JP2024086391A - Gas compression device and maintenance method thereof - Google Patents

Abstract

A gas compression device is provided that can suppress the accumulation of dust on a heat exchanger that cools compressed gas by heat exchange with cooling air, thereby suppressing a decrease in the cooling performance of the heat exchanger.
[Solution] A gas compression device 100 comprising a compression section 105 that compresses air A, a heat exchanger 113 that cools at least one of compressed air PA compressed in the compression section 105 and lubricating oil LO separated from the compressed air PA by heat exchange with cooling air CA, and a discharge port 117 that discharges the compressed air PA. The gas compression device 100 comprises an air release valve 110 that opens and closes a discharge flow path 108 that branches off from a discharge flow path 108 between the compression section 105 and the discharge port 117, and an air release section 120 that is provided at the end of an air release flow path 109 and releases the compressed air PA toward the heat exchanger 113.
[Selected Figure] Figure 1

Description

This disclosure relates to a gas compression device and a maintenance method thereof.

There is a known invention related to an aftercooler that cools compressed air (see Patent Document 1 below). The aftercooler of Patent Document 1 includes a heat exchanger, an oil-water separator, an intermittent drain trap, an ejector, a gas-liquid discharge section, a water tank, a check valve, and a cooling fan (Patent Document 1, paragraph 0026, Figures 1 and 2). In this conventional aftercooler, the gas-liquid discharge section is formed with an open end where one end of the pipe is open to the atmosphere. This open end faces the heat exchanger. The gas-liquid discharge section is also arranged to discharge gas and liquid to the upper part between the cooling fan and the heat exchanger (Patent Document 1, paragraph 0033, Figures 1 and 2).

The low-temperature treated water and exhaust air discharged from the drain water outlet of the intermittent drain trap are passed through the ejector by the pressure of the discharged compressed air, and are discharged from the gas-liquid discharge section and applied to the heat exchanger. In the heat exchanger, the low-temperature treated water and exhaust air are applied, and the compressed air is cooled to a lower temperature than if it were cooled only by the outside air blown from the cooling fan. Note that this temperature is even lower than if it were cooled by the latent heat of water that is the same temperature as the outside air temperature, because the temperature of the treated water is lower. At this time, the treated water applied to the heat exchanger washes away dust that has accumulated in the heat exchanger (Patent Document 1, paragraph 0046).

JP 2009-066504 A

In a gas compression device equipped with a heat exchanger that cools at least one of the compressed gas and the lubricating oil separated from the compressed gas by heat exchange with cooling air, if dust contained in the cooling air adheres to and accumulates in the heat exchanger, the cooling performance will, for example, increase thermal resistance and pressure loss, and decrease. In the aftercooler described in Patent Document 1, some of the dust that has accumulated in the heat exchanger is washed away by treated water sprayed on the heat exchanger. However, spraying cooling water onto the heat exchanger together with compressed air may encourage the adhesion and accumulation of dust in other parts of the heat exchanger excluding that part.

The present disclosure provides a gas compression device that can suppress the accumulation of dust in a heat exchanger that cools at least one of the compressed gas and the lubricating oil separated from the compressed gas by heat exchange with cooling air, thereby suppressing a decrease in the cooling performance of the heat exchanger.

One aspect of the present disclosure is a gas compression device comprising: a compression section that receives a lubricating oil and compresses the gas; a heat exchanger that cools at least one of the compressed gas compressed in the compression section and the lubricating oil separated from the compressed gas by heat exchange with cooling air; a discharge port that discharges the compressed gas; an air release valve that opens and closes an air release flow path that branches off from the discharge flow path between the compression section and the discharge port; and an air release section that is provided at the end of the air release flow path and releases the compressed gas toward the heat exchanger.

According to the above aspect of the present disclosure, it is possible to provide a gas compression device and a maintenance method thereof that can suppress the accumulation of dust in a heat exchanger that cools at least one of the compressed gas and the lubricating oil separated from the compressed gas by heat exchange with cooling air, thereby suppressing a decrease in the cooling performance of the heat exchanger.

1 is a block diagram illustrating an embodiment of a gas compression device according to the present disclosure. FIG. 2 is an exploded view showing an example of an air release portion of the gas compression device of FIG. 1 . FIG. 2B is a front view showing the expanded state of the air release portion of FIG. 2A . FIG. 2B is a front view showing a contracted state of the air release portion of FIG. 2A . FIG. 2 is a cross-sectional view showing a first modified example of the gas release portion of the gas compression device of FIG. 1 . FIG. 3B is a cross-sectional view showing a bent state of the air release portion of FIG. 3A . FIG. 2 is a perspective view showing a second modified example of the gas release portion of the gas compression device of FIG. 1 . FIG. 2 is a cross-sectional view showing a second modified example of the gas release portion of the gas compression device of FIG. 1 . FIG. 2 is a cross-sectional view showing a second modified example of the gas release portion of the gas compression device of FIG. 1 . FIG. 4 is a cross-sectional view showing a third modified example of the gas release portion of the gas compression device of FIG. FIG. 13 is a perspective view showing a fourth modified example of the gas release portion of the gas compression device of FIG. FIG. 6B is a front view of the air release section of FIG. 6A .

Below, an embodiment of a gas compression device and a maintenance method thereof according to the present disclosure will be described with reference to the drawings.

FIG. 1 is a block diagram showing an embodiment of a gas compression device according to the present disclosure. The gas compression device 100 of this embodiment is, for example, a positive displacement oil-lubricated screw compressor. Note that the gas compression device 100 is not limited to an oil-lubricated screw compressor, and any type of compressor can be used. In the following, a case will be described in which the gas compressed by the gas compression device 100 is air A, but the gas compression device 100 can also compress gases other than air A.

