JP3343245B2 - Fluid machine diagnostic system - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

The present invention relates to a fluid machine diagnostic system,
More specifically, the present invention relates to a system for grasping wasteful energy consumed around a fluid machine, and more particularly to a system for grasping and verifying a minimum necessary power consumption in equipment using a chilled / hot water circulation pump or the like.

[0002] Using an inverter (frequency converter),
2. Description of the Related Art A technique for controlling the rotation speed of a motor pump is known.
This method is an extremely effective energy-saving means not only for applications involving severe load fluctuation such as a water supply device, but also for circulation pumps and the like.

[0003] General-purpose pumps are not essential criteria. That is, instead of manufacturing a pump in accordance with the essentials (flow rate and head), a pump that exceeds the essentials is selected from the stock and used. In addition, in general, the plan requirements are calculated at the maximum flow rate with an allowance for the flow rate, and the pipe loss is also expected to have an allowance and aging. Therefore, the actual operation involves valve adjustment for suppressing an excessive flow rate, and is wasteful. In other words, even if the pump is selected according to the calculation formula, a large or small waste occurs.

[0004] The decisive factor in energy saving is that the operation of the pump is matched to the essentials of "true" (the minimum necessary flow rate and head, which can be found only after operation at the site), and efficient operation without waste. is there. For example, in the case where there is too much capacity in the pump capacity when the pump is operated on site, it is possible to save energy by the following method. Replace the pump with a smaller one-class capacity. Process the outer diameter of the impeller to reduce the performance of the pump to an appropriate value. However, these methods are expensive and
In an emergency, it is difficult to improve (restore) the performance. On the other hand, the inverter can easily and reversibly adjust the pump performance, so that drastic energy saving operation can be realized each time.

However, in order to save energy by adding an inverter to the existing pump equipment, there are the following methods, each of which has advantages and disadvantages. Method of inverter control of existing motor pump (Advantage) The motor pump itself does not need to be changed. (Disadvantages) The surroundings of the pump are likely to be humid places, and are not suitable for installation of general inverters. Therefore, it is desirable that the inverter be built in the control panel. Therefore, in addition to the inverter, the control panel needs to be modified or newly manufactured. Method of replacing existing motor pump with inverter-mounted pump (Advantage) Modification of control panel is virtually unnecessary. (Disadvantages) The pump needs to be replaced entirely. Therefore, it is disadvantageous in terms of cost to replace an existing pump that has not reached its useful life. Method of replacing only the motor of the existing motor pump with a motor equipped with an inverter (Advantage) Only the motor needs to be replaced. However, it is necessary to substantially disassemble and reassemble the pump part except for the pump directly connected to the coupling. Modification of the control panel is substantially unnecessary. (Disadvantages) If you replace a motor that has not reached the end of its useful life,
It is disadvantageous in cost. Therefore, it is necessary to select an effective method according to each site condition. What is more problematic is that a method for estimating the amount of energy saving that can be realized by an inverter has not been generalized. That is, there is no method for grasping the essential points of “true” and grasping / verifying the difference from the actual operating point when the inverter is not used. For this reason, although it is known that the inverter contributes to energy saving, it has not been specifically grasped how much energy is saved. As a result, for example, it was not possible to estimate the return on investment when replacing the pump with an inverter-mounted pump, and this was a factor that prevented energy saving from penetrating the market.

As shown in FIG. 42, a flow rate-pressure characteristic (QH characteristic) of a centrifugal pump has a horizontal axis representing a flow rate (discharge amount) and a vertical axis representing a total head (pressure). It is indicated by a curve, and the pump shaft power (output), pump efficiency, pump suction performance (requirement (Requ
ired) NPSH) and current value (in the case of a motor pump).

As described above, a technique for controlling the rotation speed of a motor pump using a device for changing the rotation speed of a fluid machine represented by, for example, an inverter (frequency converter) is known. ing. This method is an extremely effective energy-saving means not only for applications involving severe load fluctuation such as a water supply device, but also for circulation pumps and the like.

As described above, general-purpose pumps are not based on essential requirements, that is, pumps that exceed planned requirements from stock items are not manufactured according to the requirements (flow rate / head). In most cases, the most important factor in “energy saving” is the essential point of “true” (the minimum necessary flow and
The operation point of the pump coincides with the head, and “efficient operation” without waste is performed. Therefore, an extremely large energy saving effect can be obtained by decelerating the pump by the inverter.

On the other hand, there has been proposed a pump in which an inverter is mounted in advance so that the frequency applied to the pump via an adjustment knob can be controlled stepwise. In this type of pump, the QH characteristics are represented by the flow rate (discharge rate) when the frequency (rotation speed) is changed for each adjustment knob number as shown in FIGS. 43A and 43B. The display has been performed using a plurality of curves indicating the relationship between the total head (pressure). FIG. 43A is a partially enlarged view,
FIG. 43B shows an overall view.

However, in the prior art in which the characteristics are displayed as shown in FIG. 42, even if an attempt is made to save energy by using an inverter, the characteristics are not displayed when the rotational speed is changed. At the same time, the relationship between the discharge volume and the total head is not known at all, and at the same time, information on power consumption is not described. Therefore, it is necessary to perform cumbersome simulations each time to grasp the return on investment of the inverter. was there.

On the other hand, in the prior art in which the characteristics are displayed as shown in FIGS. 43A and 43B, although the output for each rotation speed (each adjustment knob number) is described, the power consumption is not considered. Since no information is described, it is necessary to separately obtain and simulate data such as motor efficiency and inverter efficiency in order to understand how much energy is saved when the rotational speed is changed. Was. In other words, in the conventional technology,
When implementing energy saving measures for a pump using an inverter, etc., it takes time and effort to calculate the return on investment, and in the case of an inverter-mounted pump, the energy saving effect cannot be expressed widely and generally. Was the current situation.

The present invention has been made in view of the above problems, and provides a diagnostic system that can estimate the amount of energy saved by rotation speed adjustment using an inverter (frequency converter) before performing rotation speed adjustment. The first
The purpose of. That is, a first object of the present invention is to provide a fluid machine diagnostic system capable of grasping useless energy consumed around a fluid machine.

A second object of the present invention is to provide an energy-saving pre-diagnosis system for a fluid machine which can easily estimate the energy-saving amount brought by the rotation speed adjustment using an inverter (frequency converter) or the like. Aim.

Further, according to the present invention, for example, an inverter is introduced (extended) by describing information on power consumption when the number of revolutions is changed in a characteristic display of a fluid machine such as a pump.
It is a third object of the present invention to provide a method for displaying the characteristics of a fluid machine and a display object capable of easily grasping the return on investment at the time of performing the operation, thereby enabling energy saving to penetrate the market.

In order to achieve the first object, the diagnostic system for a fluid machine of the present invention adopts the modes listed in (1) to (4). (1) First specifying means for specifying characteristics of a fluid machine represented by a flow rate-head characteristic by inputting predetermined information of a fluid machine to be diagnosed, and a fluid machine to be diagnosed By operating the operating pressure (head), operating flow rate, power consumption, or operating current value of the fluid machine at the time of operation, the characteristics of the specified fluid machine and the measured fluid machine Second specifying 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, and operating flow rate or operating pressure or consumption when the rotational speed of the fluid machine to be diagnosed is changed And a processing unit for calculating a change in electric power and displaying a calculation result.

(2) By inputting predetermined information of the fluid machine to be diagnosed, a function for specifying the characteristics of the fluid machine typified by the flow rate-head characteristics, and the fluid machine to be diagnosed By operating and inputting the measurement result of the operating pressure (head), operating flow rate, power consumption, or operating current value of the fluid machine at the time of the operation, the characteristics of the specified fluid machine and the measured operating pressure of the fluid machine are measured. Or, a function of specifying the operating flow rate or operating pressure of the fluid machine based on the relationship with the operating flow rate, and calculating the change in the operating flow rate, operating pressure, or power consumption when the rotational speed of the fluid machine to be diagnosed is changed. And a function of displaying a calculation result on a computer-readable recording medium storing a program for causing a computer to realize the function.

(3) Flow rate of fluid machine to be diagnosed
First specifying means for specifying a characteristic represented by a head characteristic, and an actual operating point determined by an operating pressure (head), operating flow rate, power consumption, or operating current value during operation of the fluid machine to be diagnosed Second specifying means for specifying the relationship between the specified characteristics of the fluid machine and the operating pressure or the operating flow rate of the fluid machine, and an operation when the rotation speed of the fluid machine to be diagnosed is changed. Calculate the change of the point,
And a processing means for displaying a calculation result.

(4) Flow rate of fluid machine to be diagnosed
Specifying a characteristic represented by a head characteristic, and specifying the actual operating point determined by the operating pressure (head), operating flow rate, power consumption, or operating current value during operation of the fluid machine to be diagnosed. Specifying the relationship between the characteristics of the fluid machine and the operating pressure or operating flow rate of the fluid machine, and calculating a change in the operating point when the rotational speed of the fluid machine to be diagnosed is changed. And displaying the calculation result.

According to each aspect of the inventions described in the above (1) to (4), the energy saving amount brought by the rotation speed adjustment utilizing an inverter (frequency converter) or the like is
A trial calculation can be made before adjusting the rotation speed.

Each means or step of the present invention is executed by a computer such as a programmed personal computer. The aspect 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).

Further, in order to achieve the above-mentioned first object,
According to another aspect of the present invention, one point of fluid machine characteristics is set as a representative point based on the diameter and the number of impeller stages of the fluid machine, and the rated output and the rated speed of the electric motor that drives the fluid machine. Determining the ratio of the head and the shaft power other than the representative point to the head and the shaft power at, calculating the head and the shaft power at each flow rate, assuming the tentative characteristics of the fluid machine, and at least the head during the current operation. And a step of correcting the provisional characteristic based on the measurement data including power consumption and specifying a characteristic of the fluid machine and an operating point including an operation flow rate. It is.

In order to achieve the above-mentioned second object, data of 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 items (flow rate- Means for inputting pressure), means for inputting or assuming pipeline resistance (actual head) when the flow rate is zero, and reduction of power consumption when the rotational speed of the fluid machine is reduced using a frequency converter An energy-saving pre-diagnosis system for a fluid machine including means for calculating the effect and processing means for displaying the calculation result may be configured.

