KR20150123731A

KR20150123731A - Air cycle system

Info

Publication number: KR20150123731A
Application number: KR1020150056487A
Authority: KR
Inventors: 정현욱
Original assignee: 정현욱
Priority date: 2014-04-25
Filing date: 2015-04-22
Publication date: 2015-11-04
Also published as: KR101684587B1

Abstract

The air cycle system includes a primary heat exchanger for exchanging a part or all of the high-pressure air supplied from the outside with the atmospheric air; A first inlet for introducing high-pressure air passing through the primary heat exchanger, and a second inlet for introducing high-pressure air bypassed without passing through the primary heat exchanger; A secondary heat exchanger for exchanging a part or all of the high-pressure air passed through the primary temperature control valve with the low-pressure air passing through the cooling turbine; A secondary temperature control valve including an inlet communicating with the outlet of the primary temperature control valve, a first outlet communicating with the inlet of the cooling turbine, and a second outlet communicating with the high pressure side flow passage inlet of the secondary heat exchanger .

Description

[0001] AIR CYCLE SYSTEM [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air-cycle system, and more particularly, to an air-cycle system capable of quickly providing air-conditioned air of a temperature, pressure, and humidity range required from a compressed air supplied from the outside.

The Air Conditioning Unit (ACU), which supplies the air conditioning air required for aircraft ground inspection, is applying an air cycle system based on a system principle called Reverse Brayton Cycle. This air cycle system mainly receives compressed air from a separate independent gas turbine and exchanges heat with the atmosphere to lower the temperature of the compressed air and obtain cooling effect by expansion while passing through the cooling turbine.

Air conditioning air for aircraft should basically be supplied after removing the condensed water and ice generated in the cooling process of the atmospheric air reliably and the temperature should be adjusted quickly within a wide range from low temperature to high temperature, Which distinguishes it from a regular air conditioner.

In the case of conventional ACU, compressed air is supplied from a separate gas turbine but power is not supplied. Therefore, ACU is controlled by mechanical pneumatic control. In order to solve the problems caused by the manual control and the pneumatic control, a method of attaching the generator to the coaxial shaft using the shaft power generated by the cooling turbine, and utilizing the power for controlling the cooling system or the cooling turbine load adjustment is also used . In addition, the air cycle system configuration, the water removal system, and the temperature control system are presented in various forms.

The present invention is based on electronic control using an electric actuator, an electronic sensor and a controller, which are operated by electric power generated by a shaft power generated by a cooling turbine. In order to maximize the dehumidification effect, To be precisely maintained at a temperature just before condensation of low-pressure air is frozen.

The present invention also provides a method for controlling a temperature of a low-pressure air having passed through a cooling turbine and a low-pressure water separator by using a secondary heat exchanger without rapidly increasing moisture in the air and unnecessarily consuming the amount of compressed air supplied from the outside And to provide an air cycle system capable of controlling the flow rate without changing the flow rate.

The air cycle system according to an embodiment of the present invention includes: a) a cooling turbine for expanding and cooling high pressure air, ii) a primary heat exchanger for heat-exchanging part or all of high pressure air supplied from the outside with atmospheric air, Iii) a first inlet through which high-pressure air having passed through the primary heat exchanger flows and a second inlet through which high-pressure air bypassed without passing through the primary heat exchanger flows in, and a cross-sectional area of the flow path between the first inlet and the second inlet A second heat exchanger for exchanging a part or the whole of the high pressure air passed through the first temperature control valve with the low pressure air passing through the cooling turbine, and v) a first temperature control valve A first outlet communicating with the inlet of the cooling turbine, and a second outlet communicating with the high-pressure-side flow passage inlet of the second heat exchanger, wherein the first outlet communicates with the oil outlet of the second outlet, And a second temperature control valve is inversely related to each other with the cross-sectional area.

The air cycle system may further include a high pressure water separator installed between the primary heat exchanger and the first inlet of the primary temperature control valve to remove condensed water in the high pressure air passing through the primary heat exchanger.

The air cycle system may further include a low pressure water separator installed between the outlet of the cooling turbine and the low pressure side flow passage inlet of the secondary heat exchanger to remove condensed water from the low pressure air passing through the cooling turbine.

The high pressure air passing through the secondary heat exchanger can be supplied to the cooling turbine by joining with the high pressure air passing through the first outlet of the secondary temperature control valve and the low pressure air passing through the low pressure side channel of the secondary heat exchanger can be supplied to the low pressure air And can be supplied to the discharge box through the piping.

The secondary temperature control valve may further include a third outlet communicating with the low-pressure air pipe. The first outlet is fully closed and the second outlet is partially or completely opened, the third outlet is gradually opened to increase the temperature of the low-pressure air to be finally discharged.