The gas compression device 100 includes, for example, a housing 101, an intake filter 102, an intake flow path 103, an intake throttle valve 104, a compression section 105, a gas-liquid flow path 106, and an oil separator 107. The gas compression device 100 also includes, for example, a discharge flow path 108, an air release flow path 109, an air release valve 110, a check valve 111, and a lubricating oil flow path 112. The gas compression device 100 also includes, for example, a heat exchanger 113, a cooler fan 114, an oil filter 115, an air cooler 116, a discharge port 117, a control section 118, a cooling air flow path 119, and an air release section 120.

The housing 101 houses, for example, the above-mentioned components and devices that constitute the gas compression device 100. The housing 101 has, for example, an intake port 101a and an exhaust port 101b that connect the internal space of the housing 101 with the external space. When the compression section 105 and the cooler fan 114 described below are operated, air A is taken into the housing 101 through the intake port 101a of the housing 101, and air A is exhausted to the outside of the housing 101 through the exhaust port 101b of the housing 101.

The intake filter 102 is connected to the intake port 105a of the compression unit 105 via the intake flow path 103, for example. When the compression unit 105 operates and starts compressing the air A, the intake filter 102 passes the air A taken into the inside of the housing 101 and removes dust contained in the air A. As a result, the clean air A from which dust has been removed by passing through the intake filter 102 is supplied to the intake port 105a of the compression unit 105 via the intake flow path 103 and the intake throttle valve 104.

The intake throttle valve 104 is provided, for example, in the intake flow path 103 between the intake filter 102 and the compression section 105. The intake throttle valve 104 is, for example, a control valve whose opening can be adjusted by an actuator. The intake throttle valve 104 has its opening adjusted, for example, by controlling the actuator by the control section 118, and controls the flow rate of air A supplied to the intake port 105a of the compression section 105 via the intake flow path 103.

The compression unit 105 has, for example, a casing, male and female screw rotors housed in the casing, a motor that rotates the screw rotors, and an inverter that is connected to a power source and supplies power to the motor. The casing of the compression unit 105 has, for example, an intake port 105a, an exhaust port 105b, and an oil supply port 105c. The rotation of the motor of the compression unit 105 is controlled, for example, by a control unit 118.

The compression section 105 compresses the air A taken in through the intake port 105a by rotating the screw rotor. The lubricating oil LO supplied through the oil supply port 105c of the compression section 105 cools the compressed air A whose temperature has increased, and seals the gaps between the screw rotors. The compression section 105 discharges the compressed air A, i.e., compressed air PA, from the discharge port 105b together with the lubricating oil LO.

The gas-liquid flow path 106 connects, for example, the discharge port 105b of the compression section 105 and the gas-liquid inlet 107a of the oil separator 107, and introduces the compressed air PA containing the lubricating oil LO discharged from the discharge port 105b of the compression section 105 to the gas-liquid inlet 107a of the oil separator 107. The oil separator 107, for example, rotates the compressed air PA containing the lubricating oil LO introduced from the gas-liquid inlet 107a along its inner circumferential surface, and separates the lubricating oil LO from the compressed air PA by centrifugal force and stores it at the bottom. The compressed air PA introduced into the oil separator 107 and from which the lubricating oil LO has been separated flows into the discharge flow path 108 from the gas outlet 107b of the oil separator 107.

The discharge flow path 108, for example, extends from the gas outlet 107b of the oil separator 107 through the check valve 111, the heat exchanger 113, and the air cooler 116 to the discharge port 117 that discharges compressed air PA, which is a compressed gas. The air release flow path 109, for example, branches off from the discharge flow path 108 between the compression section 105 and the discharge port 117 and reaches the vicinity of the heat exchanger 113. The air release valve 110 is provided, for example, at the start end of the air release flow path 109 that branches off from the discharge flow path 108, and opens and closes the air release flow path 109. The air release valve 110 is, for example, a control valve whose opening can be adjusted by an actuator, and the opening is controlled by the control section 118.

The check valve 111 is provided, for example, downstream of the air release flow path 109 that branches off from the discharge flow path 108, and blocks the flow of compressed air PA in the opposite direction to the flow from the gas outlet 107b of the oil separator 107 to the heat exchanger 113. The lubricating oil flow path 112 runs, for example, from the lubricating oil outlet 107c at the bottom of the oil separator 107 through the heat exchanger 113 and the oil filter 115 to the oil supply port 105c of the compression section 105.

The heat exchanger 113 includes, for example, an aftercooler 113a and an oil cooler 113b. The aftercooler 113a is provided, for example, in the discharge flow passage 108 between the check valve 111 and the air cooler 116, and is equipped with a cooling flow passage having a plurality of corrugated fins. Compressed air PA, which is a compressed gas flowing through the cooling flow passage of the aftercooler 113a, is cooled, for example, by heat exchange with cooling air CA generated by the rotation of the cooler fan 114. That is, the gas compression device 100 of this embodiment is equipped with an air-cooled heat exchanger 113.

The oil cooler 113b is provided, for example, in the lubricant flow passage 112 between the lubricant outlet 107c of the oil separator 107 and the oil filter 115, and has a cooling passage having a plurality of corrugated fins. The lubricant LO flowing through the cooling passage of the oil cooler 113b is cooled, for example, by heat exchange with the cooling air CA generated by the rotation of the cooler fan 114. The aftercooler 113a and the oil cooler 113b are arranged, for example, adjacent to each other in the passage of the cooling air CA. The heat exchanger 113 may be configured to include only one of the aftercooler 113a and the oil cooler 113b.

The cooler fan 114 is disposed, for example, near the cooling air outlet 119b inside the cooling air flow path 119. The cooler fan 114 is driven, for example, by a motor to rotate, thereby generating a flow of cooling air CA that passes through the heat exchanger 113 and the cooling air flow path 119. The cooler fan 114 is disposed, for example, downstream of the heat exchanger 113 in the flow direction of the cooling air CA.