Also, the flow rate—pressure (head) and flow rate—of a fluid machine with a motor when driven by an AC commercial power supply
By inputting the power consumption data and the planning parameters (flow rate-pressure) on the equipment side and inputting or assuming the pipeline resistance (actual head) when the flow rate is zero, the frequency converter is used to The function of calculating the effect of reducing the power consumption when the rotation speed is reduced and the function of displaying the calculation result may be a computer-readable recording medium storing a program for causing a computer to realize the function.

In order to achieve the above third object,
The modes listed in (1) to (5) can be taken. (1) A flow rate-pressure characteristic of a fluid machine that varies depending on the number of revolutions is displayed by a plurality of curves on the same surface, and information related to power consumption is displayed on the surface. Is the way. According to the present invention, information relating to power consumption can be obtained at a glance at the same time at a glance corresponding to the flow rate-pressure characteristics of a fluid machine that varies depending on the number of revolutions. Easy to understand. (2) A display object displaying the characteristics of the fluid machine using the method for displaying the characteristics of the fluid machine according to (1). Examples of this display include sales materials represented by catalogs and the like. (3) Flow rate-pressure characteristics of a fluid machine that vary depending on the number of revolutions are displayed by a plurality of curves on the same surface of a sales document such as a catalog, and information related to power consumption is displayed on the sales material. It is a fluid machine characterized by displaying simultaneously, or a device for changing the rotation speed of the fluid machine. Thus, when introducing a device that changes the rotation speed of a fluid machine such as a fluid machine or an inverter, it is possible to easily understand the return on investment by looking at these sales materials. (4) Power consumption reading of a fluid machine in which a plurality of curves indicating the flow rate-pressure characteristics of the fluid machine for each rotation speed and a plurality of curves indicating the flow rate-pressure characteristics of the fluid machine for each power consumption are described in the same coordinate system. FIG. (5) Calculation by a computer capable of obtaining the display or the diagram by inputting data of flow rate-pressure characteristics and flow rate-power consumption of a fluid machine with a motor when driven by an AC commercial power supply. A computer-readable recording medium in which an image forming system and a program for realizing the system by a computer are recorded.

An embodiment of a diagnostic system for a fluid machine according to the present invention will be described below with reference to the drawings. The fluid machine diagnosis system includes a first specification unit configured to specify a characteristic of a fluid machine represented by a flow rate-head characteristic by inputting predetermined information of a fluid machine to be diagnosed, and a diagnosis target 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 during operation, the characteristics of the specified fluid machine are measured. Second specifying means for specifying the operating flow rate or operating pressure of the fluid machine according to the relationship with the operating pressure or operating flow rate of the fluid machine, and the operating flow rate when the rotation speed of the fluid machine to be diagnosed is changed or Processing means for calculating a change in operating pressure or power consumption and displaying the calculation result.

FIG. 1 is a hardware configuration diagram of a diagnostic system for a fluid machine according to the present embodiment. In the present embodiment, 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 controls the entire system as a whole, and a main storage device 2 that is connected to the main control unit 1.
And The main control unit 1 includes a control device 3 and an arithmetic device 4. The main controller 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. In FIG. 1, 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 diagnostic procedure for a fluid machine, and an internal memory for storing necessary data.
The 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.

Note that 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.

According to the present invention, for example, 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 diameter of the pump ・ The rated output of the motor (or the nominal output of the pump) ・ The number of poles of the motor ・ The operating frequency of the motor ・ The number of impeller stages Input to the device 5. The first specifying means specifies the flow rate-head characteristic and the flow rate-power consumption characteristic of the pump based on these data. This specification is performed, for example, by selecting data close to the data stored in the main storage device 2. The information (data) input to the input device 5 includes, in addition to the above,
Includes essentials of the nameplate of the pump, the name of the pump, the number of stages of the impeller of the pump, the outer diameter of the impeller of the pump, test data of the pump, and the like.

The specification is displayed using, for example, one solid line, a broken line, and a diagonal line as shown in FIG. FIG. 2 is a diagram showing a flow rate-head characteristic and a flow rate-power consumption characteristic of the pump. The horizontal axis indicates the flow rate (Q), and the vertical axis indicates the head (H) or power consumption (W). As shown in FIG. 2, the flow rate-head characteristic and the flow rate-power consumption characteristic of the pump are specified with a predetermined width by the first specifying means based on the input result. That is, the area of the hatched portion a is specified. The broken line indicates the upper and lower limits of the area of the hatched area a, and the solid line is the center line of the area of the hatched area a. The result specified by the first specifying means is:
The information is displayed on an output device 6 including a display such as an LCD (liquid crystal). The hatched portion a is configured so that its accuracy is corrected by the input data and its 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. Therefore, the area of the hatched portion a can be minimized as shown in FIG. 3B from the state of FIG. 3A.

The accuracy of the result specified by the first specifying means is further corrected by inputting the power consumption of the fluid machine at the actual operating point. That is, by measuring the power consumption of the motor during the actual operation and inputting it to the input device 5, the accuracy is corrected, and the state shown in FIG.
As shown in B, the area of the hatched portion a is corrected so that the hatched portion a includes the actual power consumption value of the motor.

The result specified by the first specifying means is further corrected for accuracy by inputting the operating pressure and power consumption during the actual shutoff operation as shown in FIG. 5B from the state of FIG. 5A. 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 result specified by the first specifying means can be further corrected by inputting pump test data (flow rate-head, flow rate-power consumption) performed before the pump is shipped from the factory. In this case, FIG.
As shown in (1), the characteristics of the pump can be specified with extremely high accuracy. Actually, if the above-mentioned data is input without inputting the test data of the pump, the specification similar to FIG. 6 can be obtained. In this case, 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.

By operating the second specifying means with respect to the pump characteristics specified by the first specifying means, the operating point of the pump in the facility can be specified. At this time, the pump to be diagnosed is operated, and the actual operating pressure (head) or operating flow rate or power consumption is measured.
By inputting to the input device 5, the second specifying means is operated. When inputting the operating pressure Calculate and input the operating pressure by measuring the pump suction pressure and the pump discharge pressure. As a result, the operation flow rate and the power consumption can be specified as shown in FIG. 7 by obtaining the intersection of the flow rate-head characteristic curve and the flow rate-power consumption characteristic curve. When inputting the operating flow rate Measure the operating flow rate using a flow meter and enter it. As a result, the operating pressure (head) and power consumption can be specified as shown in FIG. 8 by obtaining the intersection of the flow rate-head characteristic curve and the flow rate-power consumption characteristic curve. When inputting power consumption Measure and input the power consumption of the motor during operation using a wattmeter. As a result, the operating pressure (head) and the operating flow rate can be specified as shown in FIG. 9 by obtaining 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. In practice, the measurement of the flow rate and the power consumption often requires an expensive measuring instrument or is troublesome. On the other hand, the operating pressure can be easily calculated simply by attaching a compound gauge on the suction side of the pump and a pressure gauge on the discharge side of the pump.

Before operating the processing means, it is convenient to grasp and input the actual head. This is because the resistance curve on the equipment side (piping side) can be calculated as shown in FIG. In FIG. _{10, H 1 -H 0 = K} 1 Q 1 2 ∴K 1 = (H 1 -H 0) / Q 1 2 (H 1 is total head, _{H 0} is actual head, _{Q 1} is the flow rate) That is, If Q ₁ , H ₁ , and H ₀ can be specified, K ₁ can be obtained. Accordingly, the resistance F on the equipment side (piping side) at an arbitrary flow rate Q is F = H ₀ + K ₁ Q ² = H ₀ + (H ₁ −H ₀ ) (Q / Q ₁ ) ² . Note that the actual head is calculated by using the controller described later.
It can also be grasped more accurately. When it is difficult to determine the actual head, as shown in FIG. 11, it is possible to input about three types (models 1, 2, and 3) of the temporary actual head.

The processing means functions as follows. FIG.
In, the curve alpha ₈ flow rate of the pump identified by the first specifying means - a lift characteristic. On curve alpha _8, there are a plurality of points, not shown. The coordinates of that point are (q ₁ , h ₁ ), (q ₂ ,
h ₂ )... The processing means sets a certain rotational speed ratio for these points. Now, when the rotational speed ratio was set to 0.95, _{q 1} moves to _{q 1} × 0.95,
h ₁ is moved to _{h 1} × 0.95 ^2.

That is, (0.95q ₁ , 0.95
^{_{2 h 1), (0.95q 2}} , 0.95 2 h 2) ...... made the point was born, is the connected curve these points the α _7.
Hereinafter, similarly, the rotation speed ratio is set to 0.9, 0.85, 0.8.
A curve of α _{6 to} α ₁ is drawn as 0.

A curve β is a resistance curve on the equipment side (piping side) calculated by the method shown in FIG. The points indicated by are the actual operating points, and the points to are the calculated operating points when the rotation speed is changed. Curve γ ₈ is,
It is a flow rate-power consumption characteristic of the pump specified by the first specifying means. On curve gamma _8, there are a plurality of points, not shown. The coordinates of the point are defined as (q ₁ , w ₁ ), (q ₂ , w ₂ )... According to the flow rate and the power consumption.

The processing means sets a certain rotational speed ratio for these points as described above. If the rotational speed ratio was set to 0.95, _{q 1} moves to _{q 1} × 0.95, _{w 1} is _{w 1} ×
To move to 0.95 ^3. This is based on the premise that the pump efficiency and the motor efficiency do not change even when the rotation speed is changed. In addition, the frequency conversion loss when using an inverter or the like is not considered. By considering these factors in advance, it is possible to calculate the power consumption with higher accuracy.

As described above, (0.95q ₁ , 0.9
5 ³ w ₁ ), (0.95 q ₂ , 0.95 ³ w ₂ )... Points are generated, and a curve connecting these points is γ ₇ . Hereinafter, similarly, the rotational speed ratio is set to 0.9, 0.85, 0.8,.
.. Are plotted as curves γ ₆ to γ ₁ . Curve γ _{8 to} γ ₁
Above, the power consumption corresponding to the operating points is indicated by dots. Now, in FIG. 12, the points indicated by the hatched portions are the design points of the equipment. In other words, this is a calculation point that when a flow rate of 3500 l / min is required, the pipe resistance including the actual head will be 38.5 m. On the contrary,
Is the actual operating point.

