JP6249671B2 - Inverter-driven compressor operation control method and inverter-driven compressor - Google Patents

Description

  The present invention relates to an inverter-driven compressor operation control method and an inverter-driven compressor that executes the operation control method, and more specifically, inverter-driven compression that controls the rotational speed of a motor, which is a drive source of the compressor body, by an inverter. The present invention relates to an operation control method capable of reducing power (power consumption) and an inverter-driven compressor that executes the operation control method.

  In an inverter-driven compressor, an inverter is arranged between the motor provided as the drive source of the compressor body and the power supply, and the frequency of the alternating current input from the power supply to the motor is changed by this inverter so that the rotational speed of the motor It is comprised so that it can control.

  In such an inverter driven compressor, the pressure on the discharge side of the compressor body is detected by pressure detection means such as a pressure sensor, and the detected pressure is converted to the pressure of the compressed gas (target pressure) to be supplied to the consumption side. The frequency of the alternating current output to the motor by the inverter is changed so as to match, and the motor speed, and hence the compressor speed, is controlled. If the detected pressure exceeds the target pressure, the motor While reducing the frequency of the alternating current output to the motor and lowering the motor rotation speed, if the compressor discharge side pressure drops below the target pressure, the motor outputs an alternating current that increases the motor rotation speed. Control is taking place.

  In the inverter-driven compressor configured as described above, unnecessary power consumption can be suppressed by controlling the rotational speed of the compressor body according to the amount of compressed air consumed on the consumer side. Although it is possible to reduce power consumption compared to a motor-driven compressor that does not perform speed control, the inverter-driven compressor also aims to reduce running costs by further reducing power consumption. As a result, improvements in various operation control methods have been proposed.

  As an example of such an operation control method, Japanese Patent Application Laid-Open No. H10-228707 discloses a rotation that changes the rotational speed of the compressor body in response to a change in load for the purpose of reducing power and preventing drain generation in the oil separator. Capable of speed control and no-load operation that closes the suction throttle valve provided on the suction side of the compressor body and releases the compressed air in the oil separator, with the rotation speed of the compressor body as the lower limit rotation speed of the rotation speed control. By reducing the discharge side pressure of the compressor body during this no-load operation, the power consumption is reduced, and when the no-load operation continues for a predetermined time or more, or when the no-load operation and the load are controlled by the capacity control. It has been proposed to perform control to stop the screw compressor when the time ratio with respect to operation exceeds a predetermined ratio (claims 1 and 2 of Patent Document 1).

JP-A-9-287580

  In the invention described in Patent Document 1 described above, when the no-load operation continues for a predetermined time or when the ratio of the no-load operation to the load operation increases, the rotation of the motor is stopped to Since it is intended to stop, the power consumption can be reduced compared to the case where the motor is continuously driven during no-load operation.

  In addition, during no-load operation or when the motor is stopped, the pressure in the oil separator decreases due to air release, so that the dew point is lowered and drainage is less likely to occur.

  However, during no-load operation where the discharge pressure on the compressor body is reduced, the load on the motor is sufficiently small, so even if the compressor is stopped during no-load operation, this It is not possible to obtain a significant reduction in power.

  In addition, since the compressor main body stops discharging compressed air and the compressed air in the oil separator is released due to the shift to the no-load operation, the amount of drain generation in the oil separator is reduced. Since the reduction in the amount of drain generation has already been achieved by shifting to the load operation, further reduction in the amount of drain generation cannot be expected even if the compressor main body in the no-load operation state is further stopped.

  On the other hand, compared to the power consumed during no-load operation, the power consumed during load operation is large, which means that full-load operation or high-load operation (hereinafter referred to as “upper-load operation” or “high-load operation”) These are collectively referred to as “high load operation”), and are also applicable during low load operation in which the compressor body is operated near the lower limit rotational speed.

  Moreover, although power consumption is reduced during low-load operation compared to high-load operation, the power required to generate compressed air per unit air volume is compared to that during low-load operation compared to high-load operation. Then, as a result of research by the inventors of the present invention, it is clear that a larger power is required.

  Therefore, for example, when the pneumatic equipment connected to the consumer side always consumes a small amount of compressed air, or in the air piping connecting the inverter-driven compressor and the pneumatic equipment provided on the consumer side If a small amount of compressed air is always consumed on the consumption side as in the case of slight leakage due to poor connection or deterioration of the gas seal, the operation control described in the above-mentioned Patent Document 1 is performed. In the method, in order to compensate for the consumption of this small amount of compressed air, the compressor will continue low load operation for a long time without shifting to no-load operation, and the running cost will increase.

  In addition, when the compressor is an oil-cooled compressor, especially an inverter-driven compressor, if low load operation is continued for a long time, the amount of heat generated during low load operation is much smaller than during high load operation. The temperature of the discharge air discharged from the compressor body decreases, the flow rate of the compressed gas passing through the oil separator relatively slows down, and the time that the compressed air stays in the oil separator becomes longer. If the operation is continued for a long time, the temperature in the oil separator will drop below the dew point temperature, and water vapor will tend to aggregate in the oil separator. It is not preferable to perform for a time.