The cooling air flow path 119 has, for example, a cooling air inlet 119a near the heat exchanger 113, and the cross-sectional area of the flow path decreases the farther away from the heat exchanger 113 in the flow direction of the cooling air CA, and the cross-sectional area of the flow path is smallest in the portion surrounding the periphery of the cooler fan 114. In addition, the cooling air flow path 119 has, for example, a cooling air outlet 119b downstream of the cooler fan 114 in the flow direction of the cooling air CA and near the exhaust port 101b of the housing 101.

The oil filter 115 removes foreign matter such as metal particles from the lubricating oil LO that has passed through the oil cooler 113b and been cooled by heat exchange with the cooling air CA. The air cooler 116 further cools the compressed air PA that has passed through the aftercooler 113a and been cooled by heat exchange with the cooling air CA. The discharge port 117 discharges the compressed air PA, which is a compressed gas that has passed through the discharge port 105b of the compression section 105 and passed through the oil separator 107, the aftercooler 113a, and the air cooler 116, to an external device or air tank of the gas compression device 100.

The control unit 118 is configured, for example, by one or more microcontrollers including an input/output unit, a central processing unit (CPU), a memory, and a timer. The control unit 118 controls each part of the gas compression device 100, for example, by executing a program stored in the memory. More specifically, the control unit 118 controls, for example, the operation of the intake throttle valve 104, the compression unit 105, and the release valve 110. The control unit 118 may also control, for example, the operation of the cooler fan 114.

For example, in normal operation in which compressed air PA is discharged from the discharge port 117 of the gas compression device 100, the control unit 118 maintains the air release valve 110 in a fully closed state. As a result, the compressed air PA compressed by the compression unit 105 and from which the lubricating oil LO has been removed by the oil separator 107 passes through the check valve 111, aftercooler 113a, and air cooler 116 provided in the discharge flow path 108, and is discharged from the discharge port 117.

For example, when the gas compression device 100 is operating in a maintenance mode, the control unit 118 controls the air release valve 110 to a predetermined opening degree or to a fully open state. As a result, the compressed air PA compressed by the compression unit 105 and from which the lubricating oil LO has been removed by the oil separator 107 passes through the air release flow path 109 branching off from the discharge flow path 108 and the air release valve 110, and is released from the air release unit 120 provided at the end of the air release flow path 109 toward the heat exchanger 113.

The control unit 118 switches the operating state of the gas compression device 100 from normal operation to maintenance mode, for example, when the compression unit 105 stops compressing the gas. In this case, in the maintenance mode, the control unit 118 switches the supply destination of the compressed air PA from the discharge flow path 108 to the release flow path 109. The control unit 118 also switches the operating state of the gas compression device 100 from normal operation to maintenance mode, for example, when an operator operates the gas compression device 100 or when the cumulative operating time of the gas compression device 100 exceeds a threshold value.

The control unit 118 can also, for example, perform unloaded operation of the gas compression device 100. For example, during unloaded operation, the control unit 118 continues compression of air A by the compression unit 105, distributes compressed air PA to the discharge flow path 108 and the discharge flow path 109 by the air release valve 110, and reduces the pressure of the compressed air PA discharged from the discharge port 117. For example, during unloaded operation of the gas compression device 100, the control unit 118 switches the operating state of the gas compression device 100 to a maintenance mode.

The air release section 120 is provided, for example, at the end of the air release passage 109, and in the maintenance mode of the gas compression device 100, releases the compressed air PA supplied through the air release passage 109 toward the heat exchanger 113. The air release section 120 is provided, for example, downstream of the heat exchanger 113 in the flow direction of the cooling air CA generated by the rotation of the cooler fan 114. The air release direction De in which the air release section 120 releases the compressed air PA toward the heat exchanger 113 includes, for example, a directional component opposite to the flow direction of the cooling air CA.

Figure 2A is an exploded view showing an example of the air release section 120 of the gas compression device 100 of Figure 1. Figure 2B is a front view showing the air release section 120 of Figure 2A in an expanded state. Figure 2C is a front view showing the air release section 120 of Figure 2A in a contracted state.

The air release section 120 has, for example, a direction variable mechanism 121 that uses the pressure of the compressed air PA to change the air release direction De in which the compressed air PA is released. The direction variable mechanism 121 has an elastic member 122 whose elastic deformation amount changes according to the pressure of the compressed air PA, and a direction variable section 123 whose air release direction De changes according to the elastic deformation amount of the elastic member 122. The direction variable mechanism 121 may also have, for example, a protrusion 124 and a stopper 125.

The elastic member 122 is, for example, a metallic coil spring. The spring constant of the elastic member 122 is determined, for example, so that in the extended state shown in FIG. 2B, the elastic force Fe in the contraction direction of the elastic member 122 is balanced with the maximum force Fa acting on the direction variable part 123 when the compressed air PA is released. Note that the elastic force Fe of the elastic member 122 and the force Fa acting on the direction variable part 123 when the compressed air PA is released are forces in a direction parallel to the central axis Ac of the tip of the cylindrical air discharge flow path 109.

The direction variable section 123 has, for example, a straight pipe section 123a having an inner diameter larger than the outer diameter of the tip of the circular pipe-shaped air discharge flow path 109, and a nozzle section 123b provided at the tip of the straight pipe section 123a. The direction variable section 123 also has, for example, a spiral groove section 123c provided in the straight pipe section 123a, and a flange section 123d provided at the base end of the straight pipe section 123a.

The straight pipe section 123a is arranged around the tip of the air discharge flow path 109 and is installed so as to be rotatable in the circumferential direction around the central axis Ac by inserting the tip of the air discharge flow path 109 in the direction of the central axis Ac from the opening of the base end where the flange section 123d is provided. In this state, the central axis Aa of the straight pipe section 123a roughly coincides with the central axis Ac of the tip of the air discharge flow path 109.

The central axis Ab of the nozzle portion 123b forms, for example, an acute angle α with respect to the central axis Aa of the straight pipe portion 123a. The tip of the nozzle portion 123b has a truncated cone shape whose diameter decreases as it approaches the tip, and has an opening at the tip for releasing compressed air PA.

