JP2011179414A - Fluid machine, and fluid machine operation control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid machine effectively suppressing counter wind pressure entered into an air duct and applied to the rotary vane of a ventilation fan without causing impact and impact noise when a valve element is opened/closed. <P>SOLUTION: Each guide vane 14 includes a fixed guide vane 14a and a movable guide vane 14b, the fixed guide vane 14a is fixed to a barrel 10, and the movable guide vane 14b is rotatable around a rotating shaft 16 perpendicular to the axial direction of the barrel 12. A movable vane opening automatic control mechanism 24 is provided so that when a reverse fluid flow flowing into an inlet port is led to flow into from the discharge port of the barrel, by fluid differential pressure generated, the movable guide vane 14b is retained in such a position that the movable guide vane 14b is rotated in the direction of a fully closed position from a fully opened position as a normal position with the vane surface of the movable guide vane 14b continuous with the vane surface of the fixed guide vane 14a, thereby changing the direction of the reverse fluid flow and reducing pressure of the reverse fluid flow abutting on the rotating vane 15. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to an operation control device for a fluid machine that is disposed in a flow path such as an exhaust duct and sends an air flow from one end of the flow path to the other end, and in particular, an air flow (wind) having a pressure from the outside from one end. TECHNICAL FIELD The present invention relates to a fluid machine such as a ventilation fan disposed in a flow path that enters the other end (forward flow direction) and from the other end to one end (reverse flow direction), and a fluid machine operation control device that controls the operation of the fluid machine. Is.

  Conventionally, as shown in FIG. 1A, there is a ventilation fan 101 as an example of a fluid machine that is disposed in a flow channel 100 such as an exhaust duct and sends gas from one end of the flow channel 100 to the other end. The ventilation fan 101 includes a rotor blade 102, and an airflow (wind) sucked from one end of the flow path 100 is indicated by an arrow B by rotating the rotor blade 102 in the direction indicated by the arrow A by an electric motor 103. Thus, the other end is fed and discharged.

  In the ventilation fan 101 as described above, an air flow (pressure wind) having a pressure at which the normal rotation of the ventilation fan 101 cannot be maintained in the flow path 100 is indicated by arrows C and D in FIGS. In addition, there are cases where it enters in the reverse flow direction and the forward flow direction. As a countermeasure in such a case, conventionally, as shown in FIG. 2, the apparatus includes a pressure wind shut-off device 110 and a ventilation fan protection control device 202, and the control flow shown in FIG. The ventilation fan 101 installed in 100 is protected so that the pressure air does not reach it. Note that FIG. 2 shows a ventilation fan operation control device that controls the operation of a normal ventilation fan when no pressure air is blown, and the ventilation fan when the pressure air enters and the normal ventilation fan operation control cannot be performed. FIG. 3 is a diagram showing a system configuration including a ventilation fan protection device for performing control for protecting against airflow, and FIG. 3 is a control flow showing a control method for the pressure wind blocker 110 under conditions for switching between normal control and protection control of the ventilation fan. FIG.

  In FIG. 2, reference numeral 110 denotes a pressure wind blocking device (damper) that suppresses the pressure wind acting on the flow path 100, 112 denotes a drive unit such as an electric motor that drives the opening / closing operation of the pressure wind blocking device 110, and 111 denotes a ventilation fan 101 , A rotational speed transmitter 114 for detecting the rotational speed of the ventilation fan 101, a signal to be controlled such as a temperature in the flow path 100 used for normal control of the ventilation fan 101, and 115 for normal control operation from outside such as remote operation used for normal control. Stop input signal, 116 is a forced rotation speed setting signal from the outside such as remote operation used for normal control, 113 is an external force such as pressure acting on the flow path 100 used for judgment for switching between normal control and protection control, or an external force such as air volume Is the state quantity.

  The ventilating fan operation control device 201 controls the temperature and the like, and the pressure wind shut-off device open / close command function 201a that issues an open / close command signal to the pressure wind shut-off device 110 when the ventilation fan 101 is operated / stopped in normal control. A control function 201b is provided that obtains the input of the target signal 114, calculates the necessary rotational speed of the ventilation fan 101, and outputs the required rotational speed to the speed control device 120. Further, the ventilation fan protection device 202 obtains a pressure acting on the flow path 100 or a state quantity of the external force 113 such as an air volume, and performs a judgment function for switching between normal control and protection control, and protection control prioritizing normal control. A pressure wind shut-off device open / close command function 202a for issuing an open / close command to the pressure wind shut-off device 110 is provided. In addition, the auxiliary machine panel 130 receives an input of an open / close signal from the pressure wind shut-off device open / close command function 201a or the pressure wind shut-off device open / close command function 202a, and opens to the driver 112 of the pressure shut-off device 110. -Supply closing power.

  The ventilation fan operation control device 201 receives signals from the control target signal transmitter 114, the operation / stop command signal transmitter 115, the set rotational speed transmitter 116 that transmits the set rotational speed, and the rotational speed transmitter 111. Then, an open / close command signal of the pressure wind blocker 110 and a set rotation speed signal of the ventilation fan 101 are generated, and the respective signals are set and rotated from the pressure wind blocker open / close command signal transmitter 201a to the auxiliary panel 130. A number is transmitted from the number transmitter 201b to the speed control device 120. The ventilation fan protection control device 202 receives an external force state quantity signal from the external force state quantity transmitter 113, generates an open / close command signal for opening / closing the pressurized air shut-off device 110, and transmits it to the auxiliary panel 130. The auxiliary panel 130 receives the opening / closing command signal from the ventilation fan operation control device 201 or the opening / closing command signal from the ventilation fan protection control device 202, and receives the opening / closing command signal from the opening / closing power transmitter 130a. Opening / closing power (current) is supplied to the electric motor 112 that drives the pressure wind blocking device 110. Further, the speed control device 120 receives the set rotation speed signal from the set rotation speed transmitter 201b of the ventilation fan operation control device 201, and the frequency power is set so that the rotation speed of the electric motor 103 of the ventilation fan 101 becomes the set rotation speed. (Current) is output to the electric motor 103.

  In the control flow shown in FIG. 3, in step ST1, the ventilation fan 101 is operated under normal control, that is, operation control is performed so that the rotation speed of the ventilation fan 101 becomes the set rotation speed. In step ST2, in this state, the external force state quantity (pressure, air volume, etc.) B from the external force state quantity transmitter 113 is compared with a specified value to determine whether the external force state quantity B is within the allowable specified value range. If the value is greater than or equal to the specified value or less than the specified value (outside the specified value range), the process proceeds to step ST3. In step ST3, ventilation fan protection control is started, and the process proceeds to step ST4. In step ST4, the pressure wind blocking device 110 is closed, and the process proceeds to step ST5. In this step ST5, the external force state quantity B from the external force state quantity transmitter 113 is compared with the specified value, and it waits for the external force state quantity B to be within the specified value range. , The pressure wind blocker 110 is opened, the process proceeds to step ST7, and the ventilation fan protection control is terminated.

  In the above conventional ventilation fan operation control device, when the operation of the ventilation fan 101 is continued even if the pressure air blocking device 110 is closed and the flow path 100 is blocked, the operation point of the ventilation fan 101 is the deadline operation with zero air volume. It becomes. In this case, in the “air volume-shaft power operation characteristics” of the ventilation fan, when the shaft power exceeds or falls below the rated shaft power of the electric motor 103, the following two correspondences (1) and (2) are satisfied. Divided.

