Gas compression device

Abstract

To provide a gas compression device capable of enhancing specific energy at the time of manufacturing compression gas while actualizing an isothermal compression process for compression gas such as air.SOLUTION: A gas compression device 10 using a liquid piston for compressing gas captured into a cylinder tank 1, includes liquid filling means 6 for filling liquid into the cylinder tank 1, heat absorbing means 13 for absorbing compression heat into the liquid with direct heat exchange between compression gas generated in the cylinder tank 1 and a liquid dispersion flow while changing the liquid filled into the cylinder tank 1 into the liquid dispersion flow composed of liquid droplets and / or liquid films, cooling means 71 for cooling the liquid with indirect heat exchange between the liquid absorbing the compression heat and a cooling medium supplied from an outsider system, and control means 7 for controlling the operation of the heat absorbing means 13 and the cooling means 71. The control means 7 allows the operation of the cooling means 71 in a period for the operation of the heat absorbing means 13 to discharge compression heat via the cooling medium to the outside system.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a gas compression device for compressing gas.

Background Art

[0002] Conventionally, electric air compressors such as screw type, scroll type, rotary vane type, and reciprocating piston type have been widely used. These air compressors are devices that adiabatically compress the inhaled air by a mechanical compression mechanism to produce compressed air at a required pressure. In the mechanical compression mechanism, after a certain operation time elapses, air leakage of the compressed air occurs due to wear of the gas seal part (specifically, rotor tooth groove part, tip seal, slide vane, piston ring, etc.), and a decrease in volumetric efficiency is likely to occur.

[0003] Also, in the adiabatic compression process, the gas phase part holds the compression heat generated by the increase in the kinetic energy of molecules and becomes high temperature, and the air in the compression process tends to expand against compression. Therefore, in this type of air compressor, the specific energy is directly related to the running cost.

[0004] In view of the characteristics of such a mechanical compression mechanism, a liquid pump type gas compression device disclosed in, for example, Patent Documents 1 and 2 has been studied for a long time.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Patent Document 2

Summary of the Invention

Problems to be Solved by the Invention

[0006] A liquid pump type gas compression device is configured to compress air inside a cylinder tank by sending a liquid (typically water) from the lower part of the cylinder tank into which atmospheric air is taken in, using a liquid pump. That is, the liquid filled inside the cylinder tank serves as a piston, and as the liquid level rises, the compression of air progresses. The devices disclosed in Patent Documents 1 and 2 have a configuration in which a liquid piston is alternately moved between two cylinder tanks to periodically produce compressed air. And during the production of compressed air, an operation control of continuously driving the liquid pump is adopted.

[0007] In the air compression process, since the contact surface between the cylinder tank corresponding to the cylinder and the liquid piston is completely sealed, there is no leakage of compressed air back, and high volumetric efficiency is maintained. However, continuously driving the liquid pump increases the power consumption, and there is a problem that it is difficult to obtain the expected specific energy.

[0008] Also, since a part of the compression heat generated during the compression process is absorbed by the liquid through the liquid level of the liquid piston, an intermediate compression process between adiabatic compression and isothermal compression (quasi-isothermal compression process) is realized. However, it is far from a complete isothermal compression process, and there is still room for further improvement in terms of specific energy. In view of the above problems, an object of the present invention is to provide a gas compression device capable of realizing an isothermal compression process for a compressible gas such as air and increasing the specific energy during the production of compressed gas.

Means for Solving the Problems

[0009] The gas compression device according to the present invention is a gas compression device that compresses the gas taken into the cylinder tank by a liquid piston, and includes a liquid injection means for injecting a liquid into the cylinder tank, and a liquid injection means for injecting the liquid into the cylinder tank. While changing the liquid into a liquid dispersion flow composed of liquid droplets and / or a liquid film, the heat absorption means for absorbing the compression heat by the liquid by the direct heat exchange between the compressed gas generated in the cylinder tank and the liquid dispersion flow, and the liquid that has absorbed the compression heat and the cooling medium supplied from outside the system. Cooling means for cooling the liquid by indirect heat exchange, and control means for controlling the operations of the heat absorption means and the cooling means, and the control means discharges the compression heat to the outside of the system through the cooling medium by operating the cooling means during the operation period of the heat absorption means. According to this configuration, an isothermal compression process for a compressible gas such as air can be realized, and the specific energy during the production of the compressed gas can be increased.

[0010] More specifically, as the above configuration, the liquid injection means may include a liquid pump, and the cooling means may include an indirect heat exchanger that cools the liquid discharged from the liquid pump. More specifically, as the above configuration, the indirect heat exchanger may be a plate heat exchanger disposed in a pipe through which the liquid flows.

[0011] More specifically, as the above configuration, the cooling means may include an indirect heat exchanger that cools the liquid filled in the cylinder tank. More specifically, as the above configuration, the indirect heat exchanger may include one or a plurality of heat transfer pipes disposed in the liquid filling region in the cylinder tank. More specifically, as the above configuration, a water circulation circuit for circulating cooling water as a cooling medium through the indirect heat exchanger, and a cooling tower for cooling the cooling water circulating through the water circulation circuit by heat exchange with cooling air may be provided.

Effects of the Invention

[0012] According to the gas compression device of the present invention, an isothermal compression process for a compressible gas such as air can be realized, and the specific energy during the production of the compressed gas can be increased.

Brief Description of the Drawings

[0013]

Figure 1

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Figure 10

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Modes for Carrying Out the Invention

[0014] Each embodiment of the present invention will be described below with reference to the respective drawings.

[0015] 1. First Embodiment (1) Device Configuration of Gas Compression Device FIG. 1 is a configuration diagram showing a schematic configuration of a gas compression device 10 according to the first embodiment. The gas compression device 10 is a liquid pump type gas compression device.

[0016] As shown in FIG. 1, the gas compression device 10 includes two cylinder tanks 1A and 1B, an intake mechanism 2, and an exhaust mechanism 3. By sending a liquid L from the lower part of each of the cylinder tanks 1A and 1B, the air contained inside each of the cylinder tanks 1A and 1B can be compressed. Regarding the type of the liquid L, as will be described later, clean water is preferable, but other types of liquids may be used as long as the gist of the present invention is not deviated from.

[0017] The gas compression device 10 is provided with a pressure sensor Px for detecting the gas phase pressure inside each of the cylinder tanks 1A and 1B. The air inside the cylinder tank 1A can be discharged by opening the air vent valve 14A as needed, and the air inside the cylinder tank 1B can be discharged by opening the air vent valve 14B as needed.