The groove portion 123c has a width that is slightly wider than the outer diameter of the cylindrical protrusion portion 124. The groove portion 123c extends spirally in the circumferential direction of the straight pipe portion 123a, for example, at an acute angle β with respect to the central axis of the straight pipe portion 123a, which roughly coincides with the central axis Ac of the air discharge flow path 109. The groove portion 123c is provided, for example, in an angular range of 90 degrees or more in the circumferential direction of the straight pipe portion 123a.

The flange portion 123d is provided, for example, in a circular ring shape that protrudes radially outward from the outer circumferential surface of the base end of the straight pipe portion 123a. The flange portion 123d is fixed to one end of the elastic member 122, for example, by engaging one end of the elastic member 122. The flange portion 123d may be fixed to one end of the elastic member 122, for example, by a mechanical fixing member or by welding.

The protrusion 124 is provided, for example, protruding from the outer peripheral surface of the tip of the cylindrical air discharge flow passage 109 toward the radial outside of the air discharge flow passage 109. The protrusion 124 has, for example, a cylindrical shape with a diameter slightly smaller than the width of the spiral groove 123c of the straight pipe section 123a, and engages within the spirally extending groove 123c. As a result, when the direction variable section 123 moves in the direction of the central axis Aa of the straight pipe section 123a relative to the protrusion 124, the protrusion 124 moves within the spiral groove 123c, causing the direction variable section 123 to rotate in the circumferential direction of the straight pipe section 123a.

The stopper 125 is provided, for example, in the shape of a ring protruding radially outward from the outer circumferential surface of the cylindrical air discharge passage 109. The stopper 125 is fixed to the other end of the elastic member 122 by engaging, for example, one end of the elastic member 122 fixed to the flange portion 123d of the direction variable portion 123 with the other end opposite thereto. The stopper 125 may be fixed to the other end of the elastic member 122 by, for example, a mechanical fixing member or welding.

Below, we will explain the operation of the gas compression device 100 of this embodiment and its maintenance method, comparing it with a conventional aftercooler.

In the conventional aftercooler described in Patent Document 1, low-temperature treated water and exhaust air discharged from the drain water outlet of the intermittent drain trap are released from the gas-liquid discharge section and applied to the heat exchanger. At this time, dust is washed away by the treated water in part of the heat exchanger. However, when cooling water is sprayed onto the heat exchanger together with compressed air, the cooling water adhering to the heat exchanger promotes the adhesion and accumulation of dust in other parts of the heat exchanger except for that part, and there is a risk that the accumulated dust will become stuck to the heat exchanger.

In this way, if dust adheres, accumulates, or sticks to the heat exchanger, the cooling performance of the heat exchanger will decrease, making it impossible to sufficiently cool the compressed air and lubricating oil, which may lead to an abnormal shutdown of the equipment. An abnormal shutdown of the equipment may, for example, reduce the productivity of production facilities in a factory, cause delays in production plans, and cause economic losses. To prevent such disadvantages, equipment users are required to perform appropriate maintenance to prevent the accumulation and adhesion of dust to the heat exchanger.

In contrast, the gas compression device 100 of this embodiment includes a compression section 105 that receives lubricating oil LO and compresses the gas, a heat exchanger 113 that cools at least one of the compressed gas compressed in the compression section 105 and the lubricating oil LO separated from the compressed gas by heat exchange with cooling air CA, and a discharge port 117 that discharges the compressed gas. Furthermore, the gas compression device 100 includes an air release valve 110 that opens and closes an air release flow path 109 that branches off from a discharge flow path 108 between the compression section 105 and the discharge port 117, and an air release section 120 that is provided at the end of the air release flow path 109 and releases the compressed gas toward the heat exchanger 113.

With this configuration, in the gas compression device 100 of this embodiment, when the heat exchanger 113 cools the compressed air PA and the lubricating oil LO by heat exchange with the cooling air CA, dust contained in the cooling air CA collides with and adheres to the surface or corrugated fins of the heat exchanger 113. However, in the gas compression device 100 of this embodiment, when a certain amount of dust adheres to the heat exchanger 113, the air release valve 110 can be opened. As a result, the compressed air PA compressed by the compression section 105 is supplied to the air release section 120 via the air release flow path 109 branching off from the discharge flow path 108, and the compressed air PA is released from the air release section 120 toward the heat exchanger 113.

As a result, dust adhering to the heat exchanger 113 is blown away and removed by compressed gas such as compressed air PA discharged from the air discharge section 120 toward the heat exchanger 113. In addition, since the air discharge section 120 does not discharge liquid such as cooling water, liquid such as cooling water is prevented from adhering to the heat exchanger 113, and dust is prevented from accumulating or adhering to the heat exchanger 113. Therefore, according to the gas compression device 100 of this embodiment, it is possible to prevent dust from accumulating and adhering to the heat exchanger 113, which cools at least one of the compressed gas and the lubricating oil LO separated from the compressed gas by heat exchange with the cooling air CA, and suppress a decrease in the cooling performance of the heat exchanger 113.

In addition, in the gas compression device 100 of this embodiment, the gas release section 120 has a direction variable mechanism 121 that changes the gas release direction De in which the compressed gas is released by utilizing the pressure of the compressed gas, as shown in Figures 2A to 2C.

With this configuration, the gas compression device 100 of this embodiment can release compressed gas from the air release section 120 toward the heat exchanger 113 to remove dust adhering to the heat exchanger 113, and release the compressed gas toward a wider area of the heat exchanger 113. Therefore, according to the gas compression device 100 of this embodiment, it is possible to prevent dust from accumulating and adhering to a wider area of the heat exchanger 113, and more effectively suppress a decrease in the cooling performance of the heat exchanger 113.

In the gas compression device 100 of this embodiment, the direction variable mechanism 121 has, for example, an elastic member 122 whose elastic deformation amount changes according to the pressure of the compressed gas, and a direction variable section 123 whose air release direction De changes according to the elastic deformation amount of the elastic member 122, as shown in Figures 2A to 2C.