The "deviation" between the design point and the actual operating point is:
It is created for the reasons described above (see the section of the prior art).
In this example, the operation is actually performed at a flow rate which is 40% larger than the design point flow rate.

The processing means displays an appropriate number of rotations of the pump with respect to the flow rate at the design point and the power consumption at the number of rotations (operating point). In this example, the point is an appropriate operating point. Table 1 shows the comparison with the actual operating point.

[Table 1] That is, power consumption is reduced by 50%.

In the above example, the design point flow rate was defined as an appropriate operating point. However, the design point flow rate is not always an appropriate operating point. It is more common to determine the design point flow rate a little larger than the actual required flow rate with a margin. In this case, the number of rotations can be further reduced, and the power can be further saved. That is, it is energy saving by operation in the essential condition of "true".

In FIG. 11, when a provisional actual head is set, three curves β shown in FIG. 12 are present. In this case, the conditions are further narrowed down (limited).
In this way, one curve β may be specified and compared with the equipment design point to produce one diagnosis result. Alternatively, three curves β may be compared with the equipment design point to obtain three diagnosis results. You may put out.

FIG. 13 is a schematic processing flowchart showing an outline of the processing flow in the fluid machine diagnostic system shown in FIGS. 1 to 12 and described in detail.

In step 1, information (diameter of a pump, rated output of a motor, etc.) for specifying characteristics of a fluid machine which is actually operating, which is an object to be diagnosed, is input to the input device 5. Next, in 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. Next, in step 3, information (actual head and the like) for specifying the resistance characteristics of the equipment is input to the input device 5. Next, in 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 calculation device 4 and displayed on the output device 6.

As described above, according to the present invention, the amount of wasteful energy consumed around the pump can be grasped without bringing an inverter or the like to the site. Therefore, for example, since the return on investment when an inverter or the like is introduced becomes clear, 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 applicant proposes a performance adjusting device for a fluid machine as one of the most suitable controllers to be combined with the present invention. That is, the 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 saving energy. It is possible to adjust the performance of the pump simply by adding an inverter without any change.

Next, an apparatus for adjusting the performance of a fluid machine will be described. FIG. 14 shows a first embodiment of the mounting work when using the performance adjusting device for a fluid machine according to the present invention. Symbol 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 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, is pressurized, and is discharged from the pump discharge port 103b. The discharged fluid is further supplied to a check valve 108 and a discharge-side gate valve 109.
And is guided to the discharge pipe 110.

A performance adjusting device (hereinafter, referred to as an adjusting device) 111 for a fluid machine is attached to the short pipe 107 via a heat radiating means 112 made of an aluminum alloy having good heat conductivity. In this embodiment, the heat radiating means 112 is fixed to the adjusting device 111 by a bolt (not shown), and is also fixed to the short pipe 107 by a U bolt (not shown). The electric power supplied from the control panel 113 is
From the input side cable 114 which is the input means of the adjusting device 1
The frequency is guided to a frequency converter housed in 11 and converted. The power whose frequency has been converted is supplied from an output side cable 115 which is an output unit of the adjusting device 111 to the electric motor 104.
Supplied to. The frequency conversion in the adjustment device 111 involves loss heat. In this embodiment, the loss heat is radiated to the pump handling fluid via the radiator 112 and the short pipe 107.

FIG. 15 shows a second embodiment of the mounting operation when using the adjusting device according to the present invention. Reference numeral 101 denotes a pump unit, and the pump unit 101 is a common base 1.
02 is provided with a pump 103 and an electric motor 104 provided above. The fluid guided from the suction pipe 105 passes through the suction-side gate valve 106 and the short pipe 107, and flows through the pump suction port 1
03a is sucked into the pump 103 and pressurized,
It is discharged from the pump discharge port 103b. The discharged fluid further passes through a check valve 108 and a discharge-side gate valve 109 and is guided to a discharge pipe 110.

The electric power supplied from the control panel 113 is guided from an input side cable 114 as an input means of the adjusting device 111 to a frequency converter housed in the adjusting device 111, and the frequency is converted. The power whose frequency has been converted is supplied to the electric motor 104 from an output-side cable 115 that is an output unit of the adjustment device 111.

In the embodiment shown in FIG.
Reference numeral 2 denotes a water-cooled jacket made of stainless steel, which is fixed to the adjusting device 111 by bolts (not shown), and is simultaneously fastened and fixed to flange bolts of the short pipe 107 by L-shaped fittings 116. Heat radiating means 112
, The discharge side fluid of the pump is guided from the small pipe 117,
It passes through the small pipe 118 and is bypassed to the suction side of the pump. In this embodiment, the heat loss caused by the frequency conversion
The heat is radiated to the fluid handled by the pump through the small pipes 12 and the small pipes 117 and 118. In this embodiment, a heat insulation process as shown by a broken line 119 in FIG. 15 is performed. This is performed so that heat does not move from the pipe surface to the atmosphere in cold and hot water circulation applications and the like. In this case, 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, and FIG. 16B is a side view. Heat radiating means 112
Are 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 the underwater motor pump. Further, an O-ring denoted by 121 is provided with the heat radiating means 112 and the adjusting device 1.
It is designed to prevent outside air from entering the device from the contact surface with the device 11.

Next, the peripheral structure of the adjusting device 111 will be described with reference to FIG. 17 which is a sectional view taken along the line XVII-XVII in FIG. 16A. The frequency converter body 48 includes a base 46 and a cover 4.
7 are housed. Further, the base 46 and the cover 47 are fixed by bolts (not shown) via a seal member 58 therebetween to maintain airtightness with the outside air. The frequency converter body 48 is fixed to the base 46 with high adhesion,
The generated heat is transmitted to the base 46. Similarly, the base 46 and the heat dissipating means 112 and the heat dissipating means 112 and the short pipe 107 are also fixed with high adhesion. As a result, since the heat generated by the frequency converter is preferably radiated to the handled fluid, an air-cooling fan or the like used for a general-purpose inverter is unnecessary. That is, there is no fear of poor cooling 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 cut off from the outside air, the frequency converter hardly causes insulation deterioration due to wind, rain, and dew.

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 radiating means 112 has a water cooling jacket made of stainless steel, and has an inlet / outlet 122 for a handling fluid. The input cable, the output cable, and the O-ring 121 have the same configuration as the example shown in FIG.

Next, with reference to FIG. 19, which is a cross-sectional view taken along the line XIX-XIX of FIG. The frequency converter main body 48 is housed in a case including a base 46 and a cover 47. Further, the base 46 and the cover 47 are fixed by bolts (not shown) via a seal member 58 therebetween to maintain airtightness with the outside air. The frequency converter main body 48 is fixed to the base 46 with high adhesion, and transfers the generated heat to the base 46.
Similarly, the base 46 and the heat radiating means 112 are fixed with high adhesion. As a result, since the heat generated by the frequency converter is preferably radiated to the handled fluid, an air-cooling fan or the like used for a general-purpose inverter is unnecessary.

The rib 123 has three roles. Part 1
One is to improve the strength and rigidity so that the water cooling jacket is not deformed by the pressure of the handling fluid. Another one
First, it serves as a flow guiding device for securing the residence time of the handled fluid in the jacket. Still another is to increase the contact area with the handled fluid, thereby improving the heat radiation effect. According to this aspect, the apparatus can be easily and effectively cooled even if the periphery of the pipe is insulated as described above.

Next, a third embodiment of the present invention will be described with reference to FIGS. 20A and 20B. The basic configuration in the third mode is the same as in the first and second modes as shown in FIG. 20A. However, the third
In the embodiment, the air-cooling type adjusting device 111 utilizing the airflow accompanying the rotation of the coupling 126 connecting the pump 103 and the motor 104 is formed. Generally coupling 126
20B (see the arrow XX in FIG. 20A), a coupling guard for preventing accidents is provided. In this embodiment, the coupling guard is used as the heat radiation means 112. It is. Here, the coupling guard (radiator) 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-described air flow. Since the structure around the case is the same as in the first and second embodiments, it can withstand outdoor wind and rain.

Next, the embodiment shown in FIGS. 21A and 21B will be described. 21A and 21B show another embodiment of the apparatus main body shown in FIGS.
Is a front view, and FIG. 21B is a side view. In short, this embodiment is different only in that the output side cable 115 is provided on the base 46. Since it is not necessary to attach the output side cable to the heat radiating means, the structure is simpler. Needless to say, the device of this embodiment can be applied to a water-cooled jacket type or an air-cooled type.

In FIG. 16A, FIG. 16B, FIG. 18A, FIG. 21A and FIG. 21B, the screw-type cap indicated by reference numeral 124 secures airtightness with outside air via an O-ring (not shown). Output frequency adjusting means is provided in the cap. For example, it is a rotary step-type switch, and can appropriately adjust the rotation speed of the fluid machine.

Further, in the present invention, there is no component corresponding to a switch for turning on and off the output of the frequency converter, as not described in the drawings. That is, the output is automatically started when power is supplied to the frequency converter. Therefore, there is no restriction on the position when the device is attached to the pipe. For example, even if the fluid machine is installed in a place where the hand cannot reach or a small space so as not to be tampered with by children, the fluid machine starts and stops only by turning on and off the power supply, so that there is no problem.

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 eight steps in steps of 5%. Since this interval matches the rotation speed ratio of the processing means, the actual power consumption can be verified while operating the system. Further, in the above-described processing means, the loss of the inverter has been neglected. 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. This is because the pump can withstand general outdoor use as a place for installing the pump. There is no need to house it in the control panel, so no special remodeling and construction costs are required. That is,
If the controller is brought to the site and the return on investment is good, the controller can be mounted as it is. Further, by using this controller, the actual head can be accurately grasped. That is, as shown in FIG. 22, the rotational speed of the pump is changed, and the operating pressure (head) when the valve (separating valve) is opened at each rotational speed is compared with the operating pressure when the valve is shut off. The point at which disappears indicates the actual head.

