following equation.
  • N is the number of rotations
  • Q is the flow rate
  • H is the lift of one stage of the impeller.
  • Pump characteristics such as flow-head characteristics and flow-axis power characteristics differ depending on the specific speed.
  • the pump efficiency also varies depending on the specific speed.
  • the characteristics of the pump can be summarized as the ⁇ dimensional dimensionless pump characteristics> shown in Fig. 24 with respect to the specific speed, and the pump efficiency is shown in Fig. 25.
  • Speed-pump efficiency characteristics> In Fig. 24, the horizontal axis shows dimensionless flow (Q), and the vertical axis shows dimensionless head (H) and dimensionless shaft power (KW).
  • FIG. 24 shows the characteristics of the pump when the specific speed (N s) is 560, 400, 280,..., 50. In Fig. 25, the horizontal axis shows the specific speed (N s), and the vertical axis shows the pump efficiency ⁇ (%).
  • FIGS. 24 and 25 are stored in a database in advance.
  • the pump type information including the bore ( ⁇ ) and the number of stages (STG), the motor information including the rated output (P.) and the rated speed (N), Information of measurement data including the head (H) and power consumption (P i) during operation is input to the input device 5 shown in FIG.
  • Step 1 the pump diameter ( ⁇ ) and the number of stages (STG), and the rated output of the motor
  • step 2 Specify the specific speed (N s ) from (P o) and rated speed (N).
  • Q BEP maximum efficiency flow rate
  • step 3 pump diameter ( ⁇ ) and number of stages (STG) and specific speed
  • ⁇ ⁇ (pump efficiency) is specified from (Ns).
  • ⁇ ⁇ 77 ⁇ - ⁇ . / ⁇ 6 ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ 0 0 ⁇ ⁇ ⁇ 0 ⁇ ⁇
  • ⁇ ⁇ (the highest efficiency head) means the head at the highest efficiency point.
  • ⁇ is the specific weight of the handling liquid.
  • the pump dimensionless characteristics shown in Fig. 24 are used to obtain the broken line in Fig. 26B. Create the temporary pump characteristics as shown by. That is, the specific speed specified in step 1
  • the flow-head characteristic curve corresponding to (Ns) is selected from Fig. 24, and
  • Step 1 By drawing the selected flow-head characteristic curve so that the point of (1.0, 1.0) overlaps with the point of (Q BEP , HBEP) in Fig. 26B, the provisional flow-one head Create a characteristic curve.
  • a flow rate uniaxial power characteristic curve corresponding to the specific speed (Ns) specified in step 1 is selected from Fig. 24, and (1.0, A temporary flow-rate single-shaft power characteristic curve is created by drawing the selected flow-rate single-shaft power characteristic curve so that the point of (1.0)) overlaps with the point of (Q BEP , Po ) in Fig. 26B .
  • Steps 1 to 3 are stored in a database in advance.
  • the temporary pump characteristics are corrected as shown in Fig. 26D by the following steps 1 and 2 to identify the pump characteristics.
  • the dashed line shows the temporary pump characteristics
  • the solid line shows the pump characteristics after collection. That is, in step 1, the head of the temporary pump characteristic is corrected by the ratio of ⁇ .
  • the shaft power of the temporary pump characteristics is corrected by the ratio of ⁇ ⁇ ⁇ ⁇ .
  • ⁇ ⁇ and ⁇ ⁇ are the head and shaft power at the specific operating point identified in Fig. 26C
  • H B and PB are the head and shaft power on the temporary pump characteristic curve at the current flow rate (Q), respectively. is there.
  • the pump is used to correct the tentative characteristics with the head and power consumption during the current operation, the flow rate calculated using the assumed values of the fluid machine efficiency and the motor efficiency, and the head and power consumption during the shutoff operation.
  • the assumption stage of the temporary characteristics, the specification of the pump operating point (flow rate), and the correction stage of the temporary characteristics will be described with reference to FIGS. 27A to 27D. First, as shown in Fig.
  • the pump type information including the bore ( ⁇ ) and the number of stages (STG), the motor information including the rated output (P.) and the rated speed (N), Information on the measurement data including the head (H) and power consumption (P i) during the current operation and the head (Hs) and power consumption (P is) during the shutoff operation are input to the input device 5 shown in FIG. I do.