(1) When the axial power of the ventilation fan 101 exceeds the rated axial power of the electric motor 103 When the axial power of the ventilation fan 101 exceeds the rated axial power of the electric motor 103, the electric motor 103 is overloaded and continued. I can't drive. In order to continue operation without stopping the operation of the ventilation fan 101, the following measures are required.
-As shown in FIG. 4, the bypass flow path 106 provided with the damper 108 is installed.
When the pressurized air shut-off device 110 is closed and the flow path 100 is shut off, the damper 108 is opened to switch the air blowing path to circulate air and avoid the rated cutoff operation of the ventilation fan 101.
When the blade type of the rotor blade 102 of the ventilation fan 101 is a fixed blade, the rotational power of the rotor blade 102 is reduced by controlling the engine speed, and the shaft power is forcibly reduced to an allowable range by reducing the air volume and the total pressure.
When the blade type of the rotor blade 102 of the ventilation fan 101 is a movable blade system, the shaft power is forcibly reduced to an allowable range by reducing the air volume and the total pressure by changing the blade angle.

(2) When the axial power of the ventilation fan is lower than the rated axial power of the electric motor 103 When the axial power of the ventilation fan 101 is lower than the rated axial power of the electric motor 103, the electric motor 103 is not overloaded. Continuous operation is not restricted. However, because the deadline operation is a state in which the airflow is greatly disturbed and forcedly circulated inside the ventilation fan 101, the cause of the bearings and the like being deteriorated due to adverse effects such as imbalance of fluid force and increased vibration This is not preferable. Therefore, it is necessary to take measures such as setting a time limit.

The above conventional measures have the following problems.
Since it is necessary to close the pressure air blocking device 110 every time airflow (wind) enters the flow path 100 from the outside, the inflow of the airflow from the outside and the decrease in the influence of the airflow are detected in a controlled manner. It is necessary to control the opening and closing of the pressure wind blocking device 110 with a margin.
-Since the flow path 100 will be in the completely interrupted state when the pressure wind blocking device 110 is closed, the ventilation function is completely stopped.
-The flow path 100 cannot be blocked when the pressure wind blocking device 110 is erroneously operated or fails. In this case, the ventilation fan 101 is damaged depending on the degree. The following problems occur from the direction of airflow.

(A) When excessive airflow enters in the reverse flow direction As shown in FIG. 5, at time t2, the ventilation fan 101 normally rotates in the direction indicated by the arrow A and sends the airflow in the forward flow direction indicated by the arrow B. When the airflow in the reverse flow direction indicated by arrow C enters, the operating point (air volume, pressure) of the ventilation fan 101 moves in the closing direction, and the required shaft power also changes depending on the characteristics of the ventilation fan 101. Further, when the air flow becomes stronger at times t3 and t4, the inside of the ventilation fan 101 enters a region where it flows backward as indicated by an arrow D, and the shaft power of the electric motor 103 reaches or exceeds the rated shaft power value in succession, and overload current To the state. In this overload state, the electric circuit switch is opened by the electric circuit protection device, and thereafter, the rotating body of the ventilation fan 101 reverses in the E direction in an unconstrained manner according to the magnitude of the airflow, and the runway rotational speed is ( Saturation speed at which the ventilation fan 101 is rotated by the airflow) is reached.

  When the reverse rotation speed of the ventilation fan 101 becomes excessive and the runaway rotation speed is reached, excessive centrifugal force is generated in the rotating portion, causing damage beyond the allowable strength of the rotating blade 102 and the mounting portion of the rotating blade 102. May cause damage to the bearing, damage to the rotating body due to excessive vibration when the rotational speed of the main shaft matches the natural frequency.

(B) When excessive airflow enters in the positive flow direction As shown in FIG. 6, the ventilation fan 101 normally rotates in the direction indicated by arrow A and sends the airflow indicated by arrow B to arrow D at time t2. As shown, when an air flow (wind) enters in the forward flow direction, the operating point (air volume, pressure) of the ventilation fan 101 moves in the excessive air volume direction, and the required shaft power also changes depending on the characteristics of the ventilation fan 101. Further, when the air current becomes stronger at times t3 and t4, the forced rotational force due to the air current starts to act as a rotational force on the ventilation fan 101, and when it becomes significant, the electric motor 103 starts to work as a generator. The generated power starts reverse power transmission (regeneration) through the switch. If the device does not allow regeneration, the circuit switch is opened by the protective device, and then the rotating body of the ventilation fan 101 overrotates unconstrainedly, and the runaway rotational speed (saturation rotation in which the ventilation fan 101 is rotated by the airflow) Number).

  When the rotational speed of the ventilation fan 101 becomes excessive, an excessive centrifugal force is generated in the rotating part, which may cause damage beyond the allowable strength of the rotating blade 102 or the mounting part of the rotating blade 102, Or the rotational speed of the main shaft matches the natural frequency, leading to damage of the rotating body due to excessive vibration.

  In addition, even if the excessive air flow entering is in the reverse flow direction or in the forward flow direction, if the electric circuit switch is opened, the excessive air flow will stop and the ventilation fan 101 can be operated by the speed control device. Even in such a case, the electric circuit switch must be closed to reset the speed control device, which may hinder rapid restart of operation. Furthermore, when an excessive air flow occurs repeatedly, the circuit switch is repeatedly opened and closed, reducing the life of the circuit switch. In addition, in order to avoid problems caused by erroneous operation or failure of the pressure wind blocker 110, it is necessary to provide a backup facility for the pressure wind blocker 110 (duplication of the pressure wind blocker 110, etc.).

  FIG. 7A is a front view of a check damper as the pressure wind blocking device 110, and FIG. 7B is a cross-sectional view taken along line AA. The pressure air blocking device 110 has a configuration in which a plurality (three in the figure) of valve bodies 132 are arranged in the front rectangular body 101 at predetermined intervals in the vertical direction. The valve body 132 is fixed to the valve body shaft 133, and both ends of the valve body shaft 133 are rotatably supported by bearings 134 and 134 attached to the body 131. When a fan wind generated by the ventilation fan or an air flow in the same direction as the fan wind (a normal wind) enters a wind path installed in a ventilation fan (not shown), the valve element 132 is as shown by an arrow B in FIG. Rotates to the position indicated by the broken line. When there is no wind in the air passage, the valve body 132 rotates in the direction opposite to the arrow B due to its own weight, and becomes a closed position indicated by a solid line in FIG. When the reverse wind enters the air passage, the valve element 132 comes into contact with the valve seat 135 with a pressure corresponding to the wind pressure. Thereby, the reverse wind pressure does not act on the ventilation fan 101.

  FIG. 8A is a front view of a pressure wind blocking device having a forced opening / closing mechanism (here, a forced switching mechanism including an electric motor) as the pressure wind blocking device 110, and FIG. 8B is a cross-sectional view taken along line AA. is there. The pressure air blocking device 110 has a configuration in which a plurality (three in the figure) of valve bodies 132 are arranged in the front rectangular body 131 at predetermined intervals in the vertical direction. The valve body 132 is fixed to the valve body shaft 133, and both ends of the valve body shaft 133 are rotatably supported by bearings 134 and 134 attached to the body 131. One end of a valve element opening lever 136 is fixed to one end of each valve element shaft 135, and the other end of each valve element opening lever 1366 is pivotally attached to a valve element opening link 137. Reference numeral 138 denotes an electric motor. A drive lever 140 is fixed to one end of a rotating shaft 138 a of the electric motor 138, and one end of the drive lever 140 is pivotally attached to one end of a valve body opening link 137. Yes.

  In the pressure wind shut-off device 110 having the above-described configuration, the valve opening degree link 137 is moved as indicated by the arrow D by starting the electric motor 138 and rotating the drive lever 140 as indicated by the arrow C. The body 132 is rotated about the valve body shaft 133 to open and close the pressurized air blocking device 110. When a reverse wind enters the air path, it is detected and the electric motor 138 is activated to close the pressurized wind blocker 110, so that the reverse wind pressure does not act on the ventilation fan.

  However, the method of suppressing the reverse wind pressure by providing the pressure wind shut-off device 110 as the check damper or the forced opening / closing damper as described above has the following problems.