[0018] The intake mechanism 2 communicates with the upper spaces of the cylinder tanks 1A and 1B, and includes an intake line 21A provided corresponding to the cylinder tank 1A and an intake line 21B provided corresponding to the cylinder tank 1B. An intake valve 22A is provided in the intake line 21A, and an intake valve 22B is provided in the intake line 21B.

[0019] The intake valve 22A opens (is in an open state) when the internal pressure of the cylinder tank 1A falls below the first pressure, and closes (is in a closed state) when the internal pressure of the cylinder tank 1A exceeds the second pressure which is equal to or higher than the first pressure. The intake valve 22B opens when the internal pressure of the cylinder tank 1B falls below the first pressure, and is a valve that closes when the internal pressure of the cylinder tank 1B exceeds the second pressure which is equal to or higher than the first pressure. The intake valves 22A and 22B can be constituted by self-operated valves or automatic valves that operate at a required pressure. In this embodiment, as an example, it is assumed that the intake valves 22A and 22B are constituted by self-operated valves.

[0020] When the intake valves 22A and 22B are self-operated valves, a check valve can be applied as shown in the configuration diagram of FIG. 1. In this case, the check valve opens when the secondary pressure falls below the first pressure (i.e., when it becomes a negative pressure), and closes when it exceeds the second pressure (i.e., when it becomes a positive pressure).

[0021] When the intake valves 22A and 22B are automatic valves, an electric drive valve (solenoid valve or electric valve) can be applied. In this case, the electric drive valve opens when the detected pressure of the pressure sensor Px falls below the first pressure, and closes when it exceeds the second pressure. The first pressure and the second pressure in this case can be set to appropriate values in the control means 7, for example.

[0022] The exhaust mechanism 3 communicates with the upper spaces of the cylinder tanks 1A and 1B. The exhaust mechanism 3 has an exhaust line 31A provided corresponding to the cylinder tank 1A and an exhaust line 31B provided corresponding to the cylinder tank 1B. An exhaust valve 32A is provided in the exhaust line 31A, and an exhaust valve 32B is provided in the exhaust line 31B.

[0023] The exhaust valve 32A is a valve that closes when the internal pressure of the cylinder tank 1A falls below the third pressure and opens when the internal pressure of the cylinder tank 1A exceeds the fourth pressure which is equal to or higher than the third pressure. The exhaust valve 32B is a valve that closes when the internal pressure of the cylinder tank 1B falls below the third pressure and opens when the internal pressure of the cylinder tank 1B exceeds the fourth pressure which is equal to or higher than the third pressure. The exhaust valves 32A and 32B can be constituted by self-operated valves or automatic valves that operate at a required pressure. In this embodiment, as an example, it is assumed that the exhaust valves 32A and 32B are constituted by self-operated valves.

[0024] When the exhaust valves 32A and 32B are self-operated valves, a back pressure valve (primary pressure regulating valve) can be applied as shown in the configuration diagram of FIG. 1. In this case, the back pressure valve closes when the primary pressure falls below the third pressure (a mechanically adjustable set value) and opens when it exceeds the fourth pressure (a mechanically adjustable set value which can be the same as the third pressure).

[0025] When the exhaust valves 32A and 32B are automatic valves, an electric drive valve (solenoid valve or motor-operated valve) can be used. In this case, the electric drive valve opens when the detected pressure of the pressure sensor Px falls below the third pressure and closes when it exceeds the fourth pressure. The third pressure and the fourth pressure in this case can be set to appropriate values in the control means 7, for example.

[0026] Note that when using the self-operated valve described above, since suction and discharge are actively performed without using electric power, from this viewpoint, it can contribute to the reduction of specific energy. On the other hand, when using the automatic valve described above, by selecting a valve type with a small pressure loss during suction and discharge, power-saving operation with less energy loss becomes possible, and thus from this viewpoint, it can contribute to the reduction of specific energy.

[0027] At the lower part of the cylinder tank 1A, a first liquid port 11A and a second liquid port 12A are provided. Also, at the lower part of the cylinder tank 1B, a first liquid port 11B and a second liquid port 12B are provided. A first liquid flow line 41A is connected to the first liquid port 11A, and a first liquid flow line 41B is connected to the first liquid port 11B. A second liquid flow line 51A is connected to the second liquid port 12A, and a second liquid flow line 51B is connected to the second liquid port 12B.

[0028] Also, the gas compression device 10 is provided with a liquid pump 6. Further, the gas compression device 10 includes a liquid suction line (suction side common line) 61 that connects the suction side of the liquid pump 6 to the first liquid flow lines 41A and 41B, and a liquid discharge line (discharge side common line) 62 that connects the discharge side of the liquid pump 6 to the second liquid flow lines 51A and 51B.

[0029] A first liquid flow control valve 42A is provided in the first liquid flow line 41A, and a first liquid flow control valve 42B is provided in the first liquid flow line 41B. A second liquid flow control valve 52A is provided in the second liquid flow line 51A, and a second liquid flow control valve 52B is provided in the second liquid flow line 51B.

[0030] When the first liquid flow control valves 42A and 42B corresponding to one of the cylinder tanks 1A and 1B are in an open state and the second liquid flow control valves 52A and 52B corresponding to the other of the cylinder tanks 1A and 1B are in an open state, when the liquid pump 6 is driven, the liquid L is transferred through the first liquid flow lines 41A and 41B corresponding to one of the cylinder tanks 1A and 1B, the liquid suction line 61, the liquid pump 6, the liquid discharge line 62, and the second liquid flow lines 51A and 51B corresponding to the other of the cylinder tanks 1A and 1B. That is, the liquid L is transferred from one of the cylinder tanks 1A and 1B to the other of the cylinder tanks 1A and 1B.

[0031] Further, a liquid feed check valve 611 is provided in the liquid suction line 61, and a flow rate sensor Fx (one form of flow rate detection means) is provided in the liquid discharge line 62. Note that the flow rate sensor Fx may be provided in the liquid suction line 61 or the liquid pump 6 instead of the liquid discharge line 62. By detecting a predetermined flow rate, the flow rate sensor Fx can detect the end of the expansion of the air inside the cylinder tanks 1A and 1B in the expansion / intake process described later.