With this configuration, the gas compression device 100 of this embodiment can change the pressure of the compressed gas and change the discharge direction De when releasing the compressed gas from the discharge section 120 toward the heat exchanger 113 to remove dust adhering to the heat exchanger 113. More specifically, for example, in the gas compression device 100, immediately after the compression of the air A by the compression section 105 is stopped, the pressure of the compressed air PA is hardly reduced.

Therefore, immediately after the compression section 105 stops, for example, as shown in FIG. 2B, the maximum force Fa of the compressed air PA acts on the direction variable section 123, the amount of elastic deformation of the elastic member 122 becomes maximum, and the compressed air PA is discharged from the direction variable section 123 in the air release direction De diagonally forward to the left. After that, as the pressure of the compressed air PA gradually decreases, the amount of elastic deformation of the elastic member 122 gradually decreases, the direction variable section 123 rotates circumferentially around the central axis Aa, and the air release direction De changes to the right.

2C, the amount of elastic deformation of the elastic member 122 is minimized, and the compressed air PA is discharged from the direction variable section 123 in the air release direction De diagonally forward to the right. Therefore, according to the gas compression device 100 of this embodiment, the pressure of the compressed air PA supplied to the air release section 120 can be changed, and the air release direction De of the air release section 120 can be changed by the direction variable mechanism 121. Note that when changing the pressure of the compressed air PA supplied to the air release section 120 in the gas compression device 100, the compression of the air A by the compression section 105 may be controlled without stopping, and the output of the compression section 105 may be controlled, for example, by controlling the rotation speed of the screw rotor.

In the gas compression device 100 of this embodiment, the air discharge section 120 is provided downstream of the heat exchanger 113 in the flow direction of the cooling air CA, for example, as shown in FIG. 1. The air discharge direction De of the air discharge section 120 includes a directional component opposite to the flow direction of the cooling air CA.

With this configuration, the gas compression device 100 of this embodiment can blow away and remove dust adhering to the heat exchanger 113 using compressed gas that has a directional component in the opposite direction to the direction in which the dust contained in the cooling air CA collides with and adheres to the heat exchanger 113. This makes it possible to more effectively remove dust adhering to the heat exchanger 113 compared to a case in which the compressed gas released toward the heat exchanger 113 does not have the directional component in the opposite direction.

The gas compression device 100 of this embodiment further includes a control unit 118 that controls the operation of the compression unit 105 and the air release valve 110, as shown in FIG. 1. When the compression of gas by the compression unit 105 is stopped, the control unit 118 switches the supply destination of the compressed gas from the discharge port 117 to the air release flow path 109.

With this configuration, the gas compression device 100 of this embodiment can open the air release valve 110 when the control unit 118 stops compressing the gas by the compression unit 105, and supply the compressed air PA accumulated in the device to the air release unit 120. This allows the compressed air PA accumulated in the device, which could have been gradually lost due to leakage from the device in the past, to be released from the air release unit 120 toward the heat exchanger 113, and dust adhering to the heat exchanger 113 can be automatically removed.

Therefore, according to the gas compression device 100 of this embodiment, dust can be more reliably prevented from accumulating on the heat exchanger 113 compared to manually removing dust adhering to the heat exchanger 113. This prevents abnormal temperature increases in the compressed gas and lubricating oil LO, preventing abnormal shutdowns of the device, and preventing declines in productivity of production facilities such as factories and delays in production plans, thereby preventing economic losses.

The gas compression device 100 of this embodiment also includes a control unit 118 that controls the operation of the compression unit 105 and the air release valve 110, as described above. The control unit 118 continues the compression of the gas by the compression unit 105, distributes the compressed gas to the discharge flow path 108 and the air release flow path 109 by the air release valve 110, and performs an unloading operation to reduce the pressure of the compressed gas discharged from the discharge port 117.

With this configuration, the gas compression device 100 of this embodiment can release compressed gas from the air release section 120 toward the heat exchanger 113 during unloaded operation, thereby removing dust that has adhered to the heat exchanger 113. Therefore, it is possible to remove dust that has adhered to the heat exchanger 113 by using the compressed gas during unloaded operation, which was previously released to the outside without being effectively used, thereby making effective use of the energy consumed in the compression section 105 and reducing energy consumption during maintenance.

The maintenance method for the gas compression device 100 of this embodiment is a method of removing dust accumulated in the heat exchanger 113 by operating the air release valve 110 to supply compressed gas from the compression section 105 to the air release flow path 109 and releasing the compressed gas from the air release section 120 toward the heat exchanger 113.

With this configuration, dust adhering to the heat exchanger 113 is blown away and removed by compressed gas such as compressed air PA discharged from the air discharge section 120 toward the heat exchanger 113. In addition, since the air discharge section 120 does not discharge liquid such as cooling water, the adhesion of liquid such as cooling water to the heat exchanger 113 is prevented, and dust accumulation and adhesion to the heat exchanger 113 are prevented. Therefore, according to the maintenance method for the gas compression device 100 of this embodiment, it is possible to prevent dust accumulation and adhesion to the heat exchanger 113, which cools at least one of the compressed gas and the lubricating oil LO separated from the compressed gas by heat exchange with the cooling air CA, and suppress a decrease in the cooling performance of the heat exchanger 113.

As described above, according to this embodiment, it is possible to provide a gas compression device 100 and a maintenance method thereof that can suppress the accumulation of dust on the heat exchanger 113, which cools at least one of the compressed gas and the lubricating oil LO separated from the compressed gas by heat exchange with the cooling air CA, and thereby suppress a decrease in the cooling performance of the heat exchanger 113. Note that the gas compression device according to the present disclosure is not limited to the gas compression device 100 of the above-mentioned embodiment.

Below, with reference to Figures 3A to 6B, variants 1 to 4 of the gas compression device 100 of the aforementioned embodiment will be described. In the gas compression devices of each variant, the configuration of the air release sections 120A, 120B, 120C, and 120D differs from the air release section 120 of the gas compression device 100 of the aforementioned embodiment. The other configurations of the gas compression devices of each variant are similar to those of the gas compression device 100 of the aforementioned embodiment, so similar parts are given the same reference numerals and descriptions are omitted.