(1) Problems due to the installation of the pressure wind blocking device 110 that is a check damper The structure of the pressure wind blocking device 110 that is the check damper shown in FIG. 7 is a structure that does not allow the back wind when the damper is closed. That is, the valve seat 135 part of the valve body 132 is joined (contacted) at the time of closing to ensure the sealing performance. Further, when there is no wind on both the normal wind side and the reverse wind side, the valve element 132 is naturally in the closed position indicated by the broken line in FIG. Such a structure has the following problems.

・ Problem 1
When an excessive head wind is generated in a short time as shown by an arrow E in FIG. 10, the closing operation of the valve body 132 becomes intense, and the valve body 132 and the valve seat 135 collide violently. Impact sound is generated.

・ Problem 2
When the frequency of back wind is high, the frequency of closing with impact and impact sound increases, and the portion corresponding to the valve seat 135 and the load support portion are consumed and deteriorated, and the probability of failure increases.

・ Problem 3
During normal wind, the valve body 132 swings around the valve body shaft 133 due to fluctuations in the air volume and pressure, so that when the angle of the valve body 132 is in the closing direction, ventilation resistance is generated and the ventilation efficiency of the ventilation fan is increased. Inhibit.

(2) Problems due to installation of the forced air shut-off device 110 that is a forced open / close damper In the case of installation of the forced air shut-off device 110 that is a forced open / close damper having the forced open / close mechanism (electrical, pneumatic, hydraulic, etc.) shown in FIG. Since the closing operation of the valve body 132 is forcibly performed, the opening / closing operation can be controlled to a predetermined opening / closing speed by the forcible opening / closing mechanism. Therefore, since the closing speed of the valve body 132 can be kept constant, there is no problem of closing the valve body 132 with an impact like a check damper. Further, since the valve body opening degree is constantly braked, the valve body can be fixed without swinging against fluctuations in air volume and pressure. However, since the opening / closing operation is performed by the forced opening / closing mechanism, there are the following problems.

・ Problem In order to operate the forced air shut-off device 110, which is a forced open / close damper, the back wind is detected by the instrumentation equipment, the operation of the pressure air shut-off device 110 is controlled by the control device, and the valve element is moved by the forced open / close mechanism. If the instrumentation equipment, control equipment, or driving equipment fails, the pressure wind shut-off device 110 does not reach the normal closing operation and the ventilation fan is affected by back wind. It will lead to destruction.

JP-A-63-138197 Japanese Patent Laid-Open No. 4-175500

  The present invention has been made in view of the above points, and is a fluid machine that can suppress / reduce impacts and impact noise when opening and closing a valve body, and can effectively suppress reverse wind pressure entering a wind passage and acting on a ventilation fan or the like. The purpose is to provide.

  In addition, the present invention reduces the flow efficiency by shutting off the flow path when excessive pressure fluid enters from the outside in the reverse flow direction and forward flow direction inside the flow path where a fluid machine such as a ventilation fan is arranged. And avoiding the occurrence of electrical failures such as overload due to the regeneration of electric power (electric current) from the fluid motor's electric motor that uses this pressure fluid as the source, and the increase in the required power value. A fluid machine that automatically (mechanically) suppresses the pressure wind when the fluid flow that becomes the above-mentioned over-rotation (reverse rotation) enters, and the rotor blade 102 does not reach the dangerous reverse rotation speed even at the maximum reverse wind pressure. A further object of the present invention is to provide a fluid machine operation control device capable of quickly returning a fluid machine to a normal rotational speed and sending a fluid flow when the pressure fluid causing a forced over-rotation phenomenon has left and settled. To do.

  In order to solve the above-mentioned problems, the present invention is arranged in a fuselage, and fluid sucked from a suction port of the fuselage by rotating a rotary wing at a predetermined interval in the circumferential direction on the inner periphery of the fuselage. A fluid machine that is guided by a plurality of guide blades provided along the axial direction of the body and discharges from a discharge port. Each guide blade includes a fixed guide blade and a movable guide blade. The movable inner wing is fixed to the fuselage, and the movable inner wing is rotatable about a rotation axis orthogonal to the axial direction of the fuselage, and a fluid is generated when a reverse fluid flow flows from the discharge port of the fuselage to the suction port. Due to the differential pressure, the movable guide blade rotates from the fully open position, which is the normal position where the blade surface is continuous with the blade surface of the fixed guide blade, to the direction of the fully closed position to change the direction of the reverse fluid flow and hit the rotor blade. Automatic control of movable blade opening held in a position to reduce the pressure of the reverse fluid flow in contact Characterized in that a mechanism.

  In the fluid machine described above, the movable guide blade is fixed to the rotating shaft, and integrally rotates around the rotating shaft. A fluid resistance is generated according to the rotating angle, and the fluid resistance is at the fully open position. It is characterized by having a characteristic that is minimum and maximum in the fully closed position.

  Further, the present invention is characterized in that, in the fluid machine, the movable blade opening automatic control mechanism returns the movable guide blade to the normal position during the positive fluid flow, and efficiently converts the positive fluid flow sent from the rotor blade. And

  According to the present invention, in the fluid machine described above, the fixed guide blade and the movable guide blade are disposed between the body and the inner casing disposed in the body, and the rotation shaft of the movable guide blade includes the body and the inner casing. And is rotatably supported by bearings provided at both through portions.

  In the fluid machine described above, the one end of the link member is fixed to the body side end of the rotating shaft of each movable guide blade, and the other end of the link member is always fixed by the movable blade opening automatic control mechanism. The movable guide vane is biased to rotate to a normal position with a predetermined force.

  Further, in the fluid machine described above, the mounting position of the rotary shaft of the movable guide vane is such that when the reverse fluid flow is generated, the center of the side of the movable guide vane is arranged so that a rotational moment is generated around the rotary shaft due to the difference in pressure receiving area. It is deviated from.

  Further, the present invention is characterized in that the fluid machine is provided with an initial motion power generation means for applying an initial motion power to the movable guide vanes in a normal position when the reverse fluid flow is generated.

  In the fluid machine according to the present invention, the initial rotational power generation means is a gap provided in an adjacent portion of the movable guide vane of the fixed guide vane or an adjacent portion of the fixed guide vane of the movable guide vane. .

  The present invention also relates to a fluid machine operation control apparatus that controls the operation of a fluid machine that is disposed in a flow path and that sends a fluid flow from one of the flow paths to the other by rotating a rotor blade with a driving machine. The control device includes a control device, a driving operation control device, and a protection control device. The speed control device normally outputs power for rotating the rotor blades at a set rotational speed commanded from the driving operation control device to the driving machine. Function and a free-run control function that allows the rotating body including the rotor blades of the fluid machine to freely rotate by removing the power output to the drive machine, and the operation control device sets a rotational speed signal to the speed control device during normal control. The protection control device is equipped with a normal control instruction function for rotating the rotor blade at a set rotational speed, and the protection control device is in a free-running state when the external pressure fluid flow outside the allowable range enters the flow path. In Comprising a free run instruction function to, characterized by using a fluid machine according to any one of claims 1 to 8 to the fluid machine.

  In the fluid machine operation control device according to the present invention, when the protection control device instructs the speed control device to perform free run, the protection control start notification function that notifies the operation control device that the protection control has started, A protection control end notification function for notifying the end of protection control when the external pressure fluid acting on the passage falls within the allowable range is provided.

  According to the present invention, each guide vane includes a fixed guide vane and a movable guide vane. When a reverse fluid flow flowing from the discharge port of the fuselage to the suction port flows, the movable guide vane is caused by the generated fluid differential pressure. The surface is rotated from the fully open position, which is a normal position that is continuous with the blade surface of the fixed guide blade, to the fully closed position to change the direction of the reverse fluid flow, thereby reducing the pressure of the reverse fluid flow contacting the rotor blade. Therefore, even when a strong reverse fluid flow flows in, the reverse fluid pressure contacting the rotor blade can be greatly reduced, and the reverse rotation can be suppressed at a high speed leading to breakage of the rotor blade.