[0032] In the gas compression device 10, instead of using the flow rate sensor Fx, alternative means may be used. For example, a flow switch (a switch that turns on when the set flow rate is reached or more and turns off when the set flow rate is not reached) or a magnetic sensor (a sensor that attaches a magnet to the drive shaft directly connected to the rotor (such as an impeller or gear) of the liquid pump 6 to detect the rotation speed) can be used as an alternative means to the flow rate sensor Fx.

[0033] In addition, a spray nozzle (injector) 13A for spraying the liquid L into the internal space is provided in the cylinder tank 1A, and a spray nozzle 13B for spraying the liquid L into the internal space is provided in the cylinder tank 1B. Further, the gas compression device 10 has a liquid introduction line 53A that branches from the second liquid circulation line 51A on the secondary side of the second liquid circulation control valve 52A and guides a part of the liquid being transferred by the liquid pump 6 to the spray nozzle 13A, and a liquid introduction line 53A that branches from the second liquid circulation line 51B on the secondary side of the second liquid circulation control valve 52B and guides a part of the liquid L being transferred by the liquid pump 6 to the spray nozzle 13B. A liquid introduction control valve 54A is provided in the liquid introduction line 53A, and a liquid introduction control valve 54B is provided in the liquid introduction line 53B.

[0034] In the compression and exhaust process described below, liquid L is sprayed from spray nozzle 13A onto the compressed air inside cylinder tank 1A, and liquid L is sprayed from spray nozzle 13B onto the compressed air inside cylinder tank 1B, thereby realizing an isothermal compression process. Spray nozzles 13A and 13B can use, for example, full-cone nozzles or hollow-cone nozzles, and are installed in cylinder tanks 1A and 1B so as to be able to spray liquid L onto the compressed air space of the air. Also, spray nozzles 13A and 13B may be arranged in the central region of the top plates of cylinder tanks 1A and 1B (positions on the central axis extending vertically above and below cylinder tanks 1A and 1B) so that the spray direction is downward.

[0035] Each cylinder tank 1A and 1B is provided with a liquid level detection electrode rod Lx (a form of liquid level detection means). By detecting that the liquid level of liquid L inside cylinder tanks 1A and 1B has reached a predetermined liquid level with the liquid level detection electrode rod Lx, the top dead center of the liquid piston in the compression and exhaust process can be detected.

[0036] An air filter 23 is provided upstream of the intake lines 21A and 21B. The air filter 23 can remove contaminants, bacteria, etc. contained in the air during intake.

[0037] A liquid discharge line 81 and a liquid supply line 83 are connected to the first liquid flow line 41A. Note that the liquid discharge line 81 and the liquid supply line 83 may be connected to any of cylinder tanks 1A and 1B, the second liquid flow lines 51A and 51B, the liquid suction line 61, and the liquid discharge line 62 instead of the first liquid flow line 41A. A liquid discharge valve 82 is provided in the liquid discharge line 81, and a liquid supply valve 84 is provided in the liquid supply line 83.

[0038] When water is used as the liquid L in the gas compression device 10, for example, contaminants and bacteria may not be sufficiently removed by the air filter 23, and there is a concern about water quality contamination and the growth of miscellaneous bacteria due to repeated intake air. In this regard, according to the configuration of the present embodiment, it is possible to periodically perform a blowdown of the retained water via the liquid discharge line 81 and the liquid discharge valve 82. Further, after the blowdown, it is also possible to replenish new water via the liquid supply line 83 and the liquid supply valve 84. Thereby, the liquid piston can be kept in a clean state, and clean compressed air without contamination can be supplied to the load equipment.

[0039] An air separator 91 is provided downstream of the exhaust lines 31A and 31B. The compressed air sent out from the exhaust lines 31A and 31B is subjected to gas-liquid separation by the air separator 91 and then accumulated in a reservoir tank (not shown) arranged on the downstream side. The liquid L separated by the air separator 91 is discharged from a drain trap 92 connected to the liquid reservoir portion of the air separator 91.

[0040] The liquid L intermittently discharged from the drain trap 92 is returned to the cylinder tank 1A or the cylinder tank 1B with a low liquid pressure by utilizing the pressure of the compressed air and the water head pressure in the air separator 91. A liquid return check valve 93A is provided in the line for returning the liquid L from the drain trap 92 to the cylinder tank 1A, and a liquid return check valve 93B is provided in the line for returning the liquid L from the drain trap 92 to the cylinder tank 1B. By installing the liquid return check valves 93A and 93B, the loss of the liquid L in these lines is prevented.

[0041] As described above, a reservoir tank (not shown) for accumulating compressed air is installed downstream of the air separator 91. Thereby, similar to the operation control of a general gas compression device, it is possible to control the operation and stop of the gas compression device 10 according to the internal pressure of the reservoir tank. In the gas compression device 10, it is also possible to omit the installation of the air separator 91 and adopt a configuration in which gas-liquid separation is performed by the reservoir tank. In this configuration, the drain trap 92 can be connected to the bottom of the reservoir tank.

[0042] A heat exchanger 71 for cooling the liquid L discharged from the liquid pump 6 is provided in the liquid discharge line 62. The heat exchanger 71 and the surrounding configuration and the like will be described in detail again.

[0043] Here, the configuration of the main control system of the gas compression device 10 is shown in FIG. 2. As shown in this figure, the gas compression device 10 is provided with control means 7. The control means 7 controls at least the operations of the elements of the process switching element group Z shown in FIG. 2 so that the gas compression device 10 operates normally.

[0044] The process switching element group Z includes elements of the liquid pump 6, each valve corresponding to the cylinder tank 1A (the first liquid flow control valve 42A, the second liquid flow control valve 52A, and the liquid introduction control valve 54A), and each valve corresponding to the cylinder tank 1B (the first liquid flow control valve 42B, the second liquid flow control valve 52B, and the liquid introduction control valve 54B). That is, the control means 7 controls the drive / stop of the liquid pump 6, the opening / closing of each of the first liquid flow control valves 42A, 42B, the opening / closing of each of the second liquid flow control valves 52A, 52B, and the opening / closing of the liquid introduction control valves 54A, 54B.