  • the provisional pump characteristics shown in FIG. 27B are specified by the following steps 1 to 3. That is, in step 1, the specific speed (Ns) is specified from the pump diameter ( ⁇ ) and the number of stages (STG), and the rated output (Po) and the rated speed (N) of the motor. In step 2, specify the Q BEP (maximum efficiency flow rate) from the pump diameter ( ⁇ ), the number of stages (STG), the rated motor speed (N) and the specific speed (Ns). In step 3, the representative point in the X direction is Q BEP, and the representative points in the Y direction are H s (head during shutoff operation) and P is (power consumption during shutoff operation), as shown in Fig. 27B. Create pump characteristics. At this time, the temporary pump characteristics are created using the dimensionless pump characteristics shown in FIG. 24 in the same manner as described in the embodiment shown in FIGS. 26A to 26D. Steps 1 and 2 are databased.
  • Step 1 the rated output (P.) of the motor is 77 M
  • ⁇ 3 ⁇ ⁇ ⁇ ⁇ -P i /0.163 3 y
  • the temporary pump characteristics are corrected as shown in Fig. 27D by the following steps 1 and 2 to specify the pump characteristics.
  • the dashed line shows the temporary pump characteristics
  • the solid line shows the pump characteristics after collection. That is, in step 1, the flow rate of the temporary pump characteristic is corrected by the ratio of QZQB.
  • the scan Tetsupu 2 shaft power curve (0, P is. 77 M ), is corrected to approximate curve passing through the (Q, P i ⁇ 77 M ).
  • the tentative characteristics are calculated based on the head and power consumption at the current operation, the flow rate calculated using the assumed values of the fluid mechanical efficiency and the motor efficiency, and the head and power consumption at the time of the valve fully open operation.
  • the assumption stage of the pump temporary characteristics, the specification of the pump operating point (flow rate), and the correction stage of the temporary characteristics will be described with reference to FIGS. 28A to 28D.
  • Fig. 28A information on the pump type including the bore ( ⁇ ) and the number of stages (STG), and information on the motor including the rated output (P.) and the rated speed (N),
  • the input device shown in Fig. 1 shows information on measurement data including the head (H) and power consumption (P i) during the current operation, and the head (Hv) and power consumption (P i V) during the valve fully open operation.
  • the provisional pump characteristics shown in FIG. 28B are created by the following steps 1 to 5. That is, the pump diameter and the number of stages (STG) in step 1 and the rated output of the motor
  • step 2 specify the Q BEP (maximum efficiency flow rate) from the pump diameter ( ⁇ ) and the number of stages (STG), the rated motor speed (N), and the specific speed (N s ).
  • step 3 pump diameter ( ⁇ ) and number of stages (STG) and specific speed
  • ⁇ ⁇ (pump efficiency) is specified from (Ns).
  • ⁇ ⁇ 77 p ⁇ p. ZO. 1 6 3 ⁇ y ⁇
  • Q BEP is used to calculate H BEP (maximum efficiency head).
  • step 5 Based on the specific speed and the representative points ((Q BEP , H BEP) and (Q BEP , P o)) specified in step 5, create temporary pump characteristics as shown by the broken line in Fig. 28B. At this time, a temporary pump characteristic is created using the dimensionless pump characteristic shown in FIG. 24 in the same manner as described in the embodiment shown in FIGS. 26A to 26D.
  • Steps 1 to 3 are stored in a database in advance.
  • Step 1 specify the flow rate shown in Fig. 28C by the following steps 1-2. In other words, in Step 1, ⁇ ⁇ from the rated output (P.) of the motor
  • the temporary pump characteristics are corrected as shown in Fig. 28D by the following steps 1 to 5 to specify the pump characteristics.
  • the broken line shows the provisional pump characteristics
  • the solid line shows the corrected pump characteristics. That is, in step 1, the head of the temporary pump characteristic is corrected by the ratio of ⁇ .
  • the shaft power of the temporary pump characteristics is corrected by the ratio of ⁇ ⁇ ⁇ ⁇ .
  • HA and P are the head and shaft power at the specific operating point specified in Fig. 28C
  • HB and PB are the head and shaft power on the temporary pump characteristic curve at the current flow rate (Q), respectively. Identifying the lift definitive when the valve fully open operation (Hv) of the valve fully open when the flow rate (Q v) in step 3.
  • Step 4 the shaft power (P i V ⁇ 77 M ) at the time of Qv is specified. Go to step 5 Then, the shaft power curve is corrected to an approximate curve passing through (Q, P i ⁇ r? M ) and (Q v, Piv ⁇ 7] M ).