  Further, according to the present invention, the speed control device normally outputs the power for rotating the rotor blades at the set rotational speed commanded from the operation control device to the drive machine, and the power output to the drive machine. Equipped with a free-run control function that allows the rotating body including the rotor blades of the lost fluid machine to rotate freely, and the operation control device sends a set rotation speed signal to the speed control device during normal control to rotate the rotor blades at the set rotation speed. A normal control instruction function is provided, and the protection control device has a free run instruction function that causes the speed control device to put the rotating body in a free run state when an external pressure fluid flow outside the allowable range enters the flow path. When excessive pressure fluid enters from the outside in the reverse flow direction and forward flow direction inside the passage, the flow of the fluid machine is reduced without blocking the flow path and reducing the fluid flow efficiency. Target To avoid the occurrence of a failure, further away an external pressure fluid flow, can provide a fluid machine operation control system which quickly fluid machine with calm time can send a fluid flow is returned to the speed of normal.

  According to the present invention, the protection control device instructs the speed control device to rotationally brake the rotating body when the rotating body is in a free-run state and the rotational speed of the rotating body is equal to or higher than a predetermined rotational speed. With the free-run braking command function, it is possible to prevent damage to the rotating body due to over-rotation in the free-running state of the rotating body, and at the time when the external pressure fluid tributary leaves and settles, the fluid machine is quickly The fluid flow can be sent back to the rotational speed.

FIG. 1 is a diagram showing a schematic configuration example of a conventional ventilation fan. FIG. 2 is a diagram showing a system configuration of a conventional ventilation fan operation control device. FIG. 3 is a diagram showing a control flow of the ventilation fan operation control device of FIG. FIG. 4 is a diagram showing a case where a bypass channel is installed in the channel. FIG. 5 is a view for explaining a case where an air flow enters from the outside in a reverse flow direction in an air passage in which a conventional ventilation fan is arranged. FIG. 6 is a diagram for explaining a case where airflow enters the airflow path in which the conventional ventilation fan is disposed from the outside in the positive flow direction. FIG. 7 is a diagram showing a configuration example of a conventional pressurized air blocking device (non-return damper). FIG. 8 is a diagram showing a configuration example of a conventional pressurized air blocking device (forced opening / closing damper). FIG. 9 is a view for explaining the operation of the valve body of the check damper. FIG. 10 is a view for explaining the operation of the check damper due to the reverse wind of the valve body. FIG. 11 is a diagram showing a system configuration example of the ventilation fan operation control device according to the present invention. FIG. 12 is a diagram showing a control flow of the ventilation fan operation control device of FIG. FIG. 13 is a diagram for explaining a free-run transition standard of the ventilation fan operation control device. FIG. 14 is a diagram showing a system configuration example of the ventilation fan operation control device according to the present invention. FIG. 15 is a diagram showing a control flow of the ventilation fan operation control device of FIG. FIG. 16 is a diagram for explaining a case where airflow enters the airflow path in which the ventilation fan is disposed from the outside in the positive flow direction. FIG. 17 is a diagram for explaining a case where airflow enters the airflow path in which the ventilation fan is arranged from the outside in the backward flow direction. FIG. 18 is a diagram showing a schematic configuration of a ventilation fan provided with fixed guide vanes. FIG. 19 is a diagram showing a schematic configuration of a ventilation fan according to the present invention provided with a fixed guide vane and a movable inner vane. FIG. 20A is a diagram for explaining the operation of the guide vanes. FIG. 20B is a diagram for explaining the operation of the guide vanes. FIG. 21 is a diagram showing a configuration example of the guide vanes of the ventilation fan according to the present invention. FIG. 22 is a diagram showing a configuration example of a ventilation fan according to the present invention.

  Hereinafter, embodiments of the present invention will be described in detail. FIG. 11 is a diagram showing a system configuration of a ventilation fan operation control device as a fluid machine operation control device according to the present invention. In this embodiment, a ventilation fan is described as an example of a fluid machine. However, the present invention can be applied to a fluid machine operation control device that is disposed in a flow path and sends a fluid from one end to the other end of the flow path. As shown in FIG. 11, the fluid machine operation control device includes a ventilation fan operation control device 1, a ventilation fan protection control device 2, a speed control device 3, and a mechanical automatic reverse wind pressure suppression device 4. Operation control of the arranged ventilation fan 10 is performed. Here, the ventilation fan 10 is a ventilation fan having a general fixed wing. The ventilation fan operation control device 1 is a device that performs normal operation control of the ventilation fan 10, and the ventilation fan protection control device 2 is a device that protects the ventilation fan 10 and the like. The ventilation fan protection control device 2 is the same type of control device, but is divided here for easy understanding of the function.

  The ventilation fan operation control device 1 transmits a control target detection signal such as the temperature in the air passage 11 from the control target signal transmitter 31, a driving / stop command signal from the driving / stop command signal transmitter 32, and a set rotational speed transmission. Receiving the set rotational speed signal from the device (distant operation unit) 33 and the measured rotational speed signal of the ventilation fan 10 from the rotational speed transmitter 27, generating the set rotational speed signal of the ventilation fan 10, and setting the rotational speed transmitter The set rotational speed signal is transmitted from 1a to the speed control device 3.

  The ventilation fan protection control device 2 includes a free-run command signal transmitter 2a, a restart command (acceleration) signal transmitter 2b, a protection control start signal transmitter 2c, and a protection control end signal transmitter 2d, and transmits an external force state quantity. A state quantity detection signal of an external force such as pressure or air volume from the air conditioner 37, an actual speed signal of the ventilation fan 10 from the speed transmitter 27, an output speed signal from the inverter control section 36, and an inverter output section 35 An electric power (current) signal output to the electric motor 17 is received.

  In addition, the ventilation fan protection control device 2 is provided with the electric motor 17, the speed control device 3, or the like when an electric failure such as regeneration of electric power (current) of the electric motor 17 of the ventilation fan 10 or overload occurs. When it is necessary to protect equipment such as an electric circuit, a free-run command signal is output from the free-run command signal transmitter 2a to the speed control device 3 to perform control to protect the equipment from an electrical failure. Further, the ventilation fan protection control device 2 performs control to maintain a state where the circuit breaker upstream of the power wiring that supplies power to the speed control device 3 is not opened.

  Further, the ventilation fan protection control device 2 informs the ventilation fan operation control device 1 that the protection control has been started via the protection control start signal transmitter 2c, and interrupts normal control, or an external force state quantity transmitter 37. After confirming that the condition for enabling the free run is completed from the pressure or the external force state quantity detected in step 3, the restart command signal is sent from the restart command signal transmitter 2b to the speed control device 3. The ventilation fan 10 is normally operated by the function of returning the electric motor 17 of the ventilation fan 10 to the operation at the set rotation speed at the time of normal control or the measured rotation speed signal of the ventilation fan 10 detected by the rotation speed transmitter 27. It has a function of detecting that the rotational speed has been returned to the time of control and outputting a protection control end signal to the ventilation fan operation control device 1 via the protection control end signal transmitter 2d.

  The speed control device 3 includes an inverter output unit 35, receives the set rotational speed signal of the set rotational speed transmitter 1 a of the ventilation fan operation control device 1, and the inverter control unit 36 converts the rotational speed of the ventilation fan 10 to the set rotational speed. Is generated and output to the inverter output unit 35. The inverter output unit 35 receives the frequency signal and supplies electric power (current) having a frequency that reaches the set rotational speed to the electric motor 17 of the ventilation fan 10. As a result, the rotor blade 15 of the ventilation fan 10 rotates forward (rotates in the direction indicated by arrow A), passes through the casing of the ventilation fan 10, and extends from one end to the other end of the air passage 11 connected to the casing. As shown by arrow B, wind (airflow) is sent.