[0045] (2) Control content Next, the control content of the main operations in the gas compression device 10 will be described. FIG. 3 is an explanatory diagram schematically showing the transition of the control state of the gas compression device 10 (particularly, the control states of the cylinder tanks 1A and 1B). As shown in this figure, for the control state of the gas compression device 10, after passing through the control states A1 to A5 in order, and then passing through the control states B1 to B5 in order, it returns to the control state A1, and the same control state is repeated. The control states B1 to B5 are equivalent to the control states A1 to A5 when the control states are reversed between the cylinder tank 1A and the cylinder tank 1B.

[0046] Hereinafter, each of the above-described control states will be described in more detail with reference to FIGS. 4 to 9. Regarding each valve shown in FIGS. 4 to 9, those shown in black are in the closed state, and those shown in white are in the open state.

[0047] Figure 4 shows control state A1. Control state A1 is the state when the compression / exhaust process in cylinder tank 1A (the left tank in this figure) is completed and the state when the expansion / intake process in cylinder tank 1B (the right tank in this figure) is completed. Here, the liquid pump 6 is stopped, cylinder tank 1A has reached a predetermined upper liquid level (the top dead center of the liquid piston), and cylinder tank 1B has reached the lower liquid level (the bottom dead center of the liquid piston). The exhaust from cylinder tank 1A has ended, and the gas phase part has reached a pressure below the third pressure. However, compressible air that is close to the third pressure remains inside cylinder tank 1A.

[0048] Figure 5 shows control state A2. The switch from control state A1 to A2 is performed by switching the opening and closing of the first liquid flow control valves 42A, 42B and the second liquid flow control valves 52A, 52B by the control means 7. In control state A2, the expansion / intake process in cylinder tank 1A is started, and the compression / exhaust process in cylinder tank 1B is started. That is, the liquid L is sent out due to the expansion of the gas phase part in cylinder tank 1A, and partial compression and cooling of the gas phase part due to the intake of the liquid L are performed in cylinder tank 1B.

[0049] With the liquid pump 6 stopped, the transfer of the liquid L from cylinder tank 1A to cylinder tank 1B is started. The transfer is performed via the first liquid flow line 41A, the liquid suction line 61, the liquid pump 6, the liquid discharge line 62 (including the heat exchanger 71), and the second liquid flow line 51B. Specifically, the liquid L is sent out by utilizing the expansion of the gas phase part (the expansion of the remaining compressed air) and the head pressure of the liquid phase part in cylinder tank 1A. In this transfer, the liquid L is cooled when passing through the heat exchanger 71. Such cooling of the liquid L by the heat exchanger 71 continues in the subsequent control states A3 and A4 as well.

[0050] In the cylinder tank 1B, partial compression of the gas phase starts as the liquid level rises. Since the control means 7 controls the liquid introduction control valve 54B to be in an open state while filling the liquid L from the second liquid port 12B, the liquid L is sprayed from the spray nozzle 13B, and the compressed air in the cylinder tank 1B is cooled. The compression heat generated in the gas phase is absorbed by the sprayed liquid L and merges into the filling liquid L from the lower part of the cylinder tank 1B. That is, the absorption of the compression heat is performed through both the droplets of the liquid L sprayed from the upper part and the liquid surface of the liquid L filled from the lower part. Also, since the inside of the cylinder tank 1A is at a positive pressure (a pressure state exceeding the second pressure), the intake valve 22A remains closed.

[0051] Figure 6 shows the control state A3. In the control state A3, the expansion of the gas phase in the cylinder tank 1A is completed, the partial compression of the gas phase in the cylinder tank 1B is completed, and the overall compression of the gas phase starts.

[0052] When the detected flow rate by the flow rate sensor Fx drops to a predetermined flow rate, the liquid pump 6 in the stopped state is driven by the control means 7. When the expansion of the compressed air remaining in the cylinder tank 1A ends and the head pressure difference is balanced, the liquid pressure acting on the first liquid port 11A of the cylinder tank 1A (the sum of the air pressure in the gas phase and the head pressure in the liquid phase) and the liquid pressure acting on the second liquid port 12B of the cylinder tank 1B are balanced, so the delivery of the liquid L stops and the compression of the air becomes impossible.

[0053] Therefore, in the present embodiment, while the liquid pump 6 is stopped, when the detected flow rate drops to a predetermined flow rate (a set value that is higher than the lower limit flow rate value at which air compression becomes impossible by a differential value), the liquid pump 6 is driven to continue the delivery of the liquid L. As a result, the liquid pump 6 can be driven without delay to produce compressed air. That is, the liquid L flows at a sufficient flow rate in such a relationship that the liquid level in the cylinder tank 1A is higher than the liquid level in the cylinder tank 1B, and the liquid pump 6 is driven in a state where air compression can be performed. As described above, in the present embodiment, the stop of the liquid pump 6 is continued until a predetermined time during the expansion of the remaining compressed air, and then the liquid pump 6 is driven.

[0054] In the cylinder tank 1B, the isothermal compression process is continuing due to the cooling of the gas phase part (heat absorption into the aqueous phase part). However, before driving the liquid pump 6, as the liquid pressure in the cylinder tank 1A decreases, the spray flow rate from the spray nozzle 13B gradually decreases.

[0055] FIG. 7 shows the control state A4. In the control state A4, intake air is started due to the generation of negative pressure in the cylinder tank 1A, and overall compression and cooling of the gas phase part are performed in the cylinder tank 1B.

[0056] When the driving of the liquid pump 6 is continued, the liquid pressure in the cylinder tank 1A becomes lower than the liquid pressure in the cylinder tank 1B. When the gas phase part in the cylinder tank 1A turns into a negative pressure (a pressure state lower than the first pressure), the intake valve 22A is opened, and external air is taken into the cylinder tank 1A through the air filter 23.

[0057] In the cylinder tank 1B, the isothermal compression process is continuing due to the cooling of the gas phase part. After driving the liquid pump 6, the spray flow rate from the spray nozzle 13B recovers. Note that this spray flow rate gradually decreases as the head pressure (suction head of the liquid pump) in the cylinder tank 1A decreases.

[0058] Figure 8 shows control state A5. In control state A5, intake air continues to be drawn in due to the generation of negative pressure in cylinder tank 1A, and exhaust starts in cylinder tank 1B due to the set pressure in the gas phase being reached.

[0059] When pressure sensor Px detects that the gas phase of cylinder tank 1B has reached the fourth pressure, control means 7 determines that the isothermal compression process has ended, closes liquid introduction control valve 54B to stop the liquid spray from spray nozzle 13B, and opens exhaust valve 32B to start discharging compressed air. For the delivery of compressed air, the drive of liquid pump 6 continues.