[0065]

[Table 2] That is, in the example shown in Table 2, 19 m is the actual head.

As a result, even when the actual head is difficult to grasp (for example, when the piping system is complicated), the actual head can be easily grasped by using the controller of the present invention. By inputting this value to the input device 5 shown in FIG. 1 and causing the processing means to function, the accuracy of the system is further improved.

The first specifying means and the second specifying means
A recording medium on which a program for causing a computer to function (operate) is recorded as a specifying means and a processing means is incorporated in, for example, a notebook personal computer, and can be easily brought to the site where the pump is used.

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 includes a main control unit 1 (including a control device 3 and an arithmetic device 4), a main storage device 2, an input device 5, and an output device 6 shown in FIG.
, A personal computer PC including an LCD, a floppy disk (FD) or a CD-ROM as a recording medium storing the program, and a printer PR, a part of the output device 6 shown in FIG. Includes Moreover, the equipment is coupled meter C _PG attached to the suction side of the fluid machine such as a _pump, pressure gauge P _G attached to the discharge _side, and a power meter P _W for measuring the power consumption of the motor for driving the fluid machine Includes

As described above, according to the present invention, useless energy consumed around the fluid machine can be grasped. According to the present invention, the amount of wasteful energy consumed around the fluid machine can be grasped without bringing an inverter or the like to the site. Therefore, for example, since the return on investment when introducing an inverter etc. becomes clear,
It is easy to penetrate energy saving into the market.

By using the controller (performance adjusting device) of the present invention, it is possible to grasp the amount of useless energy and to eliminate the uselessness. The application of the present invention generally results in a reduction in the rotational speed of the fluid machine, so that an effect of extending the life of a bearing, a mechanical seal, and the like can be expected.

According to the present invention, a so-called “energy saving diagnosis” can be performed without stopping the pump or changing the opening of the valve, that is, without affecting the user's equipment. In other words, it can be implemented during the operation of the equipment (weekdays instead of holidays). Further, even when a more accurate “energy saving diagnosis” is required, appropriate measures can be taken. In this case, it is necessary to temporarily stop the equipment or to collect data in which the opening degree of the valve is changed.

By applying the present invention, appropriate measures such as introduction of a controller or conversion to a "fluid machine with one rank capacity" can be performed according to each situation. Also,
Since the loss on the pipe side (equipment side) can be grasped, for example, energy saving by raising the pipe diameter by one rank can be easily estimated.

Next, a method for specifying fluid mechanical characteristics 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. Generally, a centrifugal pump is designed for a model corresponding to the diameter, the motor output and the number of revolutions, and the water usage range is generally determined by the diameter and the rated motor speed, and the head is generally determined by the motor output. Therefore, it is possible to assume the specific speed (N _s ) of the pump from the diameter of the centrifugal pump, the number of impeller stages, the output of the motor, and the number of revolutions. Here, the specific speed (N _s ) is a number used in the design stage of the pump and is defined by the following equation. N _S = NQ ^1/2 / H ^3/4 Here, N indicates the number of rotations, Q indicates the flow rate, and H indicates the head of one stage of the impeller. Pump characteristics such as flow-head characteristics and flow-shaft power characteristics differ depending on the specific speed. The pump efficiency also varies depending on the specific speed. The characteristics of the pump (flow rate-head, flow rate-shaft power) are shown in FIG.
, And the pump efficiency can be arranged as <specific speed-pump efficiency characteristic> shown in FIG. In FIG. 24, the horizontal axis represents the dimensionless flow rate (Q), and the vertical axis represents the dimensionless head (H).
And dimensionless shaft power (KW). In FIG. 24, the specific speed (N _S ) is 560, 400, 280,.
The characteristics of the pump for 0 are shown. In FIG. 25, the horizontal axis indicates the specific speed (N _S ), and the vertical axis indicates the pump efficiency η (%).

Therefore, if the representative points (dimensional flow, head and shaft power) are determined in FIG. 24, it is possible to assume the entire pump characteristics as temporary characteristics. At the stage where the tentative characteristics of the pump can be assumed, the characteristics of the fluid machine can be determined by identifying the pump operating point (flow rate) and correcting the tentative characteristics to match the measured data (head and power consumption) during the pump operation. Can be identified. 24 and 25 are stored in a database in advance.

Next, the assumption stage of the pump temporary characteristics and the pump operation in the case where the temporary characteristics are corrected by the flow rate calculated using the head and power consumption during the current operation and the assumed values of the fluid machine efficiency and the motor efficiency are described. The steps of specifying the point (flow rate) and correcting the provisional characteristics will be described with reference to FIGS. 26A to 26D.

First, as shown in FIG. 26A, the aperture (φ)
And information on the pump type including the number of stages (STG), information on the motor including the rated output (P ₀ ) and the rated speed (N), the head (H) and the power consumption (Pi) during the current operation.
Is input to the input device 5 shown in FIG.

Next, in the main controller 1 shown in FIG. 1, the temporary pump characteristics shown in FIG. 26B are created by the following steps 1 to 5. That is, in step 1, the specific speed (N _S ) is obtained from the pump diameter (φ) and the number of stages (STG), the rated output (P ₀ ) and the rated rotation speed (N) of the electric motor.
To identify. In step 2, Q _BEP (maximum efficiency flow rate) is specified based on the diameter (φ) and the number of stages (STG) of the pump, the rated speed (N) of the electric motor, and the specific speed (N _S ).
Here, Q _BEP (the highest efficiency flow rate) refers to the flow rate at the highest efficiency point. In step 3, η _{P is obtained} from the pump diameter (φ), the number of stages (STG), and the specific speed (N _S ).
(Pump efficiency). H in step 4
H _BEP (maximum efficiency head) is calculated by the following equation: _BEP = η _P · P ₀ /0.163·γ·Q _BEP here,
H _BEP (highest efficiency head) refers to the head at the highest efficiency point. Γ is the specific weight of the handling liquid. Step 5
The specific speed and the representative point ((Q _BEP , H
Based on ( _BEP ) and (Q _BEP , P ₀ )), a temporary pump characteristic is created as shown by a broken line in FIG. 26B using the pump dimensionless characteristic shown in FIG. That is, a flow rate-head characteristic curve corresponding to the specific speed (N _S ) specified in step 1 is selected from FIG. 24, and the point (1.0, 1.0) in FIG. 24 corresponds to (Q _{BEP in} FIG. 26B). , H _BEP ), a temporary flow rate-head characteristic curve is created by drawing the selected flow rate-head characteristic curve so as to overlap the point. Further, a flow rate-shaft power characteristic curve corresponding to the specific speed (N _S ) specified in step 1 is selected from FIG. 24, and (1.0, 1..
The temporary flow rate-shaft power characteristic curve is created by drawing the selected flow rate-shaft power characteristic curve such that the point ( ₀ ) overlaps the point (Q _BEP , P ₀ ) in FIG. 26B. Steps 1 to 3 are stored in a database in advance.

Next, the flow rate shown in FIG. 26C is specified by the following steps 1 and 2. That is, in step 1, η _M (motor efficiency) is specified from the rated output (P ₀ ) of the motor. In this case, the rated output of the motor (P ₀ )
Is input in advance so that η _M is specified. In step 2, Q = η _M · η _P ·
Q (current flow rate) according to the equation of Pi / 0.163 · γ · H
Is calculated. Current flow rate (Q) by steps 1 and 2
And eta Since _M has been identified, since current lift (H) is known, the flow rate of Figure 26C - flow rate by possible illustrates particular operating point, also to calculate the Pi · eta _M that the lifting height coordinate system -
The specific operating point can be illustrated in the shaft power coordinate system. Next, the temporary pump characteristics are corrected as shown in FIG. 26D by the following steps 1 and 2 to specify the pump characteristics. FIG.
In 6D, the dashed line indicates the temporary pump characteristic, and the solid line indicates the corrected pump characteristic. That is, in step 1, H _A
/ A ratio of H _B corrects the lift of the temporary pump characteristics. Correcting the shaft power of the provisional pump characteristics in a ratio of P _{A /} P _B in step 2. Here H _A, P _A is the lift and the shaft power of the specified operating point specified in FIG. _26C, H _B, P B, respectively are lift and the shaft power of the temporary pump characteristic curve in current flow (Q) .

Next, the tentative characteristic is corrected by 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 during the shutoff operation. The assumption stage of the pump temporary characteristics and the specification stage of the pump operating point (flow rate) and the correction stage of the temporary characteristics in the above will be described with reference to FIGS. 27A to 27D. First, as shown in FIG. 27A, the aperture (φ) and the number of stages (STG)
, Information on the motor including the rated output (P ₀ ) and the rated speed (N), the head (H) and power consumption (Pi) in the current operation, and the head (H in the shutoff operation) _S ) and information of measurement data including power consumption (Pis) are input to the input device 5 shown in FIG.

Next, the main control unit 1 shown in FIG. 1 specifies the provisional pump characteristics shown in FIG. 27B by the following steps 1 to 3. That is, in step 1, the specific speed (N _S ) is obtained from the pump diameter (φ) and the number of stages (STG), the rated output (P ₀ ) and the rated rotation speed (N) of the electric motor.
To identify. In step 2, Q _BEP (maximum efficiency flow rate) is specified based on the diameter (φ) and the number of stages (STG) of the pump, the rated speed (N) of the electric motor, and the specific speed (N _S ).
In step 3, a temporary pump characteristic is created as shown in FIG. 27B, where the representative point in the X direction is Q _BEP and the representative point in the Y direction is Hs (head during shutoff operation) and Pis (power consumption during shutoff operation). At this time, the temporary pump characteristics are created using the non-dimensional 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.

Next, the flow rate shown in FIG. 27C is specified by the following steps 1-2. That is, in step 1, η _M (motor efficiency) is specified from the rated output (P ₀ ) of the motor. In this case, the rated output of the motor (P ₀ )
Is input in advance so that η _M is specified. In step 2, Q = η _M · η _P ·
Q (current flow rate) according to the equation of Pi / 0.163 · γ · H
Is calculated. Current flow rate (Q) by steps 1 and 2
Since the current head (H) is already known since η and η _M have been specified, the specific operating point can be illustrated in the flow-head coordinate system of FIG. 27C, and the flow rate can be calculated by calculating Pi · η _M.
The specific operating point can be illustrated in the shaft power coordinate system. Next, the temporary pump characteristics are corrected as shown in FIG. 27D by the procedure of the following steps 1 and 2, and the pump characteristics are specified. FIG.
In FIG. 7D, the broken line indicates the temporary pump characteristics, and the solid line indicates the corrected pump characteristics. That is, in step 1, Q /
Correcting the flow rate of the provisional pump characteristics in a ratio of Q _B. In Step 2, the shaft power curve is changed to (0, Pis · η _M ), (Q,
Pi · η _M ).