  Further, the speed control device 3 receives the free run command signal from the free run command signal transmitter 2 a of the ventilation fan protection control device 2 and eliminates the power supplied from the inverter output unit 35 to the electric motor 17 of the ventilation fan 10. A state where the rotating body of the ventilation fan 10 including the rotating portion of the electric motor 17 can be freely rotated, that is, a free-run function for setting the rotating body to a free-run state is provided. The speed control device 3 receives the restart command signal from the restart command signal transmitter 2 b of the ventilation fan protection control device 2 and supplies the output power of the inverter output unit 35 to the electric motor 17 of the ventilation fan 10.

  The mechanical automatic reverse wind pressure suppression device 4 allows the reverse wind to enter so that excessive reverse wind pressure in the direction indicated by the arrow C enters the air passage 11 and the ventilation fan 10 does not over-rotate (reverse) beyond the allowable value. It is a device that automatically operates according to the wind pressure and sets the ventilation resistance according to the wind pressure. As will be described in detail later, a mechanism that obtains the wind pressure and operates mechanically, that is, power and control for the operation from the outside. It has a mechanism that is not required. In FIG. 11, an arrow D indicates the direction of the positive wind.

  FIG. 12 is a diagram showing a control flow of the ventilation fan operation control device. First, in step ST11, the normal control of the ventilation fan 10, that is, the speed control device 3 has a frequency power (the frequency at which the rotation speed of the ventilation fan 10 becomes the set rotation number from the set rotation number transmitter 1a of the ventilation fan operation control device 1). Current) is supplied from the inverter output unit 35 to the electric motor 17 of the ventilation fan 10. In step ST12, the actual rotational speed of the ventilation fan 10 from the rotational speed transmitter 27 is set to N, and as shown in FIG. 13 (a) and FIG. The (current) value range is calculated to obtain a low power (current) side specified value AL and a high power (current) side specified value AH.

  In step ST13, the electric power value (current value) supplied from the inverter output unit 35 to the electric motor 17 is A, and “free run” transition reference processing, that is, detection of the regenerative current itself, or current to avoid regenerative. The detection of the value condition A <AL, and the detection of the current value condition A> AH that should avoid overload (overcurrent) are checked. If either one is satisfied (OR), the process proceeds to step ST14. In step ST14, protection control of the ventilation fan 10 is started, and the process proceeds to step ST15. At the same time, the normal control of the ventilation fan 10 is interrupted.

  In step ST15, a free-run command signal is transmitted from the free-run command signal transmitter 2a of the ventilation fan protection control device 2 to the speed control device 3, and the process proceeds to step ST16. At step ST16, the external force state quantity transmitter 37 detects the external force state quantity (pressure or air volume) B with a prescribed value, and waits for the external force state quantity B to return to the prescribed value. When returning to the inside, that is, as shown in FIG. 13C, when the external force state quantity B falls within the range between the low pressure side external force reference value (−) BL and the high pressure side external force reference value (+) BH, the process proceeds to step ST17. To do.

  In step ST17, the rotation direction of the ventilation fan 10 is detected, and the flow is branched depending on the rotation direction. If the rotation direction is reverse, the process proceeds to step ST18. In step ST18, after detecting that the rotation speed (reverse rotation) of the ventilation fan 10 has decelerated to within the specified value, the process proceeds to step ST20, the free run is terminated, and then the process proceeds to step ST21. In step ST21, the ventilation fan protection control device 2 outputs a restart command signal from the restart command signal transmitter 2b to the speed control device 3 to restart the ventilation fan 10, and the process proceeds to step ST23. If the rotation direction of the ventilation fan 10 is normal in step ST17, the process proceeds to step ST19, the free run is terminated, and then the process proceeds to step ST22. In step ST22, even if the ventilation fan 10 is rotating, it is restarted from the rotational speed, and the process proceeds to step ST23. In step ST23, the ventilation fan 10 is accelerated, and the process proceeds to step ST24. In step ST24, control is performed to set the rotational speed of the ventilation fan 10 to the set rotational speed, and the control returns to normal control, and the process proceeds to step ST25 to end the ventilation fan protection control.

  Some speed control devices 3 are provided with a power regeneration function. In this case, the free run movement reference value on the regeneration side (rotating body side) is set to a regenerative capacity, and the forward rotation side excess It is also possible to collect power (electric power) as much as possible during rotation. In this case, in step ST13, detection of the regenerative current is excluded from the reference, and AL is set as a negative current value (current value that can be regenerated).

  In addition, when the number of rotations that can be restarted at the time when the free run ends is limited on the low rotation number side, the regenerative braking is performed in order to quickly stop the rotor blades 15 of the ventilation fan 10 that is freely rotating. Thus, the rotation of the rotating body composed of the rotating portions of the rotary blade 15 and the electric motor 17 can be stopped.

  In addition, in this case, if the state of fluctuation of the state quantity of pressure or air volume is so great that it fluctuates greatly in and out of the specified value range, it may fall into a hunting phenomenon in which the transition of protection control and its termination are repeated. As a means for avoiding the hunting phenomenon, it is possible to add a measure such as setting a holding time from the free run command to the confirmation of the external force state quantity for returning to the normal control.

  FIG. 14 is a diagram showing a system configuration example of the ventilation fan operation control device according to the present invention. The ventilation fan operation control device shown in FIG. 14 differs from the ventilation fan operation control device shown in FIG. 11 in that the ventilation fan operation control device shown in FIG. 14 sends a free-run braking command signal to the ventilation fan protection control device 2. When the rotational speed of the rotating body of the ventilation fan 10 due to free run returns to within the specified range, a free run braking command signal is transmitted to the speed control device 3 as the end of the free run. The rest is the same as the ventilation fan operation control device of FIG.

  FIG. 15 is a diagram showing a control flow of the ventilation fan operation control device shown in FIG. First, in step ST31, normal control of the ventilation fan 10 is performed. In step ST32, the measured rotational speed from the rotational speed transmitter 27 is set to N, and the low power side defined value AL and the high power side defined value AH within the allowable power (current) value range for the measured rotational speed N are calculated and obtained. (See FIGS. 13A and 13B), the process proceeds to step ST33. In step ST33, the electric power value (current value) supplied from the inverter output unit 35 to the electric motor 17 is A, and the “free-run” transition reference process, that is, the detection of the regenerative current itself, or the current that should be avoided. The detection of the value condition A <AL and the detection of the current value condition A> AH that should avoid overload (overcurrent) are checked. If either one is satisfied (OR), the process proceeds to step ST34. In step ST34, protection control of the ventilation fan 10 is started, and the process proceeds to step ST35. At the same time, the normal control of the ventilation fan 10 is interrupted.

  In step ST35, a free-run command signal is transmitted from the free-run command signal transmitter 2a of the ventilation fan protection control device 2 to the speed control device 3, and the process proceeds to step ST36. In step ST36, in order to prevent the hunting phenomenon in which the transition of the protection control and the end thereof are repeated, a predetermined free run holding time is set by a timer or the like, and the process moves to step ST37 after the free run holding time has elapsed. In step ST37, the external force state quantity B detected by the external force state quantity transmitter 37 is compared with a specified value, and is returned to the specified value, that is, the external force state quantity B is equal to the low-pressure side external force reference value (-) BL. It is determined whether or not the pressure has returned during the high-pressure side external force reference value (+) BH (see FIG. 13C).