  Accordingly, the present invention provides a further reduction in power consumption and an air flow path connected to the discharge side of the compressor body in an inverter-driven compressor in which the rotational speed is variable in accordance with the consumption amount of compressed air on the consumption side. An object of the present invention is to provide an operation control method capable of suppressing the generation of drain in (for example, an oil separator or a receiver tank).

  Hereinafter, means for solving the problem will be described together with reference numerals used in the embodiment for carrying out the invention. This code is used to clarify the correspondence between the description of the scope of claims and the description of the mode for carrying out the invention. Needless to say, it is used in a limited manner for the interpretation of the technical scope of the present invention. It is not a thing.

In order to achieve the above object, an operation control method for an inverter driven compressor 1 according to the present invention generates a compressor body 10, a motor 15 for driving the compressor body 10, and an alternating current input to the motor 15. Inverter-driven compressor having a variable output speed of the inverter 30 and a variable rotational speed of the compressor body 10 so that the discharge side pressure of the compressor body 10 becomes a predetermined target pressure Pt. In 1,
A check valve 54 is provided in the air flow path 50 from the discharge port 10b of the compressor body 10 to the consumption side, and the air flow path on the primary side of the check valve 54 is connected to the discharge flow path 51 and the check flow. The air flow path 50 on the secondary side of the valve 54 forms the supply flow path 52, and a predetermined high pressure with respect to the target pressure Pt is set as the no-load operation start pressure Pul.
When the pressure Pd in the supply flow path 52 is less than the no-load operation start pressure Pul, the frequency of the alternating current output by the inverter is set so that the pressure Pd in the supply flow path 52 matches the target pressure Pt. Rotational speed control for controlling the rotational speed of the compressor main body 10 by changing between a predetermined lower limit frequency fmin and an upper limit frequency fmax is performed.
When the pressure Pd in the supply flow path 52 becomes the no-load operation start pressure Pul, the discharge flow path 51 is shifted to a no-load operation that is opened to the atmosphere, and after the transition to the no-load operation, the supply The pressure Pd in the flow path 52 is configured to return to the rotational speed control when the pressure Pd becomes equal to or lower than the target pressure Pt.
When the compressor main body 10 is in a predetermined low load operation state during the rotational speed control, the rotational speed control is stopped and the output frequency of the inverter 30 is set to the pressure Pd in the supply flow path 52. and performing the forced migration control of forced into said no-load operation is increased to a pressure increase frequency fb is the frequency at which Ru is raised above the no-load operation start pressure Pul (claim 1).

  In the inverter-driven compressor 1 configured as described above, a predetermined high frequency is set as the determination reference frequency fa with respect to the lower limit frequency fmin, the continuous output time of the frequency below the determination reference frequency fa by the inverter 30 is counted, When the output of the frequency equal to or lower than the determination reference frequency fa is continuously performed for a predetermined time t (or t ′), it can be determined that the low load operation state has been established.

  The inverter 30 outputs a frequency equal to or lower than the determination reference frequency fa, and the pressure Pd of the supply flow path 52 is equal to or higher than a determination reference pressure Pj that is higher by a predetermined value P2 (0.01 MPa) than the target pressure Pt. When this happens, counting of the continuous output time of the frequency below the determination reference frequency fa may be started (Claim 3).

  Further, instead of counting the output time of the frequency equal to or lower than the determination reference frequency fa, the pressure Pd in the supply flow path 52 becomes equal to or higher than the determination reference pressure Pj higher than the target pressure Pt by a predetermined value P2 (0.01 MPa). It is good also as what determines with having become the said low load driving | running | working state (Claim 4).

The inverter-driven compressor 1 of the present invention includes a compressor body 10, a motor 15 that drives the compressor body 10, a pressure detection means 60 that detects a pressure on the discharge side of the compressor body 10, and the A control device 2 that includes an inverter 30 that generates an alternating current to be input to the motor 15 and that changes the output frequency of the inverter 30 so that the pressure detected by the pressure detection means 60 matches a predetermined target pressure Pt. In the inverter driven compressor 1 provided,
A check valve 54 is provided in the air flow path 50 extending from the discharge port 10b of the compressor body 10 to the consumption side, and the air flow path 50 on the primary side of the check valve 54 forms a discharge flow path 51 and An air discharge means 40 is provided to allow the discharge flow path 51 to be opened to the atmosphere. The air flow path 50 on the secondary side of the check valve 54 forms a supply flow path 52, and the pressure detection means is connected to the supply flow path 52. 60,
The control device 2 is
A predetermined high pressure with respect to the target pressure Pt is stored as the no-load operation start pressure Pul, and compared with the pressure in the supply flow path 52 detected by the pressure detection means 60, the detected pressure Pd of the pressure detection means 60 is detected. Is less than the no-load operation start pressure Pul, the frequency of the alternating current output from the inverter 30 is set to a predetermined lower limit frequency fmin and an upper limit frequency fmax so that the pressure in the supply flow path 52 matches the target pressure Pt. A rotational speed control for controlling the rotational speed of the compressor body 10 by outputting a control signal that changes between
When the detected pressure Pd of the pressure detecting means 60 reaches the no-load operation start pressure Pul, the discharge means 51 is moved to the no-load operation by operating the air release means 40 and the no-load operation is started. Switching of the operating state to return to the rotational speed control when the detected pressure Pd of the pressure detecting means 60 becomes equal to or lower than the target pressure Pt after shifting to the load operation;
When it is determined that the compressor main body 10 is in a predetermined low load operation state during the rotation speed control, the rotation speed control is stopped and the output frequency of the inverter 30 is changed to the pressure in the supply flow path 52. forcibly transferred to said no-load operation is increased to a pressure increase frequency fb is the frequency at which Ru is raised above the no-load operation start pressure Pul and is characterized in that a forced migration control (claim 5) .