[0060] The delivered compressed air is separated into gas and liquid by air separator 91 and then accumulated in a reservoir tank (not shown) arranged on the downstream side. The liquid L separated by air separator 91 is discharged from drain trap 92. The liquid L intermittently discharged from drain trap 92 is returned to the cylinder tank with a lower liquid pressure (here, cylinder tank 1A where the liquid level has dropped and the gas phase is in equilibrium with the atmospheric pressure due to intake air) by utilizing the pressure of the compressed air and the head pressure in air separator 91.

[0061] Note that in order to prevent liquid droplets from being entrained in the compressed air, the closing timing of liquid introduction control valve 54B may be made earlier than the opening timing of exhaust valve 32B. That is, liquid introduction control valve 54B may be closed at a set pressure lower than the fourth pressure.

[0062] Figure 9 shows control state B1. In control state B1, the expansion / intake process ends in cylinder tank 1A, and the compression / exhaust process ends in cylinder tank 1B.

[0063] In the cylinder tank 1B, when the top dead center (upper limit liquid level) of the liquid piston is detected by the liquid level detection electrode rod Lx, the control means 7 stops the liquid pump 6. At this time, the exhaust valve 32B is closed. Instead of this, in the cylinder tank 1B, when the detected pressure in the gas phase part by the pressure sensor Px drops to the third pressure (a set value lower than the differential value from the exhaust start pressure value by the differential value), the control means 7 may stop the liquid pump 6. At this time, the exhaust valve 32B is closed.

[0064] As described above, the compression and exhaust process is completed. As a result, at the end point of this process, compressed air surely remains in the cylinder tank 1B. As a result, immediately after switching to the expansion and intake process in the cylinder tank 1B, it is possible to send out the liquid L using the expansion of the gas phase part without driving the liquid pump 6, contributing to the reduction of specific energy.

[0065] The control state B1 corresponds to the control state A1 (see FIG. 4) when the control states between the cylinder tank 1A and the cylinder tank 1B are reversed. Thereafter, as already described, the control states B2 to B5 (the control states A2 to A5 when the control states between the cylinder tank 1A and the cylinder tank 1B are reversed) are passed through in order and return to the control state A1, and the same control state is repeated. In the control states B2 to B5, the expansion and intake process is executed in the cylinder tank 1B, and the compression and exhaust process is executed in the cylinder tank 1A.

[0066] As described above, the control means 7 according to the present embodiment controls the process switching element group Z so that when one cylinder tank (one of 1A and 1B) is in a control state of executing the compression / exhaust process, the other cylinder tank (the other of 1A and 1B) is in a control state of executing the expansion / intake process. Further, in the compression / exhaust process, the control means 7 ends the process by stopping the liquid pump 6 with compressed air remaining in the cylinder tanks 1A and 1B. Furthermore, in the expansion / intake process, the control means 7 continues to stop the liquid pump 6 until a predetermined time during the expansion of the remaining compressed air, and then drives the liquid pump 6. Therefore, according to the gas compression device 10, it is possible to achieve an improvement in specific energy by realizing an operation cycle by intermittent driving of the liquid pump 6.

[0067] In the expansion / intake process, with the liquid pump 6 stopped, the liquid L filled in the cylinder tanks 1A and 1B is sent out by utilizing at least the expansion of the gas phase part, preferably by utilizing the expansion of the gas phase part and the head pressure of the liquid phase part. Then, after a predetermined time during the expansion of the gas phase part, the liquid pump 6 is driven, and the external air is inhaled by utilizing the negative pressure of the gas phase part generated along with the further sending out of the liquid L.

[0068] In the compression / exhaust process, with the liquid pump 6 stopped, the gas phase part is partially compressed by taking in the liquid L. Then, when the liquid pump 6 is driven, the gas phase part is entirely compressed by further taking in the liquid L. And when the gas phase part reaches the set pressure, the generated compressed air is discharged.

[0069] Also, in the compression and exhaust process, the liquid pump 6 is stopped with compressed air remaining in the cylinder tank, thereby ending the process. Therefore, immediately after switching to the expansion and intake process, even if the stop of the liquid pump 6 is continued, the liquid L can be sent out by utilizing the expansion of the gas phase part. As a result, the gas compression device 10 according to the present invention periodically produces compressed air while intermittently driving the liquid pump 6. As a result, the specific energy can be significantly improved compared to the conventional type of device that continuously drives the liquid pump. Further, even if a liquid pump with a high suction and discharge capacity is installed, an increase in specific energy can be minimized.

[0070] (3) Regarding the heat absorption means and the cooling means As described above, the gas compression device 10 is a device that compresses the air (a form of gas) taken into the cylinder tanks 1A and 1B by a liquid piston, and includes a liquid pump 6 (a form of liquid injection means) that injects the liquid L into the cylinder tanks 1A and 1B, a means for absorbing the compression heat by the liquid L in the cylinder tanks 1A and 1B (hereinafter, may be conveniently referred to as "heat absorption means Q1"), and a means for cooling the liquid L that has absorbed the compression heat (hereinafter, may be conveniently referred to as "cooling means Q2").

[0071] The heat absorption means Q1 is configured to absorb the compression heat by the liquid L through direct heat exchange between the compressed gas generated in the cylinder tanks 1A and 1B and the liquid dispersed flow while changing the liquid L injected into the cylinder tanks 1A and 1B into a liquid (hereinafter, referred to as "liquid dispersed flow") composed of at least one of liquid droplets and a liquid film. More specifically, the heat absorption means Q1 includes spray nozzles 13A and 13B that spray the liquid into the cylinder tanks 1A and 1B, and liquid introduction lines 53A and 53B that separate a part of the liquid L being transferred by the liquid pump 6 and guide it to the spray nozzles 13A and 13B.

[0072] In the heat absorption means Q1, the spray nozzles 13A and 13B can change the liquid L sent from the liquid introduction lines 53A and 53B into fine mist-like droplets (a form of liquid dispersion flow) and discharge them toward the compressed air in the cylinder tanks 1A and 1B. Thereby, it is possible to absorb the compression heat into the liquid L by direct heat exchange between the compressed air generated in the cylinder tanks 1A and 1B and the liquid dispersion flow.