Figure 3A is a cross-sectional view showing a first modified example of the air release section 120 of the gas compression device 100 of Figure 1. Figure 3B is a cross-sectional view showing the bent state of the air release section 120A of Figure 3A. The air release section 120A of this modified example has a direction variable mechanism 121A that changes the air release direction De in which the compressed gas is released by utilizing the pressure of the compressed gas, similar to the air release section 120 of the above-mentioned embodiment. The direction variable mechanism 121A has an elastic member 122A whose elastic deformation amount changes according to the pressure of the compressed gas, and a direction variable section 123A whose air release direction De changes according to the elastic deformation amount of the elastic member 122A.

More specifically, the elastic member 122A is provided on a part of the circumferential direction on the outer peripheral surface of the tip of the air discharge flow path 109 and the base end of the direction variable part 123A, and connects the tip of the air discharge flow path 109 and the base end of the direction variable part 123A. The elastic member 122A is, for example, composed of a leaf spring or a torsion spring. For example, when the pressure of the compressed air PA is high, the elastic deformation amount of the elastic member 122A increases so as to reduce the angle θ between the central axis Ac of the air discharge flow path 109 and the central axis Aa of the direction variable part 123A, as shown in FIG. 3A. Also, when the pressure of the compressed air PA decreases, the elastic deformation amount of the elastic member 122A decreases so as to increase the angle θ between the central axis Ac of the air discharge flow path 109 and the central axis Aa of the direction variable part 123A, as shown in FIG. 3B.

With this configuration, as with the air release section 120 of the above-mentioned embodiment, when compressed gas is released from the air release section 120A toward the heat exchanger 113 to remove dust adhering to the heat exchanger 113, the pressure of the compressed gas can be changed to change the air release direction De. Therefore, as with the gas compression device 100 described above, the gas compression device of this modified example equipped with the air release section 120A can prevent dust from accumulating and adhering over a wider area of the heat exchanger 113, and more effectively suppress deterioration of the cooling performance of the heat exchanger 113.

Figure 4A is a perspective view showing modified example 2 of the air release section 120 of the gas compression device 100 of Figure 1. Figures 4B and 4C are cross-sectional views of the air release section 120B of this modified example shown in Figure 4A at the IVb-IVb section. Note that Figure 4A omits the illustration of support sections 124B and the like arranged at both ends of the air release section 120B.

In this modified example, the air release section 120B has a direction variable mechanism 121B that changes the air release direction De in which the compressed gas is released by utilizing the pressure of the compressed gas, similar to the air release section 120 in the previous embodiment. The direction variable mechanism 121B also has an elastic member (not shown) such as a torsion spring whose elastic deformation amount changes according to the pressure of the compressed gas, and a direction variable section 123B in which the air release direction De changes according to the elastic deformation amount of the elastic member.

The direction-changing mechanism 121B of this modified example also includes a support portion 124B, a piston 125B, and a cylinder 126B, as shown in Figures 4B and 4C.

As shown in FIG. 4A, the direction variable section 123B has, for example, a cylindrical main body 123B1 with both ends closed, and protrusions 123B2 provided at both ends of the main body 123B1. The main body 123B1 has, for example, a pair of gas introduction holes 123B3 provided at both ends, and a number of blowholes 123B4 provided in the middle section excluding both ends.

The pair of gas introduction holes 122B3 at both ends of the main body 123B1 are, for example, slit-shaped extending in the circumferential direction of the cylindrical main body 123B1, and introduce compressed air PA into the inside of the main body 123B1. The multiple blowholes 123B4 in the middle of the main body 123B1 are, for example, round holes penetrating the cylindrical wall of the main body 123B1 on the 180-degree opposite side to the protrusion 123B2 in the circumferential direction, and are arranged at equal intervals in the longitudinal direction of the main body 122B1.

The protrusions 123B2 of the direction variable section 123B are provided on both longitudinal ends of the main body 123B1, on the circumferential opposite side of the multiple blowholes 123B4 provided in the cylindrical main body 123B1. The protrusions 123B2 protrude from the outer peripheral surface of the main body 123B1 in the radial direction of the main body 123B1.

As shown in Figures 4B and 4C, the support portion 124B has a partially cylindrical support surface 124B1 and an air passage 124B2 connected to the air discharge flow path 109. The support surfaces 124B1 of the pair of support portions 124B have an inner diameter that is slightly larger than the outer diameter of the main body portion 123B1 of the direction variable portion 123B, for example, and support the cylindrical main body portion 123B1 at both ends of the direction variable portion 123B so that it can rotate in the circumferential direction.

The air passage 124B2 is a passage that connects the end of the air discharge passage 109 shown in FIG. 1 with the gas introduction hole 123B3 provided in the main body 123B1 of the direction variable part 123B shown in FIGS. 4A to 4C. The air passage 124B2 allows the compressed air PA supplied from the air discharge passage 109 to flow into the gas introduction hole 123B3.

Piston 125B is housed in cylinder 126B, for example, and its tip abuts against protrusion 123B2 of direction variable section 123B. Piston 125B has a semispherical tip, for example, and a cylindrical shape except for the tip. Cylinder 126B is, for example, a cylindrical member with an inner diameter slightly larger than the outer diameter of piston 125B, and piston 125B is inserted into its tip. The end of cylinder 126B opposite the tip is, for example, connected to air discharge flow path 109.

The elastic member of the direction-changing mechanism 121B (not shown) is provided to apply a moment, i.e., a circumferential force Fa, to the cylindrical main body 123B1. More specifically, the elastic member of the direction-changing mechanism 121B has a greater amount of elastic deformation in the state shown in FIG. 4B than in the state shown in FIG. 4C. When the amount of elastic deformation of the elastic member increases, the circumferential force Fa acting on the main body 123B1 increases in the direction in which the protrusion 123B2 pushes the piston 125B into the cylinder 126B.