  • Fig. 29A information on the pump type including the bore ( ⁇ ) and the number of stages (STG), and information on the motor including the rated output (P.) and the rated speed (N), Head (H) and power consumption (P i) during current operation, head (Hs) and power consumption (P is) during shutoff operation, head (Hv) and power consumption (P i V) during valve fully open operation
  • the information of the measurement data including is input to the input device 5 shown in FIG.
  • the provisional pump characteristics shown in FIG. 29B are specified by the following steps 1 to 3. That is, in step 1, the specific speed (Ns) is specified from the pump diameter ( ⁇ ) and the number of stages (STG), and the rated output (Po) and the rated speed (N) of the motor. In step 2, specify the Q BEP (maximum efficiency flow rate) based on the pump diameter ( ⁇ ), the number of stages (STG), the rated motor speed (N) and the specific speed (Ns). In step 3, the representative points in the X direction are Q BEP and the representative points in the Y direction are Hs and Pis, and the temporary pump characteristics are created as shown in Fig. 29B. At this time, the temporary pump characteristics are created using the dimensionless pump characteristics shown in FIG. 24 in the same manner as described in the embodiment shown in FIGS. 26A to 26D. Steps 1 and 2 are stored in a database.
  • Step 1 ⁇ ⁇ ⁇ from the rated output (P.) of the motor
  • the temporary pump characteristics are corrected as shown in Fig. 29D by the following steps 1 and 2 to specify the pump characteristics.
  • the broken line shows the temporary bomb characteristics
  • the solid line shows the pump characteristics after correction. That is, to correct the flow rate of the provisional pump characteristics in a ratio of Q / Q B in step 1.
  • the shaft power curve is corrected to an approximate curve passing through (0, Pis 7) M ), (Q, Pi 77), (Q ⁇ , PiV ⁇ ⁇ ).
  • the operating point (flow rate) is specified from the temporary characteristics and the head during the current operation, and the assumption stage of the pump temporary characteristics and the pump operating point (flow rate) in the case of correcting the temporary characteristics with the current power consumption and identification and The temporary characteristic correction step will be described with reference to FIGS. 30A to 30D.
  • Fig. 3OA information on the pump type including the bore ( ⁇ ) and the number of stages (STG), the first (Ql, HI) and the second (Q2, H2)
  • the input device shown in Fig. 1 shows the information of the motor, including the rated output (P.) and the rated speed (N), and the information of the measured data including the head (H) and power consumption (P i) during the current operation.
  • step 1 First, specify the specific speed (Ns) from the pump diameter ( ⁇ ) and the number of stages (STG), and the rated output (Po) and rated speed (N) of the motor.
  • a head curve passing through (0, Hs') and (Q 2, H 2) is created (shown by a broken line), and (Q MAX , P.
  • step 4 To create an axial power curve (indicated by the dashed line). At this time, temporary pump characteristics are created using the dimensionless characteristics of the pump shown in Fig.24.
  • step 4 using (Q 2, H 2) as the origin, the head is corrected by the ratio of ⁇ ⁇ (HI-H 2) to create the head curve shown by the solid line.
  • step 5 a shaft power curve indicated by a two-dot chain line is created by applying a head curve correction value with (0, 0) as the origin to the shaft power curve and correcting it.
  • Step 1 is a database.
  • Step 1 the flow rate shown in FIG. 30C is specified by the following steps 1 and 2. That is, in step 1, ⁇ ⁇ (motor efficiency) is specified from the rated output (P.) of the motor. In Step 2, the current operating flow rate (Q) is specified from the head ( ⁇ ) during the current operation. The P i ⁇ 77 M calculation child and to'm Ri status quo axis power - to identify the (P i ⁇ ⁇ ). Step 1 is a database.
  • the temporary pump characteristics are corrected as shown in FIG. 30D by the following steps to specify the pump characteristics. That is, the shaft power curve shown by the solid line is created by correcting the shaft power curve by the ratio of (P i ⁇ VM) NO PA.
  • the operating point (flow rate) is specified based on the provisional characteristics and the head during the current operation, and the assumption stage of the pump temporary characteristics in the case where the provisional characteristics are corrected based on the current power consumption and the head and power consumption when the valve is fully open.
  • the steps of specifying the pump operating point (flow rate) and correcting the provisional characteristics will be described with reference to FIGS. 31A to 31D. First, as shown in Fig.