[0073] The cooling means Q2 cools the liquid L by indirect heat exchange between the liquid L that has absorbed the above-mentioned compression heat and the cooling water Wa (a form of cooling medium) supplied from outside the system (a path different from the flow path of the liquid L). FIG. 10 is a schematic configuration diagram of the heat exchanger 71 and its surroundings. As shown in this figure, the gas compression device 10 includes a water circulation circuit 72, a cooling tower 73, and a circulation pump 74. The cooling means Q2 of the present embodiment is configured to include the heat exchanger 71, the water circulation circuit 72, the cooling tower 73, the circulation pump 74, and the cooling water Wa. The circulation pump 74 is controlled by the control means 17. The water circulation circuit 72 is a flow path for circulating the cooling water Wa (cooling medium). The cooling tower 73 (for example, an open cooling tower) is a device that cools the cooling water Wa circulating in the water circulation circuit 72 by heat exchange with the cooling air Ar.

[0074] Also, the heat exchanger 7 is arranged so as to be interposed in the water circulation circuit 72. According to the configuration shown in FIG. 10, the cooling water Wa cooled by the cooling tower 73 is supplied to the heat exchanger 7. Thereby, the heat exchanger 7 functions as an indirect heat exchanger that cools the liquid L discharged from the liquid pump 6 by heat exchange with the cooling water Wa circulating in the circulation line 72. As the heat exchanger 71, for example, a plate heat exchanger is suitable, but other types of heat exchangers such as a shell and tube heat exchanger may be adopted.

[0075] In one of the cylinder tanks 1A and 1B, when the liquid L that has absorbed the compression heat is transferred to the other via a liquid pump 6 or the like, it will pass through the heat exchanger 71. At this time, when the circulation pump 74 is driven, in the heat exchanger 71, the liquid L that has absorbed the compression heat is cooled by indirect heat exchange with the cooling water Wa (a cooling medium supplied from outside the system) circulating in the water circulation circuit 72, and the compression heat moves from the liquid L to the cooling water Wa. Further, the cooling water Wa that has absorbed this compression heat reaches the cooling tower 73 through the water circulation circuit 72 and is cooled by heat exchange with the cooling air Ar. As a result, the compression heat is discharged outside the system via the cooling water Wa.

[0076] The operations of the spray nozzles 13A and 13B constituting the heat absorption means Q1 and the operation of the circulation pump 74 constituting the cooling means Q2 are controlled by the control means 7 described above. Further, the control means 7 is configured to discharge the compression heat outside the system via the cooling water Wa by operating the cooling means Q2 during the operating period of the heat absorption means Q1. Here, "operating the cooling means Q2 during the operating period of the heat absorption means Q1" is not limited to a form in which the operating period of the heat absorption means Q1 and the operating period of the cooling means Q2 completely coincide, but is a concept that also includes a form in which they partially coincide. There may be a case where the operating period of the cooling means Q2 is included in the operating period of the heat absorption means Q1, or a case where the operating periods of the heat absorption means Q1 and the cooling means Q2 partially overlap.

[0077] In the present embodiment, mainly in the control states A2 to A4 (see FIGS. 5 to 7) and the control states B2 to B4 described above, during the process of sending the liquid L that has absorbed the compression heat from one of the cylinder tanks 1A and 1B to the other, the cooling means Q2 operates, and the liquid L is cooled by indirect heat exchange with the cooling water Wa. Further, during all or part of the period when the cooling means Q2 is operating in this way, the heat absorption means Q1 on the side where the cooled liquid L is fed also operates, and the compression heat is absorbed by the liquid L by direct heat exchange with the liquid dispersion flow. In this way, by operating the cooling means Q2 during the operating period of the heat absorption means Q1, the compression heat can be efficiently removed, and an ideal isothermal compression process is realized.

[0078] Note that the specific forms of the heat absorption means Q1 and the cooling means Q2 are not limited to those described above, and various forms can be adopted without departing from the gist of the present invention. For example, as the cooling means Q2, an indirect heat exchanger that cools the liquid L filled in the cylinder tanks 1A and 1B may be adopted. An example of a gas compression device 10 employing such an indirect heat exchanger will be described below as the second embodiment.

[0079] 2. Second Embodiment Next, the second embodiment will be described. In the following description, emphasis will be placed on the description of matters different from the first embodiment, and the description of matters common to the first embodiment may be omitted. Also, in the following description, mainly the cooling means Q2 corresponding to the cylinder tank 1A will be described, but the cooling means Q2 corresponding to the cylinder tank 1B is also provided in the same manner.

[0080] In the gas compression device 10 of the second embodiment, a heat transfer tube 72a (a form of an indirect heat exchanger) is provided instead of the heat exchanger 71 of the first embodiment. FIG. 11 is a schematic configuration diagram of the heat transfer tube 72a and its periphery. As shown in this figure, the gas compression device 10 includes a water circulation circuit 72, a cooling tower 73, and a circulation pump 74, and a part of the water circulation circuit 72 is configured as the heat transfer tube 72a. The cooling means Q2 of the second embodiment is configured to include the water circulation circuit 72 including the heat transfer tube 72a, the cooling tower 73, the circulation pump 74, and the cooling water Wa.

[0081] FIG. 12 schematically shows the arrangement form of the heat transfer tube 72a in the cylinder tank 1A. The heat transfer tube 72a extends spirally in the cylinder tank 1A and is arranged in a region (liquid filling region) filled with the liquid L in the cylinder tank 1A.

[0082] The central axis of the spiral structure of the heat transfer tube 72a coincides with the central axis of the cylinder tank 1A extending vertically. The heat transfer tube 72a can be regarded as an indirect heat exchanger for cooling the liquid L filled in the cylinder tank 1A and serves as the cooling means Q2. That is, in the second embodiment, the liquid L that has absorbed the compression heat in the cylinder tank 1A comes into contact with the heat transfer tube 72a which is the cooling means Q2. As a result, the liquid L is cooled by indirect heat exchange with the cooling water Wa flowing in the heat transfer tube 72a.

[0083] To effectively perform this indirect heat exchange, it is desirable that the heat transfer tube 72a be arranged to cover as wide an area as possible of the liquid filling region in the cylinder tank 1A. For example, in the vertical direction, it is desirable that the heat transfer tube 72a be arranged to cover the entire range from the top dead center to the bottom dead center of the liquid piston in the cylinder tank 1A.