  In step ST38, the free run ends and the process proceeds to step ST39. In step ST39, the rotation direction of the ventilation fan 10 is detected, and the flow is branched depending on the rotation direction. If the rotation direction is reverse, the process proceeds to step ST40. In step ST40, a free-run braking command signal transmitter 2e of the ventilation fan protection control device 2 transmits a free-run braking command signal to the speed control device 3, and the rotational speed braking (deceleration operation) of the ventilation fan 10 that is rotating in inertia is performed. ) And move to step ST42. In step ST42, after detecting that the rotation speed of the ventilation fan 10 has decelerated to within a specified value, the process proceeds to step ST43. In step ST43, the restart command signal transmitter 2b of the ventilation fan protection control device 2 outputs a restart command signal to the speed control device 3 to restart the ventilation fan 10, and the process proceeds to step ST44. If the rotation direction of the ventilation fan 10 is normal in step ST39, the process proceeds to step ST41. In step ST41, even if the ventilation fan 10 is rotating, it is restarted from the rotational speed, and the process proceeds to step ST44.

  In step ST44, the ventilation fan 10 is accelerated, and the process proceeds to step ST45. In step ST45, control is performed to set the rotational speed of the ventilation fan 10 to the set rotational speed, and the control returns to normal control, and the process proceeds to step ST46 to end the ventilation fan protection control.

In FIG. 16, the ventilation fan 10 rotates at the rated rotation speed in the direction of arrow A, and 100% of the positive wind flows in the direction of arrow B in the wind path 11 in the same direction as the arrow B direction. When the airflow enters, the pressure applied to the ventilation fan 10 (pressure applied to the fan) (Pa), the airflow of the ventilation fan 10 (fan airflow) (m ³ / min), the rotation speed of the ventilation fan 10 (fan rotation speed) (Min ⁻¹ ), the axial power (kW) of the ventilation fan 10, the torque (N · m) of the ventilation fan 10, and the fan current value (A) that is the current value of the electric motor 17 of the ventilation fan 10 is shown. FIG. As shown in the figure, the pressure (Pa) applied to the fan increases from time t1 to time t2, time t3, and time t4 on the negative pressure side, increases at time T5, decreases at time t6, time t7, and time t8. It has converged at t9.

The fan air volume (m ³ / min) is in a normal state at time t1, and increases with time t2 and time t3 when the intensity of pressure applied from the outside to the positive flow side of the fan increases. At the same time, the fan shaft power necessary for the ventilation fan 10 acts in a direction that is reduced by applying pressure to the negative side from the outside. The fan torque (N · m) is also reduced in the same manner as the fan shaft power because the fan speed is maintained constant. The fan current value (A) also acts in the direction of decreasing as the fan shaft power (kW) decreases. Here, when reaching a point G lower than the lower limit specified current value (AL), the normal control is interrupted, the protection control is started, and the ventilation fan 10 enters a free-run state. While in the free-run state, the rotating body of the ventilation fan 10 is in an unconstrained state, rotates at a runaway speed corresponding to the pressure (Pa) applied to the fan, increases at time t4, and at point E at time t5. Maximum. Similarly, it decreases in accordance with the decrease in pressure (Pa) applied to the fan at time t6 and time t7. Since power supply to the ventilation fan 10 is stopped from time t3 to time t7 under protection control, the fan shaft power (kW), fan torque (N · m), and fan current value (A) are zero. During this time, it is possible to continue without opening the power switch by the free-run function of the inverter. When the pressure on the fan, which is the external force state quantity 37, falls below the specified value at point F, the protection control is terminated and the normal control is restored. Whatever has the rotational speed is restarted and re-accelerated by supplying power from the inverter, and returns to the specified rotational speed. At time t8, the pressure (Pa) exerted on the fan decreases, and all state quantities return to the rated value or + 100% at time t9.

FIG. 17 shows that the ventilation fan 10 rotates at the rated rotational speed in the direction of arrow A, and 100% of the normal wind in the direction of arrow B flows through the air path 11 in the direction opposite to the normal wind indicated by the arrow C. Pressure of the ventilating fan 10 (pressure) (Pa), the air volume of the ventilation fan 10 (fan air volume) (m ³ / min), and the rotation speed of the ventilation fan 10 (fan rotation speed) (Min ⁻¹ ) A diagram showing the relationship between the axial power (kW) of the ventilation fan 10, the torque (N · m) of the ventilation fan 10, and the fan current value (A) that is the current value of the electric motor 17 of the ventilation fan 10. It is. As shown in the figure, the pressure (Pa) exerted on the fan increases from time t1 to time t2, time t3, and time t4 on the positive pressure side, increases at time t5, decreases at time t6, time t7, and time t8. Converge at t9.

The fan air volume (m ³ / min) is in a normal state at time t1, and time t2 and time 3 at which the intensity of the wind pressure (pressure (Pa) applied to the fan) applied from the outside to the backflow side of the ventilation fan 10 increases. It increases as At the same time, the fan shaft power necessary for the ventilation fan 10 acts in a direction to increase when wind pressure is applied from the outside. By maintaining the fan rotation speed constant, the fan torque (N · m) also increases in the same manner as the fan shaft power. The fan current value (A) also acts in the direction of increasing as the shaft power increases. Here, when the fan current value reaches a point K exceeding the upper limit side specified current value (AH), the normal control is interrupted, the protection control is started, and the ventilation fan 10 enters a free-run state. While in the free-run state, the rotating body of the ventilation fan 10 is in an unconstrained state. Here, when the mechanical automatic back wind suppression control device 4 is provided, the ventilation fan 10 has a runaway rotational speed corresponding to the pressure reduced by the mechanical automatic wind pressure suppression device 4 from the pressure (Pa) applied to the fan. At time t4, and increases at time H at time t5. Similarly, the pressure decreases as time t6, time t7, and the pressure applied to the ventilation fan 10 decrease. Since power supply to the ventilation fan 10 is stopped from time t3 to time t7 under protection control, the fan shaft power, fan torque, and fan current value are 0. During this time, the free-run function of the inverter output unit 35 It is possible to continue without opening the power switch. When the pressure applied to the ventilation fan 10, which is the external force state quantity 37, falls below the specified value at point J, the protection control is terminated and the normal control is restored. Although the number of revolutions is arbitrary, it is restarted and re-accelerated by supplying power from the inverter output unit 35 to return to the prescribed number of revolutions. At time t8, the pressure (Pa) exerted on the fan decreases, and all state quantities return to the rated value or + 100% at time t9. Further, by adjusting the ventilation resistance value of the mechanical automatic reverse wind pressure suppression device 4, the rotation speed on the reverse side of the ventilation fan 10 can be suppressed to 0 or an extremely low speed range.

  18 and 19 are views showing the principle of the reverse rotation speed suppression mechanism of the ventilation fan according to the present invention. As shown in FIG. 18, in the ventilation fan 10, guide vanes 14 are disposed between the inner casing 13 and the body 12 on the outer periphery of the inner casing 13 at predetermined intervals in the axial direction. The counter pressure air flowing into the air passage 11 (see FIGS. 11 and 14) flows linearly from the discharge side of the body 12 as indicated by an arrow C1. Then, the pressure wind changes direction along the inclined surface of the guide blade 14 and is incident at an angle (an angle closer to 90 °) than that incident on the blade surface of the rotary blade 15. As a result, the power of the pressure wind is efficiently transmitted to the reverse rotation side based on the same principle as that of the impact type water wheel (Pelton water wheel or the like), so that the runway rotational speed is faster than that on the normal rotation / forward flow side.