  • pump type information including bore ( ⁇ ) and number of stages (STG), first (Ql, HI) and second (Q2, H2) ,
  • step 1 the specific speed (N s ) is specified from the pump diameter ( ⁇ >) and the number of stages (STG), and the rated output ( ⁇ ⁇ ) and rated speed ( ⁇ ) of the motor.
  • N s specific speed
  • STG number of stages
  • ⁇ ⁇ rated output
  • ⁇ rated speed
  • Step 3 Based on the specific velocity (Ns) specified in Step 3, a head curve passing through (0, H S ) and (Q 2, H 2) is created (indicated by a broken line), and (Q MAX , P o ) To create an axial power curve (indicated by the dashed line).
  • temporary pump characteristics are created using the dimensionless characteristics of the pump shown in Fig.24.
  • step 4 with (Q 2, H 2) as the origin, a head curve shown by a solid line is created by correcting the head by the ratio ⁇ ⁇ / (HI-H 2).
  • step 5 a shaft power curve indicated by a two-dot chain line is created by applying a head curve correction value with (0, 0) as the origin to the shaft power curve and correcting it.
  • Step 1 is a database.
  • step 1 the flow rate shown in Fig. 31C is determined by the following steps 1 and 2. That is, in step 1, ⁇ ⁇ (motor efficiency) is specified from the rated output (P.) of the motor. In step 2, the current operating flow rate (Q) is specified from the head ( ⁇ ) during the current operation. Also, the current shaft power (P i-VM) is specified by calculating P i ⁇ ⁇ ⁇ . Step 1 is the data It is based.
  • step 1 the temporary pump characteristics are corrected as shown in Fig. 31D by the following steps 1 to 3 to identify the pump characteristics.
  • Step 2 specify the flow rate ( Qv ) when the valve is fully open from Hv, and specify the shaft power when the valve is fully open.
  • step 3 the shaft power curve is changed to (Q, ⁇
  • the pump characteristics can be estimated by assuming the pump temporary characteristics, specifying the pump operating point (flow rate), and correcting the temporary characteristics by any of the methods shown in FIGS. 26A to 31D. Therefore, even when pump test data is not available, the characteristic curve as shown in FIG. 6 can be specified, so that the diagnostic system of the present invention can function with relatively high accuracy.
  • the diagnostic systems shown in Figs. 1 to 31A to D show actual measurements of power consumption etc. at the site where the pump is actually operating to make a diagnosis.The diagnostic accuracy was high, but it took time to collect data. Is disadvantageous.
  • the diagnostic system shown in FIGS. 1 to 31A to 31D requires an operation to actually perform the diagnosis at the site by actually operating the pump, so to speak, so-called “main diagnosis”. Therefore, the inventor of the present invention has studied a method of knowing the investment effect or cost effect of installing an inverter by a simple diagnosis that can be performed in advance on a desk before performing the main diagnosis on site.
  • the investment effect or cost effect means the effect of reducing the power consumption obtained by introducing the inverter with respect to the cost associated with the introduction of the inverter.
  • the main diagnosis may be omitted in some cases, and the cost of diagnosis may be reduced.
  • the energy-saving pre-diagnosis system for a fluid machine includes a main control unit 1 that controls the entire system as a whole, and a main storage device 2 connected to the main control unit 1.
  • the main control unit 1 includes a control device 3 and a calculation device 4.
  • the main control unit 1 is connected to an input device 5 composed of a keyboard, a mask and the like, and an output device 6 composed of a printer and a display.
  • the main control unit 1 has a control program such as an operating system, a program defining a diagnostic procedure of a fluid machine, and an internal memory for storing required data.
  • the main storage device 2 is composed of a hard disk, a flexible disk, an optical disk, or the like, and stores data of various pumps currently on the market. However, the pump data can also be input to the input device 5 each time.
  • Figure 32 shows the flow rate-head characteristics and flow-power consumption characteristics of the pump.
  • the horizontal axis represents the flow rate (iZmin), and the vertical axis represents the total head (m) or power consumption (kW). Show.
  • the data of the flow rate-head and the flow rate-power consumption of the motor pump when driven by AC commercial power are generally available in advance in the form of test reports and representative characteristic curves.
  • the curve 8 and ⁇ 8 can be subtracted by an appropriate function.
  • the triangular black portions indicate the input of the planning requirements on the equipment side.