[0084] In the second embodiment, by configuring the heat transfer tube 72a in a spiral shape, the contact area between the liquid L in the cylinder tank 1A and the heat transfer tube 72a is increased so that the indirect heat exchange is efficiently performed. However, the specific form of the heat transfer tube 72a is not particularly limited. For example, the heat transfer tube 72a is not limited to the form of a single heat transfer tube, and may also be in the form of a plurality of heat transfer tubes (as an example, a form in which a plurality of heat transfer tubes extending vertically are arranged side by side front and back or left and right).

[0085] Also in the second embodiment, mainly in the control states A2 to A4 (see FIGS. 5 to 7) and the control states B2 to B4 described above, during the process of sending the liquid L before absorbing the compression heat from one of the cylinder tanks 1A and 1B to the other, the heat absorption means Q1 operates, and the compression heat is absorbed by the liquid L through direct heat exchange with the liquid dispersion flow. Further, during all or part of the period when the heat absorption means Q1 is operating in this way, the cooling means Q2 on the side where the liquid L before cooling is fed operates, and the liquid L is cooled by indirect heat exchange with the cooling water Wa. Thus, also in the second embodiment, by operating the cooling means Q2 during the operation period of the heat absorption means Q1, the compression heat can be efficiently removed, and an ideal isothermal compression process is realized.

[0086] Also, in the cooling means Q2 of the second embodiment, both a heat transfer tube 72a corresponding to the cylinder tank 1A (conveniently referred to as "heat transfer tube 72aA") and a heat transfer tube 72a corresponding to the cylinder tank 1B (conveniently referred to as "heat transfer tube 72aB") may be included in the same water circulation circuit 72. FIG. 13 is a schematic configuration diagram of the water circulation circuit 72 and its surroundings in this case.

[0087] As shown in FIG. 13, the heat transfer tube 72aA and the heat transfer tube 72aB are arranged in parallel between the position P1 of the water circulation circuit 72 and the position P2 on the subsequent stage side. By arranging them in parallel in this way, the problem that the cooling water Wa (the cooling water Wa whose temperature has risen) used for heat exchange in one of the heat transfer tubes 72aA and 72aB enters the other before passing through the cooling tower 73 is avoided. According to the cooling means Q2 shown in FIG. 13, it is possible to realize indirect heat exchange between the cooling water Wa and the liquid L in both cylinder tanks 1A and 1B by using the same water circulation circuit 72, cooling tower 73, circulation pump 74, and cooling water Wa. Note that the heat transfer tube 72aA is provided in the cylinder tank 1A, and the heat transfer tube 72aB is provided in the cylinder tank 1B.

[0088] In addition, when arranging the heat transfer tubes 72aA and 72aB in parallel as described above, as shown in FIG. 14, it is more preferable to provide opening and closing valves 75A and 75B in the flow paths of the cooling water Wa to the heat transfer tubes 72aA and 72aB. The opening and closing valve 75A is arranged between the position P1 and the heat transfer tube 72aA, and the opening and closing valve 75B is arranged between the position P1 and the heat transfer tube 72aB. The opening and closing of each of the opening and closing valves 75A and 75B can be controlled by the control means 7.

[0089] During the period when the control means 7 operates the cooling means Q2 corresponding to the cylinder tank 1A, the on-off valve 75A is set to the open state and the on-off valve 75B is set to the closed state, so that the cooling water Wa flows only through the heat transfer tube 72aA among the heat transfer tubes 72aA and 72aB. On the other hand, during the period when the control means 7 operates the cooling means Q2 corresponding to the cylinder tank 1B, the on-off valve 75A is set to the closed state and the on-off valve 75B is set to the open state, so that the cooling water Wa flows only through the heat transfer tube 72aB among the heat transfer tubes 72aA and 72aB. Thereby, while appropriately operating the cooling means Q2, the flow rate of the circulation pump 74 can be reduced compared to the case where the on-off valves 75A and 75B are not provided, and the specific energy of the gas compression device 10 can be further improved.

[0090] 3. Others (1) Regarding the working medium As the above-described liquid L, that is, the working medium for the liquid piston in the gas compression device 10, for example, clean water (preferably, pure water (RO water, ion-exchanged water) or softened water) is suitable. Since the specific heat capacity of water is very large compared to other substances, it is particularly suitable as the working medium for the isothermal compression process involving the absorption of compression heat. In addition, since clean water is harmless to the human body, it is also suitable as the working medium for the gas compression device for food factories.

[0091] In this embodiment, the air filter 23 is equipped at the air inlet of the device. However, contaminants and bacteria floating in the air may pass through, and depending on the installation environment of the device, water quality contamination and the growth of miscellaneous bacteria due to repeated intake of air are a concern. Therefore, it is desirable to perform regular blowdown using the liquid discharge valve 82 and replenish clean water using the liquid supply valve 84.

[0092] In addition, as the working medium, for example, brine (aqueous calcium chloride solution, aqueous sodium chloride solution, etc.), glycerin aqueous solution, ethylene glycol aqueous solution, liquid paraffin, vegetable oil, and synthetic oil can also be preferably used as antifreeze for cold regions. As the working medium for the gas compression device 10 for food factories, any of brine, glycerin aqueous solution, liquid paraffin, and vegetable oil is preferable.

[0093] In cold regions, there is a concern of water freezing during the stoppage of the gas compression device 10 in winter. Therefore, from the perspective of minimizing this problem, it is desirable to take the following measures. First, regarding the type of liquid L, even when using clean water in summer and intermediate seasons, it is desirable to replace it with an antifreeze such as the above-mentioned brine in winter. When using such an antifreeze, the installation of the heater and heat insulation material described below is basically unnecessary.

[0094] Second, as a second measure, it is desirable to enclose the entire device with a casing and attach a planar heater to the inner surface of the casing panel. In this case, for example, when the internal temperature of the casing drops below the set temperature, the heater may be energized for heating.

[0095] Furthermore, as a third measure, it is desirable to cover the line through which the liquid L flows in the gas compression device 10 and the liquid pump 6 with a heat insulation material, and attach a planar heater to the outer surfaces of the cylinder tanks 1A and 1B. In this case, for example, when the ambient temperature around the cylinder tanks 1A and 1B drops below the set temperature, the heater may be energized for heating.