  In the inverter driven compressor 1 having the above-described configuration, the control device 2 stores a predetermined high frequency as the determination reference frequency fa with respect to the lower limit frequency fmin, and the inverter 30 continuously outputs a frequency equal to or lower than the determination reference frequency fa. In addition to counting time, when the continuous output time of the determination reference frequency fa continues for a predetermined time t (or t ′), it is determined that the low load operation state has been reached and the forced transition control is executed. (Claim 6).

  In the inverter-driven compressor 1 having the above-described configuration, the control device 2 causes the inverter 30 to output a frequency equal to or lower than the determination reference frequency fa, and the detected pressure Pd of the pressure detecting means 60 is greater than the target pressure Pt. It may be configured to start counting the continuous output time of the frequency equal to or lower than the determination reference frequency fa when the predetermined reference value P2 (0.01 MPa) is higher than the determination reference pressure Pj.

  Further, instead of counting the output duration time of the frequency below the determination reference frequency fa, the control device 2 determines that the detected pressure Pd of the pressure detecting means 60 is higher than the target pressure Pt by a predetermined value P2 (0.01 MPa). When the pressure becomes equal to or higher than the reference pressure Pj, it may be determined that the low-load operation state has been reached (Claim 8).

  With the configuration of the present invention described above, the following remarkable effects can be obtained in the inverter-driven compressor 1 of the present invention.

  When it is determined that the operation state of the inverter-driven compressor 1 has reached a predetermined low-load operation state during the rotation speed control in which the load operation is performed, the rotation speed control is stopped and the output frequency of the inverter 30 is increased. By increasing the rotational speed of the compressor body 10 and increasing the pressure in the supply flow path 52 to the no-load operation start pressure Pul, the low-load operation state can be aborted and the operation can be forcibly shifted to the no-load operation. I was able to do it.

  As a result, the low-load operation with poor compressed gas production efficiency is forcibly stopped, while the shortage of compressed air generated by the stop of the low-load operation increases the rotational speed before shifting to no-load operation. , And a high-load operation that is performed when the rotational speed control is resumed when the pressure Pd in the supply flow path decreases to the target pressure Pt, that is, generated by an operation state that is more energy efficient than the low-load operation. As a result, the power consumption of the inverter-driven compressor 1 could be greatly reduced.

  In addition, with this configuration, the low load operation time occupying the entire operation time of the inverter-driven compressor can be shortened, so that the temperature in the discharge passage 51, for example, the receiver tank 51b constituting the discharge passage 51 is lowered. As a result, the amount of drain generated in the components of the discharge flow channel 51 such as the receiver tank 51b can be reduced.

  Further, during no-load operation, the discharge flow path 51 is opened to the atmosphere by the discharge means 40 and the internal pressure is reduced, so that the dew point in the discharge flow path 51 is lowered by this pressure drop, and the discharge flow path 51 In this case, the condensation of water vapor is less likely to occur, and the time during which the compressed air stays in the discharge flow path 51 is shortened due to the release of the atmosphere, so that the generation of drain in the discharge flow path 51 can be significantly suppressed. It was.

  Not only that the inverter 30 outputs a frequency equal to or lower than the determination reference frequency fa, but also determines that the inverter is in the above-described low-load operation state when it is continuously output for a predetermined time t (or t ′). In such a case, the low-load operation for a predetermined time t (or t ′) is performed to prevent the forced transition from the rotational speed control to the no-load operation frequently in a short time. I was able to.

  Determination that the frequency output from the inverter 30 is equal to or lower than the determination reference frequency fa (22 Hz) and that the discharge side pressure, that is, the pressure Pd in the supply flow path 52 is higher than the target pressure Pt (0.69 MPa) by a predetermined value P2 (0.01 MPa). In the configuration that starts counting the output duration time of the judgment reference frequency fa when the reference pressure Pj is reached, the consumption of compressed air on the consumption side is reduced, and it is reliably detected that the vehicle is in a low load operation state. It was possible to prevent unnecessary pressure rise and venting.