  • the pipe loss is known to be proportional to the square of the flow. Then, by inputting the actual head (that is, the pipe resistance when the flow rate is zero), the pipe resistance curve 3 passing through the plan essentials on the equipment side can be drawn.
  • the present invention is provided with a calculating means for calculating the effect of reducing power consumption when the rotation speed of the fluid machine is reduced by using the frequency converter.
  • the calculation means functions as follows (see Fig. 33).
  • the calculating means sets a certain rotational speed ratio for these points. Now, when the rotational speed ratio was set to 0.9 5, moves to q! XO. 10 5, hi moves h, the X 0.9 5 2.
  • Curve / 3 is the resistance curve on the equipment side (piping side) specified by the method described above. Points indicated by 8 are actual operating points, and points 7 to ⁇ are calculated operating points when the rotation speed is changed.
  • the calculating means sets a certain rotational speed ratio for these points as described above. If the rotation speed ratio is 0.95 , then moves to qi X 0.95, and W l becomes w! To move to the X 0. 9 5 3.
  • FIG. 34 shows an example in which the contents described in FIG. 33 are actually output (printed out) by the output device 6. That is, FIG. 34 is a diagram showing the diagnosis result 10 output by the output device 6, and the upper and lower graphs of FIG. 34 show the flow rate-thickness characteristic curve and the flow rate-power consumption obtained in FIG. 3 shows a characteristic curve.
  • the lowermost table is indicated by using A, and this part is enlarged and shown in Fig. 35.
  • Part A of FIG. 34, that is, FIG. 35 is a table showing estimated values of power consumption reduction.
  • Fig. 34 is a diagram showing the diagnosis result 10 output by the output device 6, and the upper and lower graphs of FIG. 34 show the flow rate-thickness characteristic curve and the flow rate-power consumption obtained in FIG. 3 shows a characteristic curve.
  • the lowermost table is indicated by using A, and this part is enlarged and shown in Fig. 35.
  • Part A of FIG. 34 that is, FIG. 35 is a table showing estimated values of power consumption reduction.
  • the vertical list (items) shows the actual operating flow rate when the commercial power supply is driven, the flow rate was adjusted to the planned flow rate using an inverter, and the flow rate was reduced from the planned flow rate using an inverter. The three conditions for the case are shown.
  • 18% energy savings can be achieved simply by adjusting the flow rate to the planned value, and annual electricity costs of 286,000 yen can be saved.
  • the planned flow rate itself has a margin, for example, if it is possible to reduce the flow rate by 10%, it is possible to achieve 40% energy savings, and the annual electricity costs will be 63,600 yen. Can be saved.
  • the computer functions as a means for calculating the effect of reducing power consumption when the rotational speed of the fluid machine is reduced by using the frequency converter and a processing means for displaying the calculation result, as described above.
  • a recording medium on which a program for causing a program to be recorded is recorded is incorporated in, for example, a personal computer.
  • FIG. 36 is a schematic diagram showing an example of an energy-saving pre-diagnosis system for a fluid machine using a personal computer.
  • the above system includes a personal control unit including an LCD which constitutes a part of the main control unit 1 (including the control unit 3 and the arithmetic unit 4), the main storage unit 2, the input unit 5, and the output unit 6 shown in FIG. It includes a user PC, a floppy disk (FD) or a CD-ROM as a recording medium on which the above-mentioned program is recorded, and a printer PR constituting a part of the output device 6 shown in FIG.
  • a personal control unit including an LCD which constitutes a part of the main control unit 1 (including the control unit 3 and the arithmetic unit 4), the main storage unit 2, the input unit 5, and the output unit 6 shown in FIG.
  • It includes a user PC, a floppy disk (FD) or a CD-ROM as a recording medium on which the above-mentioned program is recorded, and a printer
  • Fig. 37 shows an example of application to a motor (three-phase induction motor) driven centrifugal pump.
  • the inside of the outermost square line 10 is the display of, for example, a force tag page.
  • this plane (display object) 11 includes the following curve 12 showing the QH characteristic and information 14 and 15 relating to power consumption.
  • Q-H characteristic curve 12 a curve indicating the Q-H characteristic (Q-H characteristic curve) 12 with the discharge amount on the horizontal axis and the total head on the vertical axis is shown for each frequency applied to the motor.
  • Q-H characteristic curve 12 nine lines are described, and the operating frequency 13 of the motor (pump) is indicated by a number near each curve 12. All of these Q—H characteristic curves 12 may be actually measured data, or may be displayed as calculated values based on the following relational expression (1).