Next, the provisional characteristics are corrected by the head and power consumption during 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 during 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 in this case will be described with reference to FIGS. 28A to 28D.

First, as shown in FIG. 28A, the aperture (φ)
And information on the pump type including the number of stages (STG), information on the motor including the rated output (P ₀ ) and the rated speed (N), the head (H) and power consumption (P
i), the information of the measurement data including the head (H _V ) and the power consumption (Piv) at the time of the valve fully open operation are input to the input device 5 shown in FIG.

Next, in the main controller 1 shown in FIG. 1, the temporary pump characteristics shown in FIG. 28B are created by the following steps 1 to 5. That is, in step 1, the specific speed (N _S ) is obtained from the pump diameter (φ) and the number of stages (STG), the rated output (P ₀ ) and the rated rotation speed (N) of the electric motor.
To identify. In step 2, Q _BEP (maximum efficiency flow rate) is specified based on the diameter (φ) and the number of stages (STG) of the pump, the rated speed (N) of the electric motor, and the specific speed (N _S ).
In step 3, the pump diameter (φ) and the number of stages (S
TG) and to identify a more eta _P (pump efficiency) specific speed _{(N S). H BEP = η P · P 0} /0 in step 4.
H _BEP (highest efficiency head) is calculated by the formula of 163 · γ · Q _BEP . The specific speed and the representative points ((Q _BEP , H _BEP ) and (Q _BEP ,
Based on P ₀ )), temporary pump characteristics are created as shown by the broken line in FIG. 28B. At this time, the temporary pump characteristics are created using the non-dimensional pump characteristics 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.

Next, the flow rate shown in FIG. 28C is specified by the following steps 1-2. That is, in step 1, η _M (motor efficiency) is specified from the rated output (P ₀ ) of the motor. In this case, the rated output of the motor (P ₀ )
Is input in advance so that η _M is specified. In step 2, Q = η _M · η _P ·
Q (current flow rate) according to the equation of Pi / 0.163 · γ · H
Is calculated. Current flow rate (Q) by steps 1 and 2
And eta Since _M has been identified, since current lift (H) is known, the flow rate of Figure 28C - flow rate by possible illustrates particular operating point, also to calculate the Pi · eta _M that the lifting height coordinate system -
The specific operating point can be illustrated in the shaft power coordinate system.

Next, the temporary pump characteristics are corrected as shown in FIG. 28D by the following steps 1 to 5 to specify the pump characteristics. In FIG. 28D, the broken line indicates the provisional pump characteristics, and the solid line indicates the corrected pump characteristics. That is, in step 1, the head of the temporary pump characteristic is corrected by the ratio of H _A / H _B. Correcting the shaft power of the provisional pump characteristics in a ratio of P _{A /} P _B in step 2. Where H _A ,
P _A is the lift and the shaft power of the specified operating point specified in FIG. _28C, H _B, P B is the lift and the shaft power of the temporary pump characteristic curve in current flow (Q), respectively. Identifying the the valve fully open when the flow rate (Q _V) lift (H _V) during the valve fully open operation in step 3. In step 4, the shaft power (Piv · η _M ) during QV is specified. In step 5, the shaft power curve is changed to (Q, Pi ·
η _M ) and an approximate curve passing through (Q _V , Piv · η _M ).

Next, the tentative characteristics are obtained by calculating the head and power consumption under the current operation, the flow rate calculated using the assumed values of the fluid machine efficiency and the motor efficiency, the head and consumption during the shutoff operation and the valve fully open operation. The assumption stage of the pump temporary characteristic, the specification of the pump operating point (flow rate), and the correction stage of the temporary characteristic in the case of correction with electric power will be described with reference to FIGS. 29A to 29D.

First, as shown in FIG. 29A, the aperture (φ)
And information on the pump type including the number of stages (STG), information on the motor including the rated output (P ₀ ) and the rated speed (N), the head (H) and power consumption (P
i), head (H _S ) and power consumption (Pi) during the shutoff operation
s), the information of the measurement data including the head (H _V ) and the power consumption (Piv) at the time of the valve fully open operation are input to the input device 5 shown in FIG.

Next, the main control unit 1 shown in FIG. 1 specifies the provisional pump characteristics shown in FIG. 29B by the following steps 1 to 3. That is, in step 1, the specific speed (N _S ) is obtained from the pump diameter (φ) and the number of stages (STG), the rated output (P ₀ ) and the rated rotation speed (N) of the electric motor.
To identify. In step 2, Q _BEP (maximum efficiency flow rate) is specified based on the diameter (φ) and the number of stages (STG) of the pump, the rated speed (N) of the electric motor, and the specific speed (N _S ).
The X-direction representative point and _{Q BEP} in step 3, the Y-direction representative point as _{H S} and Pis, creating a temporary pump characteristic as shown in FIG. 29B. At this time, the temporary pump characteristics are created using the non-dimensional 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.

Next, the flow rate shown in FIG. 29C is specified by the following steps 1-2. That is, in step 1, η _M (motor efficiency) is specified from the rated output (P ₀ ) of the motor. In this case, the rated output of the motor (P ₀ )
Is input in advance so that η _M is specified. In step 2, Q = η _M · η _P ·
Q (current flow rate) according to the equation of Pi / 0.163 · γ · H
Is calculated. Current flow rate (Q) by steps 1 and 2
Since the current head (H) is already known since η and η _M have been specified, the specific operating point can be illustrated in the flow-head coordinate system of FIG. 29C, and the flow rate is calculated by calculating Pi · η _M.
The specific operating point can be illustrated in the shaft power coordinate system.

Next, the temporary pump characteristics are corrected as shown in FIG. 29D by the following steps 1 and 2 to specify the pump characteristics. In FIG. 29D, the broken line indicates the temporary pump characteristic, and the solid line indicates the pump characteristic after correction. That is, in step 1, the flow rate of the provisional pump characteristic is corrected by the ratio of Q / _QB . The shaft power curve in step _{2 (0, Pis · η M} ), (Q, Pi · η M), (Q V,
Piv · η _M ).

Next, an operating point (flow rate) is specified based on the provisional characteristics and the head during the current operation, and an assumed stage of the pump temporary characteristics and the pump operating point (flow rate) when correcting the provisional characteristics with the current power consumption. FIG. 30A shows the identification and provisional characteristic correction stages
30D will be described with reference to FIG.

First, as shown in FIG. 30A, the aperture (φ)
And information on the pump type including the number of stages (STG), the first item (Q1, H1) and the second item (Q2, H2), and the electric motor including the rated output (P ₀ ) and the rated speed (N). Information, head (H) and power consumption (P
The input device 5 shown in FIG.
To enter.

Next, in the main controller 1 shown in FIG. 1, the provisional pump characteristics shown in FIG. 30B are created by the following steps 1 to 5. That is, in step 1, the specific speed (N _S ) is obtained from the pump diameter (φ) and the number of stages (STG), the rated output (P ₀ ) and the rated rotation speed (N) of the electric motor.
To identify. In step 2, H _S ′ = (H1 + 2 ×
Assume the deadline lift _{(H S} ') based on the formula H2) / 3. Identified specific speed _{(N S)} to the original in step 3 (0, _{H S} '), the (Q2, H2) to create a lift curve passing through (indicated by a broken line), and _(Q MAX, _{P 0)} A passing shaft power curve is created (shown by a broken line). At this time, a temporary pump characteristic is created using the dimensionless pump characteristic shown in FIG. In step 4, with (Q2, H2) as the origin,
A head curve shown by a solid line is created by correcting the head by the ratio of ΔH / (H1−H2). In step 5, a shaft power curve indicated by a two-dot chain line is created by applying a head curve correction value with the origin at (0, 0) to the shaft power curve and making a correction. Step 1 is a database.

Next, the flow rate shown in FIG. 30C is specified by the following steps 1 and 2. That is, in step 1, η _M (motor efficiency) is specified from the rated output (P ₀ ) of the motor. In step 2, the current operation flow rate (Q) is specified from the head (H) during the current operation. Also Pi ・
identifying the current shaft power (Pi · η _M) by calculating the eta _M. Step 1 is a database.

Next, the temporary pump characteristics are corrected as shown in FIG. 30D by the following steps to specify the pump characteristics. That is, by correcting the shaft power curve in a ratio of _{(Pi · η M) / P} A, to create a shaft power curve indicated by a solid line.

Next, an operating point (flow rate) is specified from the temporary characteristics and the head during the current operation, and the pump temporary characteristics are assumed in the case where the temporary characteristics are corrected by the current power consumption and the head and power consumption when the valve is fully opened. The steps, the specification of the pump operating point (flow rate), and the step of correcting the provisional characteristics will be described with reference to FIGS. 31A to 31D.

First, as shown in FIG. 31A, the aperture (φ)
And information on the pump type including the number of stages (STG), the first item (Q1, H1) and the second item (Q2, H2), and the electric motor including the rated output (P ₀ ) and the rated speed (N). Information, head (H) and power consumption (P
i), the information of the measurement data including the head (H _V ) and the power consumption (Piv) at the time of the valve fully open operation are input to the input device 5 shown in FIG.