With the above-mentioned configuration, when compressed air PA is supplied from the air release flow path 109 to the air release section 120B of this modified example, the compressed air PA is introduced into the cylinder 126B connected to the air release flow path 109. As a result, as shown in FIG. 4C, the pressure of the compressed air PA acts on the piston 125B housed in the cylinder 126B, and as shown in FIG. 4B, the piston 125B is pushed out of the cylinder 126B. As a result, a force acts from the tip of the piston 125B to the protrusion 123B2 of the direction variable section 123B, and the direction variable section 123B rotates from the state shown in FIG. 4C to the state shown in FIG. 4B.

The compressed air PA supplied from the air discharge flow path 109 to the air passage 124B2 of the support part 124B is introduced into the main body part 123B1 of the direction variable part 123B through the gas inlet hole 123B3 of the direction variable part 123B. The compressed air PA introduced into the main body part 123B1 is discharged from the multiple blowholes 123B4 toward the heat exchanger 113 in the air discharge direction De along the center line of each blowhole 123B4.

After that, when the pressure of the compressed air PA supplied from the air release flow path 109 to the air release section 120B decreases, the force acting from the tip of the piston 125B to the protrusion 123B2 of the direction variable section 123B decreases. Then, the moment due to the force acting from the piston 125B to the direction variable section 123B becomes smaller than the moment due to the force Fa acting from the elastic member of the direction variable mechanism 121B to the direction variable section 123B.

As a result, the direction variable section 123B rotates from the state shown in FIG. 4B to the state shown in FIG. 4C in response to a decrease in pressure of the compressed air PA, and the discharge direction De of the compressed air PA discharged from the multiple blowholes 123B4 toward the heat exchanger 113 changes. Therefore, according to the air discharge section 120B of this modified example, as with the air discharge section 120 of the above-mentioned embodiment, the pressure of the compressed air PA supplied to the air discharge section 120B can be changed, and the air discharge direction De of the air discharge section 120B can be changed by the direction variable mechanism 121B.

As described above, the gas compression device equipped with the air release section 120B of this modified example can prevent dust from accumulating and adhering over a wide area of the heat exchanger 113, as with the gas compression device 100 of the previously described embodiment, and can effectively suppress a decrease in the cooling performance of the heat exchanger 113.

Figure 5 is a cross-sectional view showing modified example 3 of the air release section 120 of the gas compression device 100 of Figure 1. Like the air release section 120 of the above-mentioned embodiment, the air release section 120C of this modified example has a direction variable mechanism 121C that changes the air release direction De in which the compressed air PA is released by utilizing the pressure of the compressed air PA. The direction variable mechanism 121C has an elastic member 122C whose elastic deformation amount changes according to the pressure of the compressed air PA, and a direction variable section 123C whose air release direction De changes according to the elastic deformation amount of the elastic member 122C. The direction variable mechanism 121C may also have, for example, a stopper 125C.

The elastic member 122C is, for example, a coil spring similar to the elastic member 122 in the above-mentioned embodiment. The direction variable part 123C is, for example, a tubular member whose tip is closed and whose base end opposite the tip is formed with a flange part 123C1. A blow hole 123C2 is provided in the tube wall of the tip of the direction variable part 123C, and the base end of the direction variable part 123C is inserted into the tip of the air discharge flow path 109. In addition, the stopper 125C is, for example, provided so as to protrude from the inner surface of the tip of the air discharge flow path 109 toward the central axis Ac of the air discharge flow path 109. The elastic member 122C is, for example, disposed between the stopper 125C and the flange part 123C1 of the direction variable part 123C.

With this configuration, when compressed air PA is introduced from the air release passage 109 into the opening at the base end of the direction variable part 123C, a force acts on the direction variable part 123C in a direction from the base end to the tip. As a result, the elastic member 122C is compressed and elastically deformed, the direction variable part 123C protruding from the tip of the air release passage 109 extends, and the compressed air PA is released from the blower hole 123C2 in an air release direction De perpendicular to the central axis Ac of the air release passage 109 toward the heat exchanger 113.

After that, when the pressure of the compressed air PA supplied from the air release flow path 109 to the direction variable part 123C decreases, the force acting from the compressed air PA on the direction variable part 123C in the direction from the base end to the tip decreases. As a result, the amount of elastic deformation of the elastic member 122C decreases, and the direction variable part 123C protruding from the tip of the air release flow path 109 contracts, changing the position of the air hole 123C2 in the direction of the central axis Ac of the air release flow path 109, thereby changing the air release direction De of the compressed air PA.

Therefore, according to the air release section 120C of this modified example, similar to the air release section 120 of the previously described embodiment, the pressure of the compressed air PA supplied to the air release section 120C can be changed, and the direction variable mechanism 121C can change the air release direction De of the compressed air PA by the air release section 120C. As a result, according to the gas compression device equipped with the air release section 120C of this modified example, similar to the gas compression device 100 of the previously described embodiment, it is possible to prevent the accumulation and adhesion of dust over a wide area of the heat exchanger 113, and effectively suppress a decrease in the cooling performance of the heat exchanger 113.

Figure 6A is a perspective view showing a fourth modified example of the air release section 120 of the gas compression device 100 of Figure 1. Figure 6B is a front view of the air release section 120D of Figure 6A as viewed from the direction of the central axis Ac of the air release flow path 109. The air release section 120D of this modified example has a direction variable mechanism 121D that uses the pressure of the compressed air PA to change the air release direction De in which the compressed air PA is released.

In the gas compression device of this modified example, the direction variable mechanism 121D has a rotating part 122D that is rotatably arranged around the central axis Ac of the air discharge flow passage 109, and an extension part 123D that extends from the rotating part 122D in a direction intersecting the central axis Ac. The direction variable mechanism 121D also has an air discharge nozzle 124D that is arranged at the tip of the extension part 123D and discharges compressed gas in an air discharge direction De that has a directional component in the tangential direction of a circle centered on the central axis Ac.