[0096] (2) Regarding the number of cylinder tanks In the above-described embodiment, the number of cylinder tanks in the gas compression device was two, but the number of cylinder tanks may be three, and three processes including the standby process may be rotated. The significance of this configuration includes continuing the production of compressed air with the remaining two cylinder tanks while putting one of them in a standby state during regular replacement of the working medium and maintenance. In this case, the operation modes of the gas compression device having three cylinder tanks (conveniently referred to as the first to third tanks) are sequentially switched among three patterns of the first to third operation modes.

[0097] In the first operation mode, the first tank undergoes an expansion / intake process (compression / exhaust process), the second tank undergoes a compression / exhaust process (expansion / intake process), and the third tank undergoes a standby process. In the second operation mode, the first tank undergoes a standby process, the second tank undergoes an expansion / intake process (compression / exhaust process), and the third tank undergoes a compression / exhaust process (expansion / intake process). In the third operation mode, the first tank undergoes a compression / exhaust process (expansion / intake process), the second tank undergoes a standby process, and the third tank undergoes an expansion / intake process (compression / exhaust process).

[0098] It is also possible to have four or more cylinder tanks. However, for example, when the number of cylinder tanks is four, it is usually more desirable to install two gas compression devices each equipped with two cylinder tanks to double the production amount of compressed air per unit time rather than installing four cylinder tanks in one gas compression device.

[0099] 4. Effects, etc. As described above, the gas compression device 10 of each embodiment is a device that compresses the gas taken into the cylinder tanks 1A and 1B by a liquid piston, and includes a liquid injection means for injecting a liquid L into the cylinder tanks 1A and 1B, a heat absorption means Q1 (a means for absorbing the compression heat by directly exchanging heat between the compressed gas generated in the cylinder tanks 1A and 1B and the liquid dispersion flow composed of droplets and / or a liquid film while changing the liquid L injected into the cylinder tanks 1A and 1B into the liquid dispersion flow), a cooling means Q2 (a means for cooling the liquid L by indirectly exchanging heat between the liquid L that has absorbed the compression heat and the cooling water Wa supplied from outside the system), and a control means 7 for controlling the operations of the heat absorption means Q1 and the cooling means Q2. And the control means 7 discharges the compression heat to the outside of the system via the cooling water Wa by operating the cooling means Q2 during the operation period of the heat absorption means Q1.

[0100] Therefore, according to the gas compression device 10 of each embodiment, an isothermal compression process for a compressible gas can be realized, and it is possible to increase the specific energy during the production of compressed gas. Further, by operating the cooling means Q2 during the operation period of the heat absorption means Q1, the operating efficiency of these means Q1 and Q2 is improved, and the above isothermal compression process can be realized in a closer form, making it possible to further increase the specific energy during the production of compressed gas.

[0101] As described above, the embodiments of the present invention have been explained. However, the configuration of the present invention is not limited to the above embodiments, and various modifications can be made without departing from the gist of the invention. That is, the above embodiments should be considered as illustrative in all respects and not restrictive. The technical scope of the present invention is shown not by the description of the above embodiments but by the scope of the claims, and it should be understood that all modifications belonging to the meaning and scope equivalent to the scope of the claims are included.

Industrial Applicability

[0102] The present invention can be used in a gas compression device for compressing gas.

[0103] <Contribution to the Sustainable Development Goals (SDGs) led by the United Nations> The air compressor according to the present disclosure improves the specific energy by realizing an isothermal compression process, and can contribute to the achievement of Goal 7, "Ensure access to affordable, reliable, sustainable and modern energy for all" of the SDGs (Sustainable Development Goals).

Explanation of Reference Numerals

[0104] 1A, 1B Cylinder tank 2 Intake mechanism 3 Exhaust mechanism 6 Liquid pump 7 Control means 10 Gas compression device 11A, 11B First liquid port 12A, 12B Second liquid port 13A, 13B Spray nozzle 14A, 14B Air Bleed Valves 21A, 21B Intake Lines 22A, 22B Intake Valves 23 Air Filter 31A, 31B Exhaust Lines 32A, 32B Exhaust Valves 41A, 41B First Liquid Flow Lines 42A, 42B First Liquid Flow Control Valves 51A, 51B Second Liquid Flow Lines 52A, 52B Second Liquid Flow Control Valves 53A, 53B Liquid Introduction Lines 54A, 54B Liquid Introduction Control Valves 61 Liquid Suction Line 62 Liquid Discharge Line 71 Heat Exchanger 72 Water Circulation Circuit 72a Heat Transfer Pipe 73 Cooling Tower 74 Circulation Pump 75A, 75B On - Off Valves 81 Liquid Drain Line 82 Liquid Drain Valve 83 Liquid Supply Line 84 Liquid Supply Valve 91 Air Separator 92 Drain Trap 93A, 93B Return Liquid Check Valves 611 Liquid Delivery Check Valve Fx Flow Sensor Lx Liquid Level Detection Electrode Rod Px Pressure Sensor L Liquid Z Process Switching Element Group

Claims

1. A gas compression device that compresses the gas taken into a cylinder tank by a liquid piston, liquid injection means for injecting liquid into the cylinder tank, while changing the liquid injected into the cylinder tank into a liquid dispersion flow composed of liquid droplets and / or a liquid film, by direct heat exchange between the compressed gas generated in the cylinder tank and the liquid dispersion flow, heat absorption means for causing the liquid to absorb the compression heat, cooling means for cooling the liquid by indirect heat exchange between the liquid that has absorbed the compression heat and a cooling medium supplied from outside the system, control means for controlling the operations of the heat absorption means and the cooling means, and the control means operates the cooling means during the operation period of the heat absorption means to discharge the compression heat to the outside of the system through the cooling medium. A gas compression device.

2. The liquid injection means includes a liquid pump, The gas compression device according to claim 1, wherein the cooling means includes an indirect heat exchanger that cools the liquid discharged from the liquid pump.

3. The gas compression device according to claim 2, wherein the indirect heat exchanger is a plate heat exchanger disposed in a pipe through which liquid flows.

4. The gas compression device according to claim 1, wherein the cooling means includes an indirect heat exchanger that cools the liquid filled in the cylinder tank.

5. The gas compression device according to claim 4, wherein the indirect heat exchanger includes one or a plurality of heat transfer pipes disposed in a liquid filling region in the cylinder tank.

6. a water circulation circuit for circulating cooling water as a cooling medium for the indirect heat exchanger, The gas compression device according to any one of claims 2 to 5, further comprising a cooling tower that cools the cooling water circulating through the water circulation circuit by heat exchange with cooling air.

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