Next, in the main controller 1 shown in FIG. 1, the temporary pump characteristics shown in FIG. 31B are created by the following steps 1 to 5. That is, in step 1, the specific speed (N _S ) is obtained from the pump diameter (φ) and the number of stages (STG), the rated output (P ₀ ) and the rated rotation speed (N) of the electric motor.
To identify. In step 2, H _S ′ = (H1 + 2 ×
Assume the deadline lift _{(H S} ') based on the formula H2) / 3. Identified specific speed _{(N S)} to the original in step 3 (0, _{H S} '), the (Q2, H2) to create a lift curve passing through (indicated by a broken line), and _(Q MAX, _{P 0)} A passing shaft power curve is created (shown by a broken line). At this time, a temporary pump characteristic is created using the dimensionless pump characteristic shown in FIG. In step 4, with (Q2, H2) as the origin,
A head curve shown by a solid line is created by correcting the head by the ratio of ΔH / (H1−H2). In step 5, a shaft power curve indicated by a two-dot chain line is created by applying a head curve correction value with the origin at (0, 0) to the shaft power curve and making a correction. Step 1 is a database.

Next, the flow rate specification shown in FIG. 31C is performed by the following steps 1 and 2. That is, in step 1, η _M (motor efficiency) is specified from the rated output (P ₀ ) of the motor. In step 2, the current operation flow rate (Q) is specified from the head (H) during the current operation. Also Pi ・
identifying the current shaft power (Pi · η _M) by calculating the eta _M. Step 1 is a database.

Next, the temporary pump characteristics are corrected as shown in FIG. 31D by the following steps 1 to 3 to specify the pump characteristics. In step 1, (Pi
correcting the shaft power curve in a ratio of η _M) / _{P A.} Step 2 Identify the valve fully open when the flow rate _{(Q V)} from the _{H V} in, and identifies the time valve fully open shaft power (Piv · η _M). In step 3, the shaft power curve is changed to (Q, Pi ·
η _M ) and an approximate curve passing through (Q _V , Piv · η _M ).

As described above, FIGS.
The pump characteristics can be specified by any of the methods shown in D, assuming the provisional characteristics of the pump, specifying the pump operating point (flow rate), and correcting the provisional characteristics. Since the characteristic curve as shown in FIG. 6 can be specified, the diagnostic system of the present invention can be operated with relatively high accuracy.

The diagnostic system shown in FIGS. 1 to 31A to 31D performs a diagnosis by actually measuring the power consumption and the like at the site where the pump is actually operated, and the diagnostic accuracy is high.
There is a disadvantage that it takes time to collect data.

That is, the diagnostic system shown in FIGS. 1 to 31A to 31D requires an operation to actually perform a diagnosis on the spot by actually operating the pump, that is, a so-called “main diagnosis”. Therefore, the present inventor has studied a method of knowing the investment effect or the cost effect of the inverter introduction by a simple diagnosis that can be performed in advance on a desk before performing the main diagnosis on site.
Here, the investment effect or the 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. As a result, as a result of the simple pre-diagnosis, the main diagnosis may be omitted in some cases, and the diagnosis cost can be reduced.

Hereinafter, an embodiment of an energy-saving pre-diagnosis system for a fluid machine according to the present invention will be described with reference to the drawings.

The hardware configuration of the energy-saving pre-diagnosis system for a fluid machine according to the present embodiment is the same as the hardware configuration shown in FIG. In the present embodiment, a pump will be described as an example of a fluid machine.

As shown in FIG. 1, the energy-saving pre-diagnosis system for a fluid machine has a main control unit 1 for controlling the whole system, and a main storage unit 2 connected to the main control unit 1.
And The main control unit 1 includes a control device 3 and an arithmetic device 4. The main controller 1 is connected to an input device 5 including a keyboard and a mask, and an output device 6 including a printer and a display. The main control unit 1 has a control program such as an operating system, a program that defines a procedure for diagnosing 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.

FIG. 32 is a diagram showing the flow rate-head characteristic and the flow rate-power consumption characteristic of the pump.
min), and the vertical axis indicates the total head (m) or the power consumption (kW). Now, data of the flow rate-head and the flow rate-power consumption of the motor pump when driven by an AC commercial power supply can be generally obtained in advance in the form of a test report or a representative characteristic curve. If you enter this number for example five points (five points indicated by & point in FIG. 32), as in FIG. 32, it is possible to draw a curve alpha ₈ and gamma ₈ by a suitable function.
In the figure, a black portion in a substantially triangular shape is a point at which the planning items on the equipment side are input. Since it is known that the pipe loss is proportional to the square of the flow rate, inputting the actual head (that is, the pipe resistance when the flow rate is zero) allows the pipe resistance curve β to pass through the planned items on the equipment side. Can be subtracted. If the actual head is unknown, it can be assumed that the actual head is 50% of the head of the plan.

The present invention is provided with a calculating means for calculating the effect of reducing the power consumption when the rotational speed of the fluid machine is reduced by using the frequency converter. The calculation means functions as follows (see FIG. 33). There are a number of points, not shown on the curve alpha _8. The coordinates of the point are defined as (q ₁ , h ₁ ), (q ₂ , h ₂ ). The calculating means sets a certain rotational speed ratio for these points. Now, when the rotational speed ratio was set to 0.95, _{q 1} moves to _{q 1} × 0.95, _{h 1} is _{h 1} × 0.
To move to 95 ^2. That is, (0.95q ₁ , 0.95 ²
_{h 1), (0.95q 2,} 0.95 2 h 2) ...... made the point was born, is the connected curve these points the α _7. Hereinafter, similarly, the rotation speed ratio is set to 0.8, 0.85, 0.80.
A curve of α _{6 to} α ₁ is drawn as. The curve β is a resistance curve on the equipment side (piping side) specified by the method described above. The points indicated by are the actual operating points,
Point is a calculated operating point when the rotational speed is changed. However, since a margin is expected in the planned value (calculated value) of the pipe loss, the true operating point is often on the higher flow rate side. Further, on the curve gamma _8, there are a plurality of points, not shown. The coordinates of the point are defined as (q ₁ , w ₁ ), (q ₂ , w ₂ )... According to the flow rate and the power consumption. The calculating means sets a certain rotational speed ratio for these points as described above. If the rotational speed ratio was set to 0.95, _{q 1} moves to _{q 1} × 0.95, _{w 1} is _{w 1} × 0.
Moving to 95 ^3. This is based on the premise that the pump efficiency and the motor efficiency do not change even when the rotation speed is changed. In addition, the frequency conversion loss when using an inverter or the like is not considered. By considering these factors in advance, it is possible to calculate the power consumption with higher accuracy.

As described above, (0.95q ₁ , 0.9
5 ³ w ₁ ), (0.95 q ₂ , 0.95 ³ w ₂ )... Are generated, and a curve connecting these points is γ ₇ . Hereinafter, the rotational speed ratio is similarly set to 0.9, 0.85, 0.80.
A curve of γ ₆ to γ ₁ is drawn as. Curve γ _{8 to} γ
_{On 1} , the power consumption corresponding to the operating points is indicated by dots.

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.
3 shows a flow rate-head characteristic curve and a flow rate-power consumption characteristic curve obtained in 3. In FIG. 34, the lowermost table is represented by using A, and this portion is enlarged and shown in FIG.
A part of FIG. 34, that is, FIG. 35 is a table showing estimated power consumption reduction values. In FIG. 35, the vertical list (items)
The figure shows three conditions of an actual operation flow rate when the commercial power supply is driven, a case where the flow rate is adjusted to a plan flow rate using an inverter, and a case where the flow rate is reduced from the plan flow rate using an inverter.

The side view shows the rotation ratio (1.0 when the commercial power supply is driven), power consumption, power consumption (calculated by multiplying the power consumption by an operation time separately input), and CO ₂ emission (consumption). Power consumption is multiplied by a coefficient shown in the figure), power consumption reduction, reduced power cost (calculated at 13 yen / kwh of power unit price), and reduction rate (power amount / CO ₂ / power cost). . In this example, 18% energy saving can be achieved only by adjusting the flow rate to the plan value, and the annual electricity bill can be reduced by 286,000 yen. In addition, if a margin is expected in the planned flow rate itself, for example, if the flow rate can be reduced by 10%, energy saving of 40% can be achieved, and the electricity bill can be reduced by 639,600 yen per year. In this way, it is possible to give an estimate of the payback period for the capital investment for the introduction of the inverter.

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. The recording medium on which the program for causing the program to execute the above method 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 is a main control unit 1 shown in FIG.
(Including the control device 3 and the arithmetic device 4), the main storage device 2,
A personal computer PC including an LCD constituting a part of the input device 5 and the output device 6, and a floppy disk (FD) or C
It includes a D-ROM and a printer PR which forms a part of the output device 6 shown in FIG.

As described above, according to the present invention, useless energy consumed around the fluid machine can be grasped in advance. Then, without actually operating the fluid machine on site, it is possible to easily estimate the energy saving amount brought by the rotation speed adjustment using an inverter or the like. Therefore, the investment effect or cost effect when introducing an inverter or the like is easily clarified in advance, so that it is easy to penetrate energy saving into the market.

Next, an embodiment of a method for displaying characteristics of a fluid machine and a display object according to the present invention will be described with reference to the drawings.

FIG. 37 shows an example in which the present invention is applied to a motor (three-phase induction motor) driven centrifugal pump. The inside of the outermost square line 10 is a display object such as a catalog page. This plane (display object)
11, a curve 12 showing the following QH characteristic and information 14, 15 related to power consumption are described.

In the plane 11, a curve (QH) showing the QH characteristic in which the horizontal axis indicates the discharge amount and the vertical axis indicates the scale of the total head.
In this example, nine (−H characteristic curves) 12 are described for each frequency applied to the motor, and the operating frequency 13 of the motor (pump) is numerically described near each curve 12. All of these QH characteristic curves 12 may be measured data, or may be displayed as calculated values based on the following relational expression (1). Q∝N H∝N ² N∝F W∝N ³ (1) where, Q: discharge amount, H: total head, N: rotation speed, F:
Frequency, W: power consumption In the vicinity of each of the QH characteristic curves 12, approximate power consumption 14 as information regarding power consumption and approximate annual power rate 1
5 is described numerically. Here, even if the frequency is the same, the power consumption (power rate) differs depending on the operating point, that is, the discharge amount. In this example, however, the discharge amount at the maximum load (however, the pump selection range when driving the commercial power supply) 2) shows an example described on the side of the QH characteristic curve 12 with the power consumption (power rate) in (in) as a representative value.