  • the power consumption (power rate) is the operating point, that is, Although it depends on the discharge rate, in this example, the power consumption (power rate) at the discharge rate at the maximum load (however, within the range of the pump selection when driving commercial power) is used as a representative value.
  • the example shown on the side of the characteristic curve 12 is shown.
  • the approximate power consumption at the maximum load point discharge rate when operating with a commercial power supply of 50 Hz is 10.5 kw, and based on this, the operation time is 8400 h / year, Electricity rate 13 yen
  • the approximate annual electricity rate calculated by kwh is .1,150,000 yen.
  • using an inverter for example, when operating at a frequency of 45 Hz, the approximate power consumption is reduced by 2.46 kW compared to when operating with the commercial power supply at 50 Hz. The fee indicates a reduction of 269,000 yen.
  • the price 16 of the inverter is described at the same time as 498, 000 yen in this example.
  • the operation time was 1.85 years (48 9, 00 00/26 It can be seen that the investment (or cost) of the inverter alone can be recovered from 9, 000).
  • the operating hours and power charges (kwh unit price) differ depending on each site and region, and that investment (or cost) requires the installation cost of the inverter.
  • the selection range 17 of the pump when the commercial power supply is driven is surrounded by a dashed line, so that it is possible to replace the pump with a one-class small capacity pump.
  • the possibility is being determined.
  • the same display as described above is also provided on a flat surface that constitutes a display object such as the paper surface of a small-capacity pump with a small capacity.
  • the price of the pump is also displayed on the flat surface (displayed item) 1 1, it will be easy to compare the investment return on replacing the pump with a smaller one-class capacity and adding an inverter. .
  • the plane (display object) 11 describes a condition 18 for calculating information relating to power consumption.
  • the operation time is 8400 h Z year
  • the electricity rate 1 It is stated as 3 yen kwh.
  • a simple multiplication / division calculation may be performed in consideration of the difference.
  • Fig. 38 shows the plane of Fig. 37 (indicated object) 11 as a double circle for an example of a pump essential for emergency only 19, and a double circle for an example of a pump essential for daily use 20. It is shown by.
  • a pump with a capacity of one class is enough for most operating conditions (requirements), but the pump is selected in consideration of emergency requirements.
  • the essential operating time is 600,000 hours, and that the electricity rate is 20 yen wh.
  • the operating frequency may be 40 Hz, the power consumption can be reduced by 4.86 kw from FIGS. 37 and 38 as compared with the case where no inverter is used.
  • the investment can be recovered in about one year even if the installation cost of the inverter is considered. As described above, according to the present invention, it is possible to grasp the investment return on introducing the inverter in a very short time.
  • FIG. 39 shows a second embodiment of a method for displaying characteristics of a fluid machine and a display object according to the present invention, in which information on power consumption is described in further detail.
  • the approximate annual power rate 15 that is information about power is described in the vicinity of the Q-H characteristic curve 12, and at the same time, the relationship between the power consumption at each frequency applied to the motor and the discharge rate is shown.
  • the curve (power consumption curve) 21 is added separately, and the reduction rate (%) 22 and the approximate power consumption 14 similar to the first embodiment are numerically described in the vicinity of the curve 21. is there.
  • the power consumption curve 21 is read to realize this. it can.
  • FIG. 40 shows a third embodiment of a method for displaying characteristics of a fluid machine and a display object according to the present invention, which includes the QH characteristic curve 12, the rotation speed (frequency), and the discharge rate.
  • a plurality of equal power consumption curves 23 for each power consumption, which are almost determined by the amount of power, are displayed on the same coordinate system.
  • the constant power consumption curve 23 is indicated by a broken line, and the annual power rate 24 is indicated by a number near the curve 23.
  • the hardware configuration of the calculation and drawing system is the same as the hardware configuration shown in FIG.
  • the operation / drawing system includes a main control unit 1 that controls the entire system in a comprehensive manner, and a main storage device 2 connected to the main control unit 1.
  • the main control unit 1 includes a control device 3 and a calculation device 4.
  • the main control unit 1 is connected to an input device 5 composed of a keyboard, a mouse and the like, and an output device 6 composed of a printer and a display.
  • thick arrows indicate the flow of data and programs
  • thin arrows indicate the flow of control signals.