With this configuration, when compressed air PA is supplied from the air discharge flow path 109 to the air discharge section 120D of this modified example, the compressed air PA is discharged in the air discharge direction De toward the heat exchanger 113 through the rotating section 122D, the extending section 123D, and the air discharge nozzle 124D. In addition, a force in the opposite direction to the air discharge direction De acts on the air discharge nozzle 124D due to the reaction of the compressed air PA discharged in the air discharge direction De.

Here, since the air release direction De has a directional component in the tangential direction of a circle centered on the central axis Ac of the air release flow path 109, the force acting on the air release nozzle 124D in the opposite direction to the air release direction De also has a directional component in the tangential direction of a circle centered on the central axis Ac of the air release flow path 109. As a result, a moment is generated via the air release nozzle 124D and the extension portion 123D that rotates the rotating portion 122D, and the rotating portion 122D rotates, causing the extension portion 123D and the air release nozzle 124D to rotate around the central axis Ac of the air release flow path 109.

As a result, the discharge direction De of the compressed air PA discharged from the air discharge nozzle 124D toward the heat exchanger 113 changes. In this manner, according to the air discharge section 120D of this modified example, the pressure of the compressed air PA supplied from the air discharge flow path 109 to the air discharge section 120D can be used to change the discharge direction De of the compressed air PA by the air discharge section 120D.

Therefore, according to the gas compression device equipped with the gas release section 120D of this modified example, as with the gas compression device 100 of the above-mentioned embodiment, it is possible to prevent dust from accumulating and adhering over a wide area of the heat exchanger 113, and effectively suppress a decrease in the cooling performance of the heat exchanger 113. Note that, in the example shown in Figures 6A and 6B, a configuration in which the direction variable mechanism 121D includes a pair of extension sections 123D and a pair of gas release nozzles 124D has been described, but the number of extension sections 123D and gas release nozzles 124D is not particularly limited.

In addition, the air release section 120D of this modified example can adjust the rotation speed of the extension section 123D and the air release nozzle 124D by adjusting the friction coefficient of the rotating section 122D of the direction variable mechanism 121D. Therefore, the rotation speed of the extension section 123D and the air release nozzle 124D can be adjusted to a rotation speed that is highly effective in removing dust adhering to the heat exchanger 113.

In addition, the air release section 120D of this modified example can change the air release direction De of the compressed air PA without changing the pressure of the compressed air PA. Therefore, dust can be removed from a wide range of the heat exchanger 113 for a long period of time while maintaining the pressure of the compressed air PA, which is highly effective in removing dust adhering to the heat exchanger 113.

The above describes in detail the embodiments and variations of the gas compression device according to the present disclosure using the drawings, but the specific configuration is not limited to these embodiments and variations, and even if there are design changes and the like within the scope of the gist of this disclosure, they are still included in this disclosure.

100 Gas compression device 105 Compression section 108 Discharge flow path 109 Air release flow path 110 Air release valve 113 Heat exchanger 117 Discharge port 118 Control section 118
120 Air release section 121 Direction variable mechanism 121A Direction variable mechanism 121B Direction variable mechanism 121C Direction variable mechanism 121D Direction variable mechanism 122 Elastic member 122A Elastic member 122C Elastic member 122D Rotating section 123 Direction variable section 123A Direction variable section 123B Direction variable section 123C Direction variable section 123D Extension section 124D Air release nozzle A Air (gas)
Ac: central axis CA: cooling air De: air discharge direction LO: lubricating oil PA: compressed air (compressed gas)

Claims (8)

a compression section that is supplied with lubricating oil and compresses a gas;
a heat exchanger that cools at least one of the compressed gas compressed in the compression section and the lubricating oil separated from the compressed gas by heat exchange with cooling air;
a discharge port for discharging the compressed gas;
an air release valve that opens and closes an air release flow path that branches off from a discharge flow path between the compression section and the discharge port;
a discharge section provided at an end of the air discharge passage for discharging the compressed gas toward the heat exchanger. The gas compression device according to claim 1, characterized in that the air release section has a direction variable mechanism that uses the pressure of the compressed gas to change the air release direction in which the compressed gas is released. The gas compression device according to claim 2, characterized in that the direction-changing mechanism has an elastic member whose elastic deformation amount changes according to the pressure of the compressed gas, and a direction-changing part whose air release direction changes according to the elastic deformation amount of the elastic member. The gas compression device according to claim 2, characterized in that the direction variable mechanism has a rotating part that is rotatably arranged around the central axis of the air discharge flow passage, an extension part that extends from the rotating part in a direction intersecting the central axis, and an air discharge nozzle that is arranged at the tip of the extension part and discharges the compressed gas in the air discharge direction having a directional component in the tangential direction of a circle centered on the central axis. The air release section is provided downstream of the heat exchanger in a flow direction of the cooling air,
3. The gas compression device according to claim 2, wherein the discharge direction includes a directional component opposite to a flow direction of the cooling air. Further comprising a control unit for controlling the operation of the compression unit and the release valve,
2. The gas compression device according to claim 1, wherein the control unit switches a supply destination of the compressed gas from the discharge port to the air release flow path when the compression of the gas by the compression unit is stopped. Further comprising a control unit for controlling the operation of the compression unit and the release valve,
The gas compression device according to claim 1, characterized in that the control unit continues compressing the gas by the compression unit and distributes the compressed gas to the discharge flow path and the air release flow path by the air release valve, thereby performing an unloading operation to reduce a pressure of the compressed gas discharged from the discharge port. A maintenance method for a gas compression device according to claim 1, comprising the steps of:
A maintenance method for a gas compression device, comprising the steps of: operating the air release valve to supply the compressed gas from the compression section to the air release flow path; and releasing the compressed gas from the air release section toward the heat exchanger, thereby removing dust accumulated in the heat exchanger.

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