That is, in the vicinity of the QH characteristic curve 12 at a frequency of 50 Hz, the approximate power consumption 14a and the approximate annual power rate 15a when the commercial power of the frequency 50Hz is directly supplied to the motor are described. In the vicinity of the QH characteristic curve 12 at the frequency of, the approximate power consumption 14b including the inverter loss when the inverter is used.
And the annual power charge 15b is described as a reduction amount in comparison with the case of the frequency of 50 Hz.

For example, when operating with a commercial power supply of 50 Hz, the approximate power consumption at the maximum load point discharge amount is 10.5.
0kw, and based on this, the operation time 8400h /
The annual power rate calculated at the annual power rate of 13 yen / kwh is 1,150,000 yen. On the other hand, the approximate power consumption when the inverter is operated at a frequency of 45 Hz, for example, is reduced by 2.46 kW as compared with the case where the inverter is operated at the commercial power supply of 50 Hz.
This indicates that the cost will be reduced by 69,000 yen. On the plane (display object) 11, the price 16 of the inverter is also
In this example, it is described as 498,000 yen. Thus, as described above, when the inverter is operated at a frequency of 45 Hz using an inverter instead of the commercial power supply of 50 Hz, the investment (or cost) of the inverter alone in 1.85 (489,000 / 269,000) It can be seen that can be recovered.

Here, it is necessary to consider that the operating time and the electricity rate (kwh unit price) differ depending on each site and region, and that investment (or cost) requires installation cost of the inverter and the like. In comparison with the conventional pump characteristic display (product), it is much easier to calculate the investment effect or the cost effect. The plane (display object) 11 includes:
The selection range 17 of the pump when the commercial power supply is driven is surrounded by a broken line, which makes it easy to examine the possibility of replacing the pump with a small one-class capacity. The same display as described above is also provided on a plane constituting a display object such as a paper surface of a catalog of a pump having a small capacity of one class. Although not shown, if the price of the pump is also displayed on the plane (display object) 11, it is easy to compare the return on investment of replacing the pump with a smaller one-class capacity and increasing the number of inverters. Further, the plane (display object)
11, a calculation condition 18 of information related to power consumption is described. In this example, the operation time is 8400 h / year,
It is described as a power charge of 13 yen / kwh. As a result, when the operation time and the like are different, a simple multiplication / division calculation may be performed in consideration of the difference.

Next, with reference to FIG. 37 and FIG. 38, an example of calculation of simple investment effect or cost effect of introducing an inverter will be described. FIG. 38 shows an example of essential items 19 of the pump required only in an emergency in the plane (display object) 11 of FIG. is there. In this case, a pump having a capacity one class lower is sufficient in consideration of almost all operating conditions (requirements), but the pump is selected in consideration of the requirements in an emergency.

The operating time of daily essential items is 6000h /
It is assumed that the electricity price is 20 yen / kwh.
At this time, since 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 the inverter is not used. Then, the electricity rate can be reduced by 4.86 kw × 6000 h / year × 20 yen / kwh = 583,200 yen per year. The price of the inverter is 498,0
Since the cost is ¥ 00, 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, the return on investment of the inverter introduction can be grasped in a very short time.

FIG. 39 shows a second embodiment of the fluid machine characteristic display method and display object according to the present invention, in which information on power consumption is described in more detail. That is, the approximate annual power rate 15 which is information on power is described in the vicinity of the QH characteristic curve 12 and, at the same time, a plurality of curves (power consumption A power curve 21 is separately added, and a reduction rate (%) 22 and the approximate power consumption 14 similar to the first embodiment are numerically described near the curve 21. According to this embodiment, when it is desired to accurately calculate the investment effect or the cost effect of the inverter introduction (expansion) and the absolute amount of energy saving, the power consumption curve 2
This can be realized by reading “1”.

FIG. 40 shows a third embodiment of a fluid machine characteristic display method and a display object according to the present invention. The third embodiment shows the QH characteristic curve 12, the rotation speed (frequency), and the like. A plurality of equal power consumption curves 23 for each power consumption substantially determined by a discharge amount are displayed in the same coordinate system. The equal power consumption curve 23 is indicated by a broken line, and the curve 2
In the vicinity of 3, an annual electricity charge 24 is indicated by a numeral. According to this embodiment, the graph shown in FIG.
There is an effect that the graph shown in FIG. 9 is combined into one graph.

Next, by inputting data of flow rate-pressure characteristics and flow rate-power consumption of the fluid machine with a motor when driven by an AC commercial power supply, the display object or the power consumption reading shown in FIGS. A calculation / drawing system by a computer which can obtain a diagram will be described. The hardware configuration of the calculation / drawing system is the same as the hardware configuration shown in FIG. Calculation·
The drawing system 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 an arithmetic device 4. The main controller 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. In FIG. 1, thick arrows indicate flows of data and programs, and thin arrows indicate flows 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 necessary data. The calculation process and the drawing process are realized. The main storage device 2 is composed of a hard disk, a flexible disk, an optical disk, or the like.

FIG. 41 is a schematic processing flowchart showing an outline of the processing flow in the calculation / drawing system shown in FIG. In step 1, data of a flow rate-head characteristic and a flow rate-power consumption characteristic 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. Next, in step 2, the flow rate-head characteristic and the flow rate-power consumption characteristic at a plurality of rotation speeds different from the rotation speed input in step 1 are calculated. The calculation is performed by the relational expression (1). In this case, measurement data of each rotation speed may be input instead of the calculation. Next, in step 3, the operating time of the fluid machine and the power rate per unit power consumption are input. Next, in step 4, the flow rate-head characteristics at different rotational speeds are displayed by a plurality of curves, and information related to power consumption is displayed on the output device 6 on the same plane. This output device 6 is a printer or an LC as described above.
D or the like. The information related to the power consumption includes various types of information shown in FIGS.

An operation / drawing system using a personal computer is the same as the configuration shown in FIG. As shown in FIG. 36, the system includes the main control unit 1 shown in FIG.
(Including the control device 3 and the arithmetic device 4), the main storage device 2,
A personal computer PC including an LCD constituting a part of the input device 5 and the output device 6, and a floppy disk (FD) or C
It includes a D-ROM and a printer PR which forms a part of the output device 6 shown in FIG.

In the embodiment of the present invention, 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). As described above, according to the present invention, by describing the characteristic curve of a fluid machine in, for example, a catalog of a pump or an inverter, the user can
It is possible to easily understand the expected energy saving effect and the payback period of the initial investment without performing complicated calculations. Therefore, there is an effect that it stimulates demand for an inverter for fluid machinery and an inverter-mounted pump that has recently become popular, and thereby allows energy saving to penetrate the market.

The present invention is a system for grasping wasteful energy consumed around a fluid machine, and is applicable to equipment using a circulating pump for cold / hot water and equipment using a water supply pump. [Brief description of drawings]

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 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.

FIGS. 3A and 3B are diagrams illustrating a diagnostic procedure in the fluid machine diagnostic system according to the present invention, and are diagrams illustrating characteristic curves of the fluid machine.

FIGS. 4A and 4B are diagrams for explaining 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.

FIGS. 5A and 5B are diagrams illustrating a diagnostic procedure in the fluid machine diagnostic system according to the present invention, and are diagrams illustrating characteristic curves of the fluid machine.

FIG. 6 is a diagram illustrating a diagnosis procedure in the diagnosis system for a fluid machine according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.

FIG. 7 is a diagram illustrating a diagnosis procedure in the diagnosis 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 diagnosis procedure in the diagnosis 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 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. 10 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. 11 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. 12 is a diagram illustrating a diagnosis procedure in the diagnosis system for a fluid machine according to the present invention, and is a diagram illustrating a characteristic curve of the fluid machine.

FIG. 13 is a schematic processing flowchart showing an outline of a processing 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 the mounting operation when the performance adjusting device for a fluid machine is used.

16A and 16B are diagrams showing details of the performance adjusting device shown in FIG. 14, FIG. 16A is a partially sectional front view, and FIG. 16B is a side view.

FIG. 17 is a sectional view taken along line XVII-XVII in FIG. 16A.

18A and 18B are views showing details of the performance adjusting device shown in FIG. 15, FIG. 18A is a partially sectional front view, and FIG. 18B is a plan view.

FIG. 19 is a sectional view taken along line XIX-XIX in FIG. 18A.

FIGS. 20A and 20B are views showing a third embodiment of the mounting work when using the performance adjusting device for a fluid machine, FIG. 20A is a side view, and FIG. 20B is a view taken along arrow XX of FIG. 20A. It is.

21A and 21B show another embodiment of the performance adjusting device main body shown in FIGS. 14 to 20;
Is a front view, and FIG. 21B is a side view.

FIG. 22 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. 23 is a schematic view showing an example of equipment brought to the operation site of the fluid machine to be diagnosed.

FIG. 24 is a dimensionless characteristic of a pump, which shows the characteristic of the pump with respect to the specific speed (flow rate-head, flow rate-shaft power) in a dimensionless manner.

FIG. 25 is a diagram showing specific speed-pump efficiency characteristics.

FIGS. 26A and 26B show temporary characteristics of a pump in a case where the temporary characteristics are corrected by a flow rate calculated using a head and power consumption during the current operation and assumed values of the fluid mechanical efficiency and the motor efficiency. It is a figure which shows the assumption stage, the specification of a pump operating point (flow rate), and the correction stage of a temporary characteristic.

FIGS. 27A to 27D are graphs showing provisional characteristics of a flow rate calculated using a head and power consumption during the current operation, assumed values of the fluid machine efficiency and the motor efficiency, and a head and consumption during the shutoff operation. It is a figure which shows the assumption stage of a pump temporary characteristic in the case of amendment with electric power, the specification of a pump operating point (flow rate), and the correction stage of a temporary characteristic.

28A to 28D are graphs showing provisional characteristics of a head and a power consumption at the time of the current operation, a flow rate calculated using assumed values of the fluid mechanical efficiency and the motor efficiency, and a head and a head at the time of the valve fully open operation. It is a figure which shows the assumption stage of a pump temporary characteristic in the case of correction | amendment by power consumption, the specification of a pump operating point (flow rate), and the correction stage of a temporary characteristic.