  • the main control unit 1 has a control program such as an operating system, a program defining a drawing procedure of a display object, and an internal memory for storing required data. The calculation process and the drawing process for creation are realized.
  • the main storage device 2 is composed of a hard disk / flexible disk, an optical disk, or the like.
  • FIG. 41 is a schematic processing flowchart showing an outline of a processing port in the computing and drawing system shown in FIG.
  • step 1 data of flow-head characteristics and flow-power consumption characteristics at a certain rotation speed of a fluid machine with a motor when driven by an AC commercial power supply is input to the input device 5.
  • the data may be stored in the main storage device 2 in advance.
  • step 2 the rotation speed differs from the rotation speed entered in step 1.
  • the flow rate characteristic and flow rate power consumption characteristic at a plurality of rotation speeds are obtained by calculation.
  • the calculation is performed according to the relational expression (1).
  • measurement data of each rotation speed may be input instead of the calculation.
  • step 3 the operating time of the fluid machine and the power rate per unit power consumption are input.
  • Step 4 the flow rate-head characteristics at different rotation speeds are displayed by a plurality of curves, and information relating to power consumption is displayed on the output device 6 on the same plane.
  • the output device 6 is composed of a display such as a printer or an LCD as described above.
  • the information related to the power consumption includes various types of information shown in FIGS. 37 to 40.
  • the operation / drawing system using a personal computer is the same as the configuration shown in FIG. As shown in FIG. 36, the above system comprises a part of the main control unit 1 (including the control unit 3 and the arithmetic unit 4), the main storage unit 2, the input unit 5, and the output unit 6 shown in FIG.
  • a personal computer including an LCD, a floppy disk (FD) or a CD-ROM as a recording medium on which the above program is recorded, and a printer constituting a part of the output device 6 shown in FIG. Including PR.
  • the surface for displaying the characteristics of the fluid machine is described as a plane, but may be a curved surface as long as it is a continuous surface.
  • the surface to be displayed is not limited to paper such as a catalog, but may be a display such as an LCD (liquid crystal).
  • the user can obtain an expected energy saving effect without performing a complicated calculation.
  • the payback period of the initial investment can be easily grasped. Therefore, the inverter for fluid machinery It stimulates the demand for inverter-mounted pumps, which has recently become popular, and has the effect of penetrating energy savings into the market.
  • the present invention is a system for grasping wasteful energy consumed around a fluid machine, and is applicable to equipment using a chilled / hot water circulation pump and the like, and equipment using a water supply pump and the like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)

Abstract

L'invention concerne un système de diagnostic destiné à un mécanisme à fluide capable de trouver un excès de consommation d'énergie autour du mécanisme à fluide. Ce système comprend un premier moyen d'identification permettant d'identifier les caractéristiques du mécanisme à fluide représentées par une caractéristique débit-levage par la réception d'informations spécifiées sur le mécanisme à fluide à diagnostiquer. Ce système comprend un deuxième moyen d'identification permettant d'identifier le débit d'exploitation ou la pression d'exploitation du mécanisme à fluide selon la relation existant entre les caractéristiques identifiées et une pression d'exploitation ou un débit d'exploitation mesurés du mécanisme à fluide par l'exploitation du mécanisme à fluide à diagnostiquer et par la réception des résultats mesurés de la pression d'exploitation (levage), du débit d'exploitation, de la consommation d'énergie, ou du courant électrique d'exploitation du mécanisme à fluide en fonctionnement. Ce système comprend enfin un moyen de calcul permettant de calculer les variations d'un débit d'exploitation, d'une pression d'exploitation, ou de la consommation d'énergie lorsque la vitesse de rotation du mécanisme à fluide à diagnostiquer est modifiée et d'afficher les résultats calculés.