  In order to avoid the fast runaway rotational speed due to the reverse pressure wind, here, as shown in FIG. 19, the guide blade 14 is divided into the upstream side and the downstream side of the reverse pressure wind, and the upstream side is the fixed guide blade 14a and the downstream side. The fixed guide vane 14 a is fixedly disposed between the inner casing 13 and the fuselage 12, and the movable guide vane 14 b can rotate between the inner casing 13 and the fuselage 12 around the rotation shaft 16. It is configured. As described above, when the guide wing 14 is divided into the fixed guide wing 14a and the movable guide wing 14b, when the reverse pressure wind flows into the fuselage 12 from the air passage 11 as shown by the arrow C1, the movable guide wing 14b. Is rotated by a predetermined angle about the rotary shaft 16 in the direction indicated by the arrow R1, the reverse pressure wind changes direction along the blade surface of the movable guide vane 14b and makes an acute angle with respect to the blade surface of the rotary blade 15. It will be incident. As a result, the rotational force transmitted in the reverse rotation direction of the rotary blade 15 is reduced, and the reverse runaway rotational speed can be significantly suppressed as compared with the guide blade 14 of FIG.

  FIG. 20 shows the flow of reverse pressure during backwind when the entire guide vane 14 is fixed as shown in FIG. 18 and when it is divided into a fixed guide vane 14a and a movable guide vane 14b as shown in FIG. FIG. 20A shows the case where the entire guide blade 14 is a fixed blade, and FIG. 20B shows the guide blade 14 divided into a fixed guide blade 14a and a movable guide blade 14b. Show the case. As shown in FIG. 20 (a), the pressure flow on the reverse flow side linearly flows in from the discharge port side as indicated by the arrow C1, but the direction is changed along the blade surface of the fixed guide blade 14, and the rotary blade The 15 blade surfaces are incident at a more vertical angle (an angle closer to 90 °) as described above, and are more efficient on the counter-rotating side in the same principle as the impulse type turbine. Power will be transmitted well. When the movable guide vane 14b is rotated by a predetermined angle in the fully closed direction around the rotation shaft 16, the reverse pressure wind changes direction along the blade surface of the movable guide vane 14b as shown in FIG. Thus, the rotational force that is incident on the blade surface of the rotor blade 15 at an acute angle and is transmitted in the reverse rotation direction of the rotor blade 15 is reduced.

  When the force of the blade rear portion of the pressure wind incident on the rotary blade 15 is FC1 and the force of the blade head is FC2, in FIG. 20A, the reverse component of the blade rear portion is FR1, and the reverse component of the blade head is FR2. The rotor blade direction component is FF1 at the blade rear and FF2 at the blade head. Here, the reverse component FR1 and the reverse component of the wing head FR2 are in the same direction, and the reverse component (runaway amount) is approximately the average of FR1 and FR2. In FIG. 20B, the reverse component of the blade rear portion is FR1, the blade head reverse component is FR2, the rotor blade direction component is FF1 at the blade rear portion, and FF2 at the blade head. Here, the reverse components FR1 and FR2 May be smaller than the reverse components FR1 and FR2 of FIG. 20 (a), and the directions may be opposite to each other. Therefore, when the guide vane 14 is divided into the fixed guide vane 14a and the movable guide vane 14b and the movable guide vane 14b is rotated by a predetermined angle with respect to the incident pressure wind, the reverse rotation component (runaway amount) is the entire guide vane 14. Compared with the case where is a fixed wing, it is significantly smaller.

  As described above, the guide wing 14 is divided into the fixed guide wing 14a and the movable guide wing 14b, and the movable guide wing 14b can be rotated around the rotating shaft 16 inside the fuselage 12, thereby generating a difference caused when the back wind flows in. By making the movable guide blade 14b rotate by the pressure and rotate to the angle that changes the blowing direction, the reverse force component can be significantly reduced. At this time, since the movable guide vane 14b has a ventilation resistance according to the rotation angle about the rotation shaft 16, the movable guide blade 14b has a characteristic that the smallest one when fully opened is the largest when fully closed. Thus, during normal wind, the movable guide vane 14b returns to a normal position (a position where the blade surface of the fixed guide vane 14a and the blade surface of the movable guide vane 14b are continuous), and the direction of the air flow blown from the rotary vane 15 is improved. Try to switch well.

  The rotating shaft 16 of the movable guide vane 14b of the guide vane 14 is movable by two bearings provided in the penetrating portion that penetrates the rotating shaft 16, the inner casing 13 and the body 12 as described later (see FIG. 22). The guide blade 14b is pivoted so as to be able to rotate smoothly, and supports the load generated by the differential pressure applied before and after the movable guide blade 14b (wing head and blade rear). The mounting position of the rotary guide 16 of the movable guide vane 14b is shifted (offset) from the center of the side surface, and the movable guide vane 14b is rotated around the rotary shaft 16 due to the difference in pressure receiving area on both sides of the rotary shaft 16 when backflow air is generated. A rotational moment force is generated, and the movable guide vane 14b automatically rotates when the back wind flows.

  FIG. 21 is a diagram illustrating a configuration example of the guide vanes 14. As shown in the drawing, in the state where the movable guide blade 14b is in a normal position where the blade surfaces are continuous with each other with respect to the fixed guide blade 14a, the initial rotational torque is applied to the side portion of the movable guide blade 14b adjacent to the fixed guide blade 14a. A generating gap 14c (a kind of air pocket) is provided. In the state where the movable guide vane 14b is in a proper position and the blade surfaces of the fixed guide vane 14a and the movable guide vane 14b are continuous, even if a backflow occurs, the closing direction of the movable guide vane 14b (arrow R1) Rotation force is not easily generated. Therefore, in order to cause the movable guide blade 14b to quickly start rotating in the closing direction at the time when the backflow air flows in, the initial motion rotational force generating gap 14c is required. The initial rotational force is generated when the movable guide vane 14b receives a backflow parallel to the air path, and the initial rotational force is generated by the backflow of the movable guide vane 14b adjacent to the fixed guide vane 14a. By providing the working gap 14c, a rotational moment force about the rotating shaft 16 is generated in the movable guide blade 14b, and the movable guide blade 14b quickly rotates in the closing direction.

  Here, as shown in the drawing, the mounting position of the rotary shaft 16 of the movable guide vane 14b is shifted (offset) from the center position of the side surface, and the movable guide vane is caused by the difference in pressure receiving areas on both sides of the rotary shaft 16 when the backflow air flows. 14 b has a structure in which a rotational moment force is generated around the rotary shaft 16, and when a backflow air flows, the movable guide blade 14 b automatically rotates around the rotary shaft 16. Further, as shown in FIG. 22, a link mechanism 19 is provided as a treatment so that the plurality of movable guide vanes 14b operate in a unified manner, and the operations of the plurality of movable guide vanes 14b are unified. .

  FIG. 22 is a view showing a side surface (partial cross section) of a ventilation fan with a reverse rotation speed suppression mechanism according to the present invention. As shown in the drawing, the movable guide vane 14b is rotatably supported by bearings 20 and 21, which are fixed to the both ends of the rotating shaft 16 and the through shafts through which the rotating shaft 16 penetrates the inner casing 13 and the body 12. It is pivoted. A link member 23 is attached to the end of each rotating shaft 16 on the body 12 side, and the link member 23 is urged by a movable guide blade opening automatic control mechanism 24 so as to be movable within a movable range ΔL. ing. The movable guide blade opening automatic control mechanism 24 includes a spring member 25, one end of the spring member 25 is attached to the end of the counter-rotating shaft 16 of the link member 23, and the other end is attached to a bracket 26 fixed to the body 12. It is fixed.

  In the movable guide blade opening automatic control mechanism 24, the movable guide blade 14 b of the guide blade 14 is always in the normal position (the blade surface of the fixed guide blade 14 a and the blade surface of the movable guide blade 14 b are continuous by the elastic force of the spring member 25. The movable guide vane 14b is positioned at the normal position when there is no backflow. In this state, when the backflow air flows into the air passage 11 (see FIGS. 11 and 14), the backflow air flows into the initial motion rotational force generation gap 14c of the guide blade 14 and rotates the movable guide blade 14b in the closing direction. An initial rotational force is generated to rotate in the closing direction about the rotation shaft 16. As the movable guide vane 14b rotates, a large amount of backflow air strikes the back surface of the movable guide vane 14b, and the movable guide vane 14b rotates until the rotational moment force generated and the elastic force of the spring member 25 are balanced. To do.