  Whether or not the inverter-driven compressor 1 is in the above-described low-load operation state is determined by replacing the discharge-side pressure Pd with the target pressure Pt (0.69) instead of counting the output duration time of the frequency equal to or lower than the above-described determination reference frequency fa. The determination may be made based on whether or not the determination reference pressure Pj is higher by a predetermined value P2 (0.01 MPa) than (MPa). In this case, it is possible to determine whether or not the low load operation state is based on the detection signal from the pressure detection means 60, and a timer or the like for counting the duration time of the low load operation becomes unnecessary. The configuration of 2 could be made simpler.

  However, even when the low load operation is determined based on the determination reference pressure Pj, a timer is provided in the control device 2, and for example, a pressure state that is higher than the determination reference pressure Pj and lower than the no-load operation start pressure Pul continues for a predetermined time. It is good also as what determines that it is the low load operation state mentioned above.

The schematic explanatory drawing of the inverter drive compressor of this invention. The time chart which showed discharge side pressure Pd and the output frequency change of an inverter. The schematic explanatory drawing which showed the example of a change of the inverter drive compressor of this invention.

  Hereinafter, an inverter-driven compressor according to the present invention will be described with reference to the accompanying drawings.

  In FIG. 1, reference numeral 1 denotes an inverter-driven compressor. In the illustrated embodiment, the inverter-driven compressor 1 includes a compressor body 10, a motor 15 that is a drive source of the compressor body 10, and a power source. An inverter 30 that converts the frequency of the alternating current and outputs it to the motor 15 is provided. By driving the compressor main body 10 by the motor 15, an intake valve 45 connected to the inlet 10a of the compressor main body 10 is provided. The compressed gas, that is, air in the example shown in the figure, is introduced into the cylinder of the compressor body 10 and the compressed gas introduced into the cylinder is compressed by the rotation of the rotor, and the resulting compressed air is compressed. It is comprised so that it may discharge from the discharge port 10b of the machine main body 10. FIG.

  In this embodiment using an oil-cooled screw compressor that injects lubricating oil into the cylinder and compresses and discharges the compressed gas as the compressor body 10, the lubrication is performed by the compressor body 10. A receiver tank 51b into which compressed gas discharged together with oil is introduced, and the compressed gas and the lubricating oil are separated in the receiver tank 51b, and a pneumatic device (Fig. The lubricating oil collected in the receiver tank 51b can be supplied to the oil supply port 10c of the compressor body 10 through the oil supply circuit.

  A check valve 54 is provided in the middle of the compressed air flow path (air flow path 50) from the discharge port 10b of the compressor body 10 to a pneumatic device (not shown) provided on the consumption side. The backflow of the compressed air is prevented from occurring from the side toward the compressor body 10 side.

  In the description of the present invention, the air flow path 50 (the air flow path 50 on the primary side of the check valve 54) from the discharge port 10b of the compressor body 10 to the check valve 54 described above is referred to as “discharge flow path. (51) ”, the air flow path 50 (secondary air flow path 50 of the check valve 54) from the check valve 54 to the consumption side will be described as the“ supply flow path (52) ”.

  Accordingly, in the embodiment shown in FIG. 1, the receiver tank 51b provided on the temporary side of the check valve 54 constitutes a part of the discharge passage 51 defined above, and the receiver tank 51b and the receiver tank 51 The aforementioned discharge flow path 51 is formed by the pipe lines 51a and 51c communicated with 51b.

  The above-described discharge flow path 51, in the illustrated example, the receiver tank 51b that constitutes a part of the discharge flow path 51 is provided with a discharge means 40 for discharging the compressed air inside. The discharge flow path 51 can be opened to the atmosphere by the control of the air release means 40 by the control device 2.

  In the illustrated embodiment, as the air release means 40, pipes 42 and 43 communicating with the primary side of the receiver tank 51b and the suction valve 45, and an electromagnetic valve 41 for opening and closing the pipes 42 and 43 are provided. By opening and closing the electromagnetic valve 41 in accordance with a control signal from No. 2, the compressed air in the receiver tank 51b can be released or stopped.

  In the illustrated embodiment, the air release means 40 is provided so as to share a part of the structure with the opening / closing mechanism of the intake valve 45 provided on the intake side of the compressor body 10 and communicates with the receiver tank 51b. The branched pipe 42 is branched on the secondary side of the solenoid valve 41, one branch path is connected to the valve-closing pressure receiving chamber of the suction valve 45, and the other branch path, the air discharge pipe 43, is connected to the suction valve via the orifice. When the electromagnetic valve 41 is opened, the compressed air in the receiver tank 51b is introduced into the closed pressure receiving chamber of the intake valve 45 to close the intake valve 45, and in the receiver tank 51b. The compressed air is introduced into the suction passage on the primary side of the suction valve 45 through the orifice, and can be discharged through an air filter provided on the primary side of the suction valve 45.