FIG. 29A to FIG. 29D are graphs showing provisional characteristics of a flow rate calculated using a head and power consumption at the current operation, an assumed value of the fluid mechanical efficiency and the motor efficiency, a shutoff operation and a valve fully open operation at the current operation. FIG. 9 is a diagram showing a tentative stage of a pump temporary characteristic, a stage of specifying a pump operating point (flow rate), and a stage of correcting the temporary characteristic in the case of correcting with a head and power consumption at the time.

FIGS. 30A to 30D show an assumed stage of a pump temporary characteristic and a pump operation in a case where an operating point (flow rate) is specified based on a temporary characteristic and a head in a current operation, and the temporary characteristic is corrected with current power consumption. It is a figure which shows the specification of a point (flow rate), and the correction | amendment stage of a temporary characteristic.

FIG. 31A to FIG. 31D show a case where an operating point (flow rate) is specified based on a provisional characteristic and a head during the current operation, and the provisional characteristic is corrected with the current power consumption and the head and power consumption when the valve is fully opened. It is a figure which shows the assumption stage of a pump temporary characteristic, the specification of a pump operating point (flow rate), and the correction stage of a temporary characteristic.

FIG. 32 is a diagram showing a diagnosis procedure in the energy-saving pre-diagnosis system for a fluid machine according to the present invention;
FIG. 3 is a diagram illustrating a characteristic curve of the fluid machine.

FIG. 33 is a diagram showing a diagnosis procedure in the energy-saving pre-diagnosis system for a fluid machine according to the present invention;
FIG. 3 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 made by the energy-saving pre-diagnosis system for a fluid machine according to the present invention.

FIG. 35 is a diagram showing a portion A in FIG. 34;

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 of the first embodiment of the method for displaying the characteristics of the fluid machine and the display object according to the present invention.

FIG. 38 is a diagram attached to description of an example of a trial calculation of a simple return on investment by introducing an inverter.

FIG. 39 is a diagram illustrating characteristics of the fluid machine according to the second embodiment of the fluid machine characteristic display method and the display object according to the present invention.

FIG. 40 is a diagram illustrating 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 flowchart showing an outline of a processing flow in the calculation / drawing system.

FIG. 42 is a diagram showing an example of a display example of conventional pump characteristics.

43A and 43B are diagrams showing another example of a display example of another conventional pump characteristic.

──────────────────────────────────────────────────続 き Continuation of the front page (31) Priority claim number Japanese Patent Application No. 10-310575 (32) Priority date October 30, 1998 (Oct. 30, 1998) (33) Priority claim country Japan (JP) Application for accelerated examination (72) Inventor Keita Uei 11-1 Haneda Asahimachi, Ota-ku, Tokyo Inside Ebara Works (72) Inventor Yoshiaki Miyazaki 11-1 Haneda Asahi-cho, Ota-ku, Tokyo Co., Ltd. Ebara Corporation (72) Inventor Katsuji Iijima 11-1, Haneda Asahimachi, Ota-ku, Tokyo Co., Ltd.Ebara Corporation (72) Inventor Hiromi Tamai 11-1, Haneda Asahi-cho, Ota-ku, Tokyo Ebara Corporation In-house (56) References JP-A-9-14180 (JP, A) JP-A-3-145597 (JP, A) JP-A-61-157790 (JP, A) JP-A-7-332280 (JP, A) JP-A-9-32806 (JP, A) JP-A-55-31908 JP, A) JP-A-55-31907 (JP, A) JP-A-59-58317 (JP, A) JP-A-59-162395 (JP, A) JP-A-64-66481 (JP, A) Hei 3-168386 (JP, A) The Japan Society of Mechanical Engineers, Handbook of Mechanical Engineering, [Parts 9 and 10], Japan, The Japan Society of Mechanical Engineers, March 20, 1979, 6th edition, 2nd edition, Pp. 9-39, 40, 49, 51, 63.65 Shigemi Kajiwara, Pump and its usage, Japan, Maruzen Co., Ltd., June 5, 1960, 4th edition, pp. 50-53, 256, 257 ( 58) Fields surveyed (Int.Cl. ⁷ , DB name) F04B 49/00-51/00 F04D 15/00-15/02

Claims (19)

(57) [Claims] 1. A first specifying means for specifying characteristics of a fluid machine represented by a flow rate-head characteristic by inputting predetermined information of a fluid machine to be diagnosed, and: By operating the 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 during operation, the characteristics of the specified fluid machine and the measured fluid are input. Second specifying 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 machine; and the operating flow rate or operating pressure when the rotational speed of the fluid machine to be diagnosed is changed Or a processing means for calculating a change in power consumption and displaying the calculation result. 2. The fluid machine according to claim 1, wherein the first specification unit is configured to function by inputting one or more of the following data 1 to 11. Diagnostic system. 1. 1. Suction aperture (or count) of fluid machine 2. Discharge diameter (or count) of fluid machine 3. Rated output of motor driving fluid machine 4. Number of poles of motor driving fluid machine 5. Operating frequency of motor driving fluid machine 6. Nameplate essentials for fluid machinery (flow rate-head) 7. Machine name of fluid machine 8. Manufacturer of fluid machinery 9. Number of stages of impeller of fluid machine 10. Outer diameter of impeller of fluid machine Fluid machine test data (flow rate-head, flow rate-power consumption) 3. The characteristic of the fluid machine according to claim 1, wherein the characteristics of the fluid machine specified by the first specifying unit are corrected by inputting power consumption of the fluid machine at an actual operating point. Fluid machine diagnostic system. 4. The characteristic of the fluid machine specified by the first specifying means is corrected in accuracy by inputting an operating pressure and / or power consumption at a cutoff operating point separately from an actual operating point. The diagnostic system for a fluid machine according to claim 3, wherein: 5. The fluid machine diagnostic system according to claim 1, wherein the calculation result obtained by said processing means is corrected for accuracy by inputting a value of an actual head. 6. A controller according to claim 1, wherein a controller provided with a frequency converter is used as means for changing the rotation speed of the fluid machine to be diagnosed.
A diagnostic system for a fluid machine according to claim 1. 7. The controller changes the frequency generated by the frequency converter to change the rotational speed of the fluid machine, and compares the operating pressure when the valve is opened and the operating pressure when the valve is shut off at each rotational speed. 7. The diagnostic system for a fluid machine according to claim 6, wherein the actual head is determined based on a point at which the difference between the two is eliminated and the pipe loss is determined. 8. A function of specifying characteristics of a fluid machine represented by a flow rate-head characteristic by inputting predetermined information of a fluid machine to be diagnosed, and operating the fluid machine to be diagnosed. By inputting a 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 input. Or, the function to specify the operating flow rate or operating pressure of the fluid machine based on the relationship with the operating flow rate, and to 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 computer-readable recording medium that records a program for causing a computer to realize a function of displaying a calculation result. 9. A first specifying means for specifying a characteristic represented by a flow rate-head characteristic of a fluid machine to be diagnosed, and an operating pressure (head) during operation of the fluid machine to be diagnosed.
Or second specifying means for specifying an actual operating point determined by an operating flow rate or power consumption or an operating current value by a relationship between the specified characteristics of the fluid machine and an operating pressure or an operating flow rate of the fluid machine. And a processing means for calculating a change in the operating point when the rotational speed of the fluid machine to be diagnosed is changed, and displaying the calculation result. 10. A step of specifying a characteristic typified by a flow rate-head characteristic of a fluid machine to be diagnosed, and an operating pressure (head) during operation of the fluid machine to be diagnosed.
Or a step of specifying an actual operating point determined by an operating flow rate or power consumption or an operating current value based on the relationship between the specified characteristics of the fluid machine and the operating pressure or the operating flow rate of the fluid machine. A method for diagnosing a fluid machine, comprising: calculating a change in an operating point when the rotation speed of the fluid machine is changed; and displaying a calculation result. 11. The diameter of a fluid machine and the number of impeller stages,
Based on the rated output and the rated rotation speed of the electric motor that drives the fluid machine, one point of the fluid machine characteristic is set as a representative point, and the ratio of the lift and the shaft power at the representative point to the lift and the shaft power other than the representative point is determined. By calculating the head and shaft power at each flow rate, and assuming the tentative characteristics of the fluid machine, and at least correcting the tentative characteristics based on measurement data including at least the head and power consumption during the current operation A step of specifying a characteristic of the fluid machine and an operating point including an operation flow rate, the method comprising: 12. The representative point may be a maximum efficiency flow rate of a fluid machine, a head calculated by using an assumed value stored in a database assuming an average efficiency of the fluid machine, and a rated output of a motor. The method according to claim 11, characterized in that: 13. The method according to claim 13, wherein the representative point is a flow rate and a head calculated using at least two points of information for specifying characteristics of the fluid machine including a flow rate and a head of the fluid machine, and a motor rated output. The method according to claim 11, characterized in that: 14. The fluid according to claim 12, wherein the tentative characteristic is corrected by a flow rate calculated using a head and power consumption at a current operation and assumed values of a fluid mechanical efficiency and an electric motor efficiency. Method for specifying mechanical properties. 15. The temporary characteristic is corrected by a head and power consumption during a current operation, a flow rate calculated using assumed values of fluid machine efficiency and an electric motor efficiency, and a head and power consumption during a shutoff operation. 13. The method according to claim 12, further comprising the steps of: 16. The tentative characteristic is corrected by a head and power consumption during a current operation, a flow rate calculated using assumed values of fluid machine efficiency and an electric motor efficiency, and a head and power consumption during a fully open valve operation. 13. The method according to claim 12, further comprising the steps of: 17. The flow rate calculated by using the tentative characteristics based on the head and power consumption at the time of the current operation, the assumed values of the fluid machine efficiency and the motor efficiency, and the head and the consumption at the time of the shutoff operation and the valve fully open operation. 13. The method according to claim 12, wherein the correction is performed using electric power. 18. The method according to claim 13, wherein an operating point (flow rate) is specified based on the temporary characteristics and a head at the time of the current operation, and the temporary characteristics are corrected with the current power consumption. 19. The tentative characteristic according to claim 13, wherein an operating point (flow rate) is specified from the tentative characteristic and the head at the time of the current operation, and the tentative characteristic is corrected with the current power consumption and the power consumption when the valve is fully opened. Fluid mechanical property identification method.