PCT/JP1999/001661 1998-04-03 1999-03-31 Systeme de diagnostic destine a un mecanisme a fluide WO1999051883A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU30537/99A AU3053799A (en) 1998-04-03 1999-03-31 Diagnosing system for fluid machinery
JP2000542580A JP3343245B2 (ja) 1998-04-03 1999-03-31 流体機械の診断システム
EP99912058A EP1072795A4 (fr) 1998-04-03 1999-03-31 Systeme de diagnostic destine a un mecanisme a fluide

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP10858898 1998-04-03
JP10/108588 1998-04-03
JP10/178120 1998-06-10
JP17812098 1998-06-10
JP10/279189 1998-09-30
JP27918998 1998-09-30
JP10/310575 1998-10-30
JP31057598 1998-10-30

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WO1999051883A1 true WO1999051883A1 (fr) 1999-10-14

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EP (1) EP1072795A4 (fr)
JP (1) JP3343245B2 (fr)
CN (1) CN1128930C (fr)
AU (1) AU3053799A (fr)
WO (1) WO1999051883A1 (fr)

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JP2002054579A (ja) * 2000-08-16 2002-02-20 Kobe Steel Ltd 圧縮機システムの省エネルギー度診断方法
JP2018004097A (ja) * 2016-06-27 2018-01-11 荏原冷熱システム株式会社 熱源システム及びその制御方法
WO2023063105A1 (fr) * 2021-10-14 2023-04-20 株式会社荏原製作所 Système de machine fluidique, dispositif et procédé de traitement d'informations
WO2023243193A1 (fr) * 2022-06-13 2023-12-21 株式会社荏原製作所 Procédé d'aide au fonctionnement de pompe et dispositif d'aide au fonctionnement de pompe

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EP2039939B2 (fr) 2007-09-20 2020-11-18 Grundfos Management A/S Procédé de surveillance d'un dispositif de transformation d'énergie
PL2258949T3 (pl) * 2009-06-02 2017-08-31 Grundfos Management A/S Sposób ustalania wartości charakterystycznych, zwłaszcza wartości, zwłaszcza parametrów, zintegrowanego z instalacją, napędzanego silnikiem elektrycznym agregatu pompy odśrodkowej
EP2354556A1 (fr) 2010-02-10 2011-08-10 ABB Oy Procédé de contrôle d'une pompe commandée avec un convertisseur de fréquence
PE20130791A1 (es) * 2010-04-07 2013-07-25 Weir Minerals Netherlands Bv Controlador de desplazamiento de fase para un sistema de bombas alternativas
DE102011012211A1 (de) * 2011-02-23 2012-08-23 Wilo Se Leistungsoptimiertes Betreiben einer elektromotorisch angetriebenen Pumpe durch Mitkopplung
JP5747622B2 (ja) 2011-04-11 2015-07-15 富士電機株式会社 給水ポンプ制御装置
US9689396B2 (en) * 2011-11-01 2017-06-27 Regal Beloit America, Inc. Entrapment detection for variable speed pump system using load coefficient
US20130204546A1 (en) * 2012-02-02 2013-08-08 Ghd Pty Ltd. On-line pump efficiency determining system and related method for determining pump efficiency
EP3137956B1 (fr) 2014-04-29 2019-10-16 Metso Flow Control Oy Contrôle des performances d'un système de soupape de pompe
CN104154005B (zh) * 2014-07-08 2016-01-20 扬州大学 基于单位流量耗油量最低的柴油机泵站调速优化运行方法
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CN110454376A (zh) * 2019-08-27 2019-11-15 上海航天动力科技工程有限公司 一种水泵机组节能诊断系统
MX2022001132A (es) 2019-09-25 2022-02-16 Halliburton Energy Services Inc Metodo para calcular el rendimiento de viscosidad de una bomba a partir de sus caracteristicas de rendimiento de agua y nuevo parametro adimensional para controlar y monitorear la viscosidad, el flujo y la presion.
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LU502112B1 (de) 2022-05-18 2023-12-01 Wilo Se Verfahren zur Bestimmung der statischen Förderhöhe

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JP2002054579A (ja) * 2000-08-16 2002-02-20 Kobe Steel Ltd 圧縮機システムの省エネルギー度診断方法
JP2018004097A (ja) * 2016-06-27 2018-01-11 荏原冷熱システム株式会社 熱源システム及びその制御方法
WO2023063105A1 (fr) * 2021-10-14 2023-04-20 株式会社荏原製作所 Système de machine fluidique, dispositif et procédé de traitement d'informations
WO2023243193A1 (fr) * 2022-06-13 2023-12-21 株式会社荏原製作所 Procédé d'aide au fonctionnement de pompe et dispositif d'aide au fonctionnement de pompe

Also Published As

Publication number Publication date
EP1072795A1 (fr) 2001-01-31
CN1303467A (zh) 2001-07-11
JP3343245B2 (ja) 2002-11-11
EP1072795A4 (fr) 2006-10-18
AU3053799A (en) 1999-10-25
CN1128930C (zh) 2003-11-26

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