  In the embodiment shown in FIG. 1, a suction valve 45 is provided on the suction side of the compressor body 10, and the suction port 10a of the compressor body 10 is closed and the intake of the compressor body 10 is stopped when shifting to no-load operation. However, the intake valve 45 is not necessarily provided, and as an example, as shown in FIG. 3, the intake valve 45 may be omitted.

  The operation of each part provided in the inverter-driven compressor 1 described above is based on the control signal from the control device 2 that receives the detection signal from the pressure detection means 60 and monitors the pressure in the supply flow path 52. The control device 2 compares the target pressure Pt and the no-load operation start pressure Pul stored in the storage means with the pressure Pd in the supply flow path 52 detected by the pressure detection means 60, and controls each part. A signal is output and the operation of each part is controlled as follows.

  When the pressure Pd in the supply flow path 52 detected by the pressure detection means 60 is less than the target pressure Pt, the control device 2 outputs a control signal for closing the electromagnetic valve 41, and the electromagnetic valve 41 receives this control signal and receives the pipe. When the pressure Pd in the supply flow path 52 detected by the pressure detection means 60 is equal to or higher than the no-load operation start pressure Pul, the control device 2 outputs a control signal for opening the electromagnetic valve 41, The valve 41 receives this control signal and opens the pipes 42 and 43. When the pressure Pd in the supply flow path 52 detected by the pressure detection means 60 is in the range of the target pressure Pt or more and less than the no-load operation start pressure Pul, the control device 2 does not change the control signal to the solenoid valve 41. Continue the previous control signal. That is, while the pressure Pd in the supply flow path 52 detected by the pressure detection means 60 increases from the target pressure Pt to the no-load operation start pressure Pul, the control device continuously outputs a control signal for closing the electromagnetic valve 41, While the pressure Pd in the supply flow path 52 detected by the pressure detection means 60 decreases from the no-load operation start pressure Pul to the target pressure Pt, the control device 2 outputs a control signal for opening the electromagnetic valve 41.

  The control device 2 outputs a control signal for closing the electromagnetic valve 41 when the pressure Pd in the supply flow path 52 falls below the target pressure Pt, and the pressure in the supply flow path 52 detected by the pressure detection means 60. The pressure difference between Pd and the target pressure Pt is calculated, the frequency of the alternating current output from the inverter 30 is obtained by PI calculation processing or PID calculation processing based on this pressure difference, and the corresponding rotation speed command (frequency command) is obtained. By generating and outputting this as a control signal to the inverter 30, the frequency output from the inverter 30 is changed between a predetermined lower limit value fmin and an upper limit value fmax to control the rotational speed of the compressor body. “Rotational speed control”.

  As an example, in the rotation speed control, when the pressure Pd in the discharge flow path 52 detected by the pressure detection means 60 exceeds the target pressure Pt, the inverter 30 sets the frequency of the alternating current output to the motor 15 to be higher than the upper limit value fmax. When the motor 15 is shifted to a low speed operation by reducing the frequency to a low predetermined frequency and the pressure Pd reaches the no-load operation start pressure Pul, the frequency is already at the lower limit value fmin. On the other hand, when the pressure Pd in the supply flow path 52 falls below a predetermined target pressure Pt, the inverter 30 sets the frequency of the alternating current output to the motor 15 to a predetermined frequency higher than the lower limit value fmin, for example, the maximum frequency fmax. To do. By repeating such an operation, the pressure Pd in the supply flow path 52 is matched with the target pressure Pt.

  In the above description, “inverter 30” refers to the main body of the inverter, and an apparatus for controlling the output frequency of the inverter (main body), such as an arithmetic processing unit that performs PI arithmetic processing or PID arithmetic processing, is an apparatus configuration. Regardless of whether it is configured integrally with the inverter body or a separate device from the inverter body, it constitutes a component of the control device 2 in the present application.

  Further, when the pressure Pd in the supply flow path 52 rises and reaches the no-load operation start pressure Pul because the consumption of compressed air on the consumption side stops, the solenoid valve 41 is opened as described above, and thereby the intake valve 45 Is closed to stop the introduction of the compressed gas into the compressor main body 10, and the compressed air in the receiver tank 51 b is released to the atmosphere through the discharge passage 43 to reduce the pressure to the lower limit pressure Pmin, and the output of the inverter 30 The operation shifts to no-load operation with the frequency set to the lower limit frequency fmin.

  This lower limit pressure Pmin is a pressure necessary for reliably pumping the lubricating oil from the receiver tank 51b to the compressor main body 10, and the air discharge pipe so that the pressure in the receiver tank 51b is maintained at the lower limit pressure Pmin. The flow rate of the compressed air discharged is adjusted by the opening area of the orifice provided in 43.