  By making the shape and size of the fixed guide vanes 14a and the movable guide vanes 14b constituting each guide vane 14 and the elastic force of the spring member 25 constituting each movable guide vane opening automatic control mechanism 24 the same, a plurality of movable The guide vanes 14b operate in unison with the backflow, and each movable guide vane 14b rotates at the same rotation angle. In this way, the direction of the backflow to the rotor blade 15 is automatically changed according to the amount of the backflow air flowing into the air passage 11 by a mechanical mechanism such as the movable guide blade opening automatic control mechanism 24. Therefore, the rotational force in the reverse direction of the rotary blade 15 can be suppressed, and the rotary blade 15 can be prevented from rotating beyond the dangerous rotational speed. Further, even if the rotating operation of the rotary blade 15 due to the backflow is intense, the movable guide blade 14b has no colliding portion, so that no impact or closing sound is generated, and no breakage occurs. When a transient rotational displacement speed of the movable guide vane 14b is suppressed, a suppression mechanism such as a shock absorber may be added.

  The mounting position of the movable guide blade opening automatic control mechanism 24 may be independently installed outside the fuselage 12 in consideration of the size and maintenance of the apparatus. Further, the position at which the initial rotational force generating gap 14c of the guide vane 14 is provided is not limited to the fixed guide vane 14a adjacent to the movable guide vane 14b, but may be provided adjacent to the movable guide vane 14b of the fixed guide vane 14. Good. Further, the shape of the initial motion torque generating gap 14c is not limited to the shape shown in FIG. 21, and any shape may be used as long as the backflow air flows into the movable guide blade 14b. There may be. Further, the shape of the movable guide vane 14b itself may be a shape such that the initial rotational force is generated by the countercurrent air. In short, as long as the initial motion torque is generated in the movable guide vane 14b by the generation of the countercurrent air, Any configuration is possible.

  22 is used as the ventilation fan 10 of the fluid machine operation control device of FIGS. 11 and 14, the mechanical automatic reverse wind pressure suppression device 4 is not necessarily required. Although not necessary, by providing the mechanical automatic backwind pressure suppression device 4, it is possible to suppress backwind pressure suppression twice.

  The embodiments of the present invention have been described above. However, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Can be modified. Note that any shape or structure not directly described in the specification and drawings is within the technical scope of the present invention as long as the effects of the present invention are achieved.

  The present invention is a fluid machine operation control apparatus that controls the operation of a fluid machine such as a fan installed in a flow path through which fluid flows, and has a pressure in the reverse flow direction or the forward flow direction in the fluid flow path from the outside. It can be used when wind (airflow) frequently enters and affects the fluid flow by the fluid machine installed in the flow path.

  The present invention provides a ventilation fan installed in a ventilation shaft that ventilates an air passage in which an airflow having a pressure opposite to the blowing direction of the ventilation fan enters, for example, a track tunnel through which a high-speed train passes. Etc., every time a train passes, a reverse wind or a normal wind enters the shaft, and a strong normal wind or a reverse wind pressure acts on the ventilation fan. However, such a ventilation fan is excessively rotated forward or reverse by the pressure. Therefore, it can be used as a device that protects the ventilation fan and power (electric power) supply equipment from damage or destruction.

DESCRIPTION OF SYMBOLS 1 Ventilation fan operation control device 2 Ventilation fan protection control device 3 Speed control device 4 Mechanical automatic reverse wind pressure suppression device 10 Ventilation fan 11 Air passage 12 Body 13 Inner casing 14 Guide vane 14a Fixed guide vane 14b Movable guide vane 14c Initial rotation Force generation gap 15 Rotating blade 16 Rotating shaft 17 Electric motor 19 Link mechanism 20 Bearing 21 Bearing 23 Link member 24 Movable guide blade opening automatic control mechanism 25 Spring member 26 Bracket

Claims (10)

A plurality of fluids arranged in the fuselage and sucked from the suction port of the fuselage by rotating the rotor blades are provided at predetermined intervals in the circumferential direction along the axial direction of the fuselage on the inner periphery of the fuselage. It is a fluid machine that guides by guide vanes and discharges from the discharge port,
Each guide wing includes a fixed guide wing and a movable guide wing, the fixed guide wing is fixed to the fuselage, and the movable inner wing is rotatable about a rotation axis orthogonal to the axial direction of the fuselage. And
When a reverse fluid flow that flows from the discharge port of the fuselage to the suction port flows in, the movable guide vane has a normal position where the blade surface is continuous with the blade surface of the fixed guide blade due to the generated fluid differential pressure. Provided with a movable blade opening automatic control mechanism that rotates in the direction of the fully closed position to change the direction of the reverse fluid flow, and holds it in a position to reduce the pressure of the reverse fluid flow in contact with the rotor blades A fluid machine characterized by The fluid machine according to claim 1,
The movable guide vane is fixed to the rotating shaft and rotates integrally around the rotating shaft, and fluid resistance is generated according to the rotating angle. The fluid resistance is minimum at the fully opened position and maximum at the fully closed position. A fluid machine characterized by having the following characteristics. The fluid machine according to claim 1 or 2,
The movable blade opening automatic control mechanism returns the movable guide blade to the normal position during a positive fluid flow, and efficiently converts the positive fluid flow sent from the rotary blade. The fluid machine according to any one of claims 1 to 3,
The fixed guide wing and the movable guide wing are disposed between the body and the inner casing disposed in the body, and the rotation shaft of the movable guide wing is disposed through the body and the inner casing. A fluid machine, wherein the fluid machine is rotatably supported by bearings provided in both through portions. The fluid machine according to claim 4.
One end portion of a link member is fixed to the body side end portion of the rotating shaft of each movable guide vane, and the other end portion of the link member is always fixed with a predetermined force by the movable blade opening automatic control mechanism. The fluid machine is biased to rotate to the normal position. The fluid machine according to claim 4 or 5,
The mounting position of the rotary shaft of the movable guide vane is shifted from the center of the side of the movable guide vane so that a rotational moment is generated around the rotary shaft due to the difference in pressure receiving area when the reverse fluid flow is generated. Fluid machine. The fluid machine according to any one of claims 1 to 6,
A fluid machine characterized by comprising initial motion power generation means for applying initial motion power to the movable guide vanes at the normal position when a reverse fluid flow is generated. The fluid machine according to claim 7, wherein
The fluid dynamic machine according to claim 1, wherein the initial rotational power generating means is a gap provided in an adjacent portion of the fixed guide vane or the adjacent portion of the movable guide vane. In a fluid machine operation control device that performs operation control of a fluid machine that is arranged in a flow path and sends a fluid flow from one of the flow paths to the other by rotating a rotor blade with a driving machine,
A speed control device, a driving operation control device, and a protection control device;
The speed control device normally eliminates the power to be output to the drive machine and the normal control function to output power to the drive machine to rotate the rotor blades at a set rotational speed commanded from the operation control device. A free-run control function for freely rotating a rotating body including the rotor blade of a fluid machine,
The operation control device includes a normal control instruction function that sends the set rotation speed signal to the speed control device during the normal control and rotates the rotor blades at a set rotation speed.
The protection control device includes a free-run instruction function that causes the speed control device to place the rotating body in a free-run state when an external pressure fluid flow outside an allowable range enters the flow path.
A fluid machine operation control apparatus using the fluid machine according to claim 1 as the fluid machine. In the fluid machine operation control device according to claim 9,
The protection control device includes a protection control start notification function for notifying the operation control device that the protection control has started when the speed control device instructs the free run, and an external pressure fluid acting on the flow path. Is provided with a protection control end notification function for notifying that the protection control has ended when the value falls within the allowable range,
A fluid machine operation control apparatus characterized by the above.

Images