  When the operation is shifted to the no-load operation in this way, the compressed air in the discharge passage 51 (receiver tank 51b) is discharged and the pressure decreases to the lower limit Pmin, but the discharge flow on the primary side of the check valve 54 is reduced. The pressure drop in the passage 51 (receiver tank 51b) does not reduce the pressure in the supply flow path 52 on the secondary side of the check valve 54, and the supply of compressed air on the consumption side is stopped. The pressure in the flow path 52 is maintained at the no-load operation start pressure Pul, and during this time, the control device 2 maintains the no-load operation state.

  After that, when the consumption of compressed air on the consumption side is resumed and the pressure in the supply flow path 52 decreases to the target pressure Pt, the electromagnetic valve 41 is closed and the suction valve 45 is opened, and the discharge flow path 51 is discharged. It stops and returns to the above-mentioned rotational speed control for controlling the output frequency of the inverter 30 so that the pressure Pd in the supply flow path 52 detected by the pressure detection means 60 becomes the target pressure Pt. As described above, the inverter-driven compressor is controlled to perform the basic operation that repeats the above-described rotation speed control and the transition to the no-load operation according to the pressure in the supply flow path 52.

  In the inverter-driven compressor 1 of the present invention, the control device 2 described above, in addition to the basic operation described above, further, the compressor body 10 is in a predetermined low load operation state during the rotation speed control. Is determined, the rotational speed control described above is stopped and the output frequency of the inverter 30 is increased to increase the pressure Pd in the supply flow path 52 to be equal to or higher than the no-load operation start pressure Pul. It is configured to perform forced transition control that forcibly shifts to no-load operation.

  In the present embodiment, as an example, when the output frequency of the inverter 30 continues for a predetermined time t (or t ′) and outputs a frequency equal to or lower than the determination reference frequency fa set as a predetermined high frequency with respect to the lower limit frequency fmin. The control device 2 determines that the low load operation state has been reached, and executes the forced transition control described above.

  Such control will be described with reference to FIG. 2. When the pressure Pd in the supply flow path 52 becomes the target pressure Pt during the rotational speed control, the inverter 30 starts control to lower the output frequency (FIG. 2). 2 (T1), the output frequency of the inverter 30 eventually decreases below the reference frequency fa (T2 in FIG. 2) and reaches the lower limit frequency fmin (T3 in FIG. 2).

  Here, when the compressed air is not consumed on the consuming side, the compressor body 10 is operated at a low rotational speed, but discharges a small amount of compressed air, so that the pressure in the supply flow path 52 is increased. Gradually increases, and the pressure Pd in the supply flow path 52 eventually rises above the no-load operation start pressure Pul. Therefore, the shift to the no-load operation is performed according to the basic operation described above.

  However, when the consumption side consumes a small amount of compressed air (including leakage) as much as the amount of compressed air generated at the rotational speed corresponding to the frequency equal to or lower than the determination reference frequency fa, The pressure Pd does not rise to the no-load operation pressure Pul, but the pressure is higher than the target pressure Pt and less than the no-load operation start pressure Pul. Since the low-load operation that is operated at the rotational speed or slightly higher than that is continued, the inverter-driven compressor 1 of the present invention has such a low-load operation state. In this case, it is now possible to force the transition to no-load operation.

  In order to enable such a forced transition of the operating state, the control device 2 described above is configured to receive the output of the inverter 30, and during the load operation in which the rotational speed control is performed, the inverter After the control signal output to 30 instructs the output of the frequency equal to or lower than the above-described determination reference frequency fa, the control device 2 receives a frequency equal to or lower than the determination reference frequency fa from the inverter 30 (T2 in FIG. 2). Is started, and counting of the time during which the output of the frequency below the determination reference frequency fa is continuously performed is started.

  Such counting may be started when the control device 2 outputs a control signal for instructing the inverter 30 to output a frequency equal to or lower than the determination reference frequency fa, instead of the above configuration.

  In this embodiment, the determination reference frequency fa is set to a value slightly higher than the lower limit frequency fmin (20 Hz) in the frequency variable range (20 to 58 Hz as an example) used in the rotational speed control described above. In this embodiment, the determination reference frequency fa is set to 22 Hz, which is 2 Hz higher than the lower limit frequency fmin (20 Hz).

  When counting is performed in this way, if the discharge side pressure Pd falls below the target pressure Pt due to an increase in the amount of compressed air consumed on the consumption side, the control device 2 increases the output frequency for the inverter. When a control signal is output and a control signal for instructing output at a frequency exceeding the determination reference frequency fa is output, the timer count is stopped and reset.

  On the other hand, when the pressure in the supply flow path 52 does not decrease and the output of the frequency equal to or lower than the determination reference frequency fa is continuously counted for a predetermined time t (T5 in FIG. 2), the control device 2 is connected to the inverter driven compressor. 1 is determined to be in a low-load operation state, and a control signal that instructs the inverter 30 to output the pressure increase frequency fb, which is set as a frequency higher than the determination reference frequency fa, is output.

  The pressure increase frequency fb needs to be set to a frequency that can quickly increase the pressure in the supply flow path 52 of the compressor in the low load operation state to the no-load operation start pressure Pul or higher. In the embodiment, 40 Hz, which is twice the lower limit frequency fmin (20 Hz), is set as the pressure increase frequency fb.

  Therefore, when the inverter 30 receives the control signal from the control device 2 and outputs an alternating current of the pressure increase frequency fb to the motor 15, the rotational speed of the motor 15, and hence the compressor body 10, is rapidly increased and the supply flow is increased. The pressure Pd in the passage 52 quickly rises to the no-load operation start pressure Pul (T6 in FIG. 2), and the operation state can be forcibly shifted to the no-load operation.

  In the above description, the pressure increase frequency fb is set to 40 Hz higher than the judgment reference frequency fa (22 Hz) and lower than the rated value ft (53.5 Hz). However, the power of the compressor main body is controlled during the forced transition control. The frequency is not limited to this frequency value as long as it does not exceed the allowable power (maximum output) of the motor (does not cause overload), and other frequencies can be selected. For example, the rated value ft (53.5 Hz) May be set as the pressure increase frequency fb, and the control device may automatically calculate and set the pressure increase frequency fb according to the setting of the target pressure, or at that time according to the pressure in the supply flow path 52. Thus, the control device 2 may calculate and set the maximum frequency at which the power of the compressor body 10 does not exceed the allowable power of the motor 15.

  When the consumption of compressed air on the consumption side is started when the inverter 30 outputs the pressure increase frequency fb and the pressure in the supply flow path 52 decreases below the target pressure Pt, the control device 2 Stops the forced transition control, shifts to the rotational speed control in which the pressure Pd in the supply flow path 52 approaches the target pressure, and the frequency output from the inverter 30 after the transition to the rotational speed control is equal to or lower than the determination reference frequency fa. When it decreases, counting is started again, and forced transition control is performed according to the process described above.

  In the above description, the inverter 30 outputs a frequency equal to or lower than the determination reference frequency fa for a predetermined time t, so that the determination criterion is that the compressor is in the low load operation state. However, the inverter 30 is in the low load operation state. Other criteria may be used as the judgment criteria.

  For example, the inverter outputs the judgment reference frequency fa or the lower limit frequency fmin, and the pressure in the supply flow path is higher than the target pressure Pt by a predetermined high pressure, for example, a predetermined value p2 (0.01 MPa as an example) higher than the target pressure Pt. The determination reference pressure Pj may be reached to determine that the vehicle is in a low-load operation state, or a pressure that is equal to or higher than the above-described determination reference pressure Pj and less than the no-load operation start pressure Pul is continuously detected for a predetermined time. Therefore, it may be determined that the vehicle is in a low load operation state.

  Further, after counting the output time of the frequency equal to or lower than the determination reference frequency fa performed in the above-described embodiment, the output Pd of the frequency equal to or lower than the determination reference frequency fa is started, and then the pressure Pd in the supply passage 52 is determined as the determination reference pressure. When the two conditions of being Pj or more are satisfied (T4 in FIG. 2), the counting of the predetermined time t ′ may be started. May be prevented from being performed.

  The set value of the target pressure Pt can be changed, and the control device 2 can automatically calculate and automatically change the no-load operation start pressure Pul in accordance with the change of the target pressure Pt. May be.

  In the configuration of the inverter-driven compressor 1 of the present invention described above, if it is determined that a predetermined low load operation state is obtained, for example, the determination reference frequency fa is continuously output for a predetermined time, the frequency is promptly determined. Is increased to the pressure increase frequency fb, the pressure Pd in the supply flow path 52 is increased to the no-load operation start pressure Pul, and the operation is forcibly shifted to the no-load operation. I was able to shorten it.

  As a result, low load operation with low compressor efficiency is not continued for a long time, so that the power consumption of the compressor can be reduced, and in the discharge flow path 51 (receiver tank 51b) by shifting to no load operation. It was possible to provide the inverter-driven compressor 1 that can significantly suppress the generation of drain.

DESCRIPTION OF SYMBOLS 1 Inverter drive compressor 2 Control apparatus 10 Compressor body 10a Inlet (compressor body)
10b Discharge port (compressor body)
10c Refueling port (compressor body)
DESCRIPTION OF SYMBOLS 15 Motor 30 Inverter 40 Air release means 41 Electromagnetic valve 42 Pipe line 43 Air discharge line (the other branch path; pipe line)
45 Suction valve 50 Air flow path 51 Discharge flow path 51a Discharge piping 51b Receiver tank 52 Supply flow path 54 Check valve 60 Pressure detection means Pd Pressure in supply flow path 52 (discharge side pressure; detection pressure of pressure detection means)
Pt Target pressure Pul No-load operation start pressure Pj Judgment reference pressure Pmin Lower limit pressure fmin Lower limit frequency fmax Upper limit frequency fa Judgment reference frequency fb Pressure rise frequency

Claims (8)

A compressor body, a motor for driving the compressor body, and an inverter for generating an alternating current to be input to the motor, and the output of the inverter so that the discharge side pressure of the compressor body becomes a predetermined target pressure. In an inverter driven compressor in which the frequency is variable and the rotation speed of the compressor body is variable,
A check valve is provided in the air flow path from the discharge port of the compressor body to the consumption side, the air flow path on the primary side of the check valve is connected to the discharge flow path, and the secondary side of the check valve The air flow path constitutes a supply flow path, and a predetermined high pressure with respect to the target pressure is set as a no-load operation start pressure,
When the pressure in the supply flow path is less than the no-load operation start pressure, the frequency of the alternating current output by the inverter is set to a predetermined lower limit frequency and an upper limit so that the pressure in the supply flow path matches the target pressure. Rotational speed control is performed to control the rotational speed of the compressor body by changing between frequencies,
When the pressure in the supply flow path becomes the no-load operation start pressure, the discharge flow path is shifted to a no-load operation that is opened to the atmosphere, and after the transition to the no-load operation, Configured to return to the rotational speed control when the pressure falls below the target pressure,
When the compressor body is in a predetermined low-load operation state during the rotation speed control, the rotation speed control is stopped and the output frequency of the inverter is set to the pressure in the supply flow path. operation control method of the inverter-driven compressor, characterized in that a forced migration control is increased to a pressure increase frequency is the frequency at which Ru is raised above operation start pressure forced into the no-load operation.   A predetermined high frequency with respect to the lower limit frequency is set as a determination reference frequency, the continuous output time of the frequency below the determination reference frequency by the inverter is counted, and the output of the frequency below the determination reference frequency is continued for a predetermined time. The operation control method for an inverter-driven compressor according to claim 1, wherein when it is performed, it is determined that the low-load operation state has been reached.   When the inverter outputs a frequency equal to or lower than the determination reference frequency and the pressure in the supply flow path is equal to or higher than a determination reference pressure that is higher than the target pressure by a predetermined value, the frequency lower than the determination reference frequency is continued. 3. The operation control method for an inverter-driven compressor according to claim 2, wherein counting of the output time is started.   2. The operation of the inverter-driven compressor according to claim 1, wherein when the pressure in the supply flow passage is equal to or higher than a determination reference pressure higher than a target pressure by a predetermined value, it is determined that the low load operation state has been reached. Control method. A compressor main body, a motor for driving the compressor main body, pressure detection means for detecting a pressure on the discharge side of the compressor main body, an inverter for generating an alternating current input to the motor, and the pressure detection to match the pressure means detects a predetermined target pressure, to have contact to the inverter-driven compressor having a control device for varying the output frequency of the inverter,
A check valve is provided in the air flow path from the discharge port of the compressor body to the consumption side, and the air flow path on the primary side of the check valve is formed as a discharge flow path, and the discharge flow path can be opened to the atmosphere. The air flow path on the secondary side of the check valve is provided as a supply flow path and the pressure detection means is provided in the supply flow path.
The control device is
A predetermined high pressure with respect to the target pressure is stored as the no-load operation start pressure, and the detected pressure of the pressure detection means is compared with the pressure in the supply flow path detected by the pressure detection means. When the pressure is less than the pressure, the control circuit outputs a control signal for changing the frequency of the alternating current output from the inverter between a predetermined lower limit frequency and an upper limit frequency so that the pressure in the supply flow path matches the target pressure. Rotational speed control that controls the rotational speed of the machine body,
When the detected pressure of the pressure detection means becomes the no-load operation start pressure, the discharge means is operated to shift to the no-load operation in which the discharge passage is opened to the atmosphere, and the shift to the no-load operation is performed. An operation state switching to return to the rotational speed control when the detected pressure of the pressure detecting means becomes equal to or lower than the target pressure later;
When it is determined that the compressor body is in a predetermined low load operation state during the rotation speed control, the rotation speed control is stopped, the output frequency of the inverter is set to the pressure in the supply flow path. forcibly transferred to the no-load operation is increased to a pressure increase frequency is the frequency at which Ru is raised above load operation start pressure, the inverter-driven compressor, characterized in that a forced migration control.   The control device stores a predetermined high frequency with respect to the lower limit frequency as a determination reference frequency, counts the continuous output time of the frequency below the determination reference frequency by the inverter, and continues the output time of the determination reference frequency. 6. The inverter-driven compressor according to claim 5, wherein the forced transition control is executed by determining that the low-load operation state has been reached when the operation is continued for a predetermined time.   When the control device outputs a frequency equal to or lower than the determination reference frequency, and the detected pressure of the pressure detection means is equal to or higher than a determination reference pressure higher than the target pressure, the determination reference frequency 7. The inverter-driven compressor according to claim 6, wherein counting of the continuous output time of the following frequency is started.   6. The inverter according to claim 5, wherein the control device determines that the low-load operation state has been reached when the detected pressure of the pressure detecting means becomes equal to or higher than a determination reference pressure higher than a target pressure by a predetermined value. Drive compressor.

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