On the other hand, the outlet of the primary temperature control valve may be the first outlet, and the primary temperature control valve may further comprise a second outlet communicating with the low pressure air line. In the course of the first inlet being closed and the second inlet being opened, the closing of the first outlet is started, and the opening of the second outlet is started and the temperature of the low-pressure air finally discharged can be increased.

On the other hand, the air cycle system may further include a connection pipe for directly supplying the high-pressure air supplied from the outside to the low-pressure air pipe, and a heating control valve provided on the connection pipe. By operating the heating control valve, the temperature of the low-pressure air that is finally discharged can be increased.

The air cycle system may further include a flow control valve installed in the low pressure air line. The flow rate control valve may include a main flow path for supplying low pressure air to the discharge box and a bypass flow path for bypassing surplus flow rate to an atmospheric air inflow path of the primary heat exchanger.

The air cycle system is equipped with a temperature sensor to prevent freezing and a temperature control range to prevent freezing of low-pressure air installed between the cooling turbine and low-pressure water separator, and to control the temperature of the low-pressure air discharged from the cooling turbine to the primary temperature And a controller for controlling the regulating valve.

When the temperature measured by the anti-freezing temperature sensor is lower than the freezing prevention temperature built in the controller, the first temperature control valve can operate to reduce the flow passage cross-sectional area of the first inlet and increase the flow passage cross-sectional area of the second inlet. Conversely, when the temperature measured by the anti-freezing temperature sensor is higher than the freezing prevention temperature built in the controller, the first temperature control valve can operate to increase the flow passage cross-sectional area of the first inlet and reduce the flow passage cross-sectional area of the second inlet .

The air cycle system includes a nozzle for injecting high pressure air to the inlet of the cooling turbine, a generator coaxially coupled to the cooling turbine for generating electricity, a fan coaxially coupled to the cooling turbine and sucking atmospheric air into the primary heat exchanger . The nozzles may be constructed of variable vane nozzles and the flow control range may be limited to have the minimum number of revolutions required of the generator.

The air cycle system according to the present invention can maintain the humidity of the finally discharged air to a minimum, satisfy the wide temperature range required in the inspection process of the aircraft, and quickly change the temperature of the finally discharged air.

1 is a configuration diagram of an air cycle system according to a first embodiment of the present invention.
2 is a configuration diagram of an air cycle system according to a second embodiment of the present invention.
3 is a configuration diagram of an air cycle system according to a third embodiment of the present invention.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings, which will be readily apparent to those skilled in the art to which the present invention pertains. The present invention may be embodied in many different forms and is not limited to the embodiments described herein.

When an element is referred to as " including " an element throughout the specification, it means that the element may further include other elements unless specifically stated otherwise. The sizes and thicknesses of the respective components shown in the drawings are arbitrarily shown for convenience of explanation, and the present invention is not limited to the illustrated ones.

The general air cycle system will be described as follows.

The compressed air introduced from the outside takes heat by heat exchange with the atmospheric air and then flows into the cooling turbine. The compressed air flowing into the cooling turbine is cooled while being rapidly expanded by rotating the turbine and discharged to the end use place. Meanwhile, the fan attached to the coaxial shaft of the turbine rotating by the compressed air rotates by the rotational force obtained from the turbine, and sucks the atmospheric air so that the compressed air can heat-exchange with the atmospheric air. The air that has passed through the heat exchanger by the fan is again vented to the atmosphere. At this time, the compressed air that has undergone heat exchange with the atmospheric air may vary depending on the pressure, the heat exchange capacity, the temperature and the humidity of the atmospheric air, but most of the compressed air contains the condensed water and the cooled air passing through the cooling turbine Thereby further generating condensed water.

In the case of the prior art air cycle system, various methods for lowering the moisture of the finally discharged air are used. First, by connecting an additional compressor to the cooling turbine coaxial shaft, the pressure of the high-pressure air supplied from the outside is further raised to increase the dew point and then heat exchange with the cooling air discharged from the atmospheric air or the cooling turbine, Pressure water separator at the downstream stage, and secondly, the temperature of the air discharged from the cooling turbine is kept as low as possible within a range that does not cause freezing, and is removed from the low-pressure water separator. Particularly, the latter method is mainly used for a simple system. When the temperature is kept too high, condensation water is less generated. If the temperature is kept too low, freezing occurs.

In particular, a heat exchanger for exchanging heat between atmospheric air and high-pressure air controls the amount of high-pressure air passing therethrough to control the temperature of high-pressure air entering the cooling turbine, The method of controlling the temperature discharged from the turbine is mainly used. On the other hand, it is necessary to raise the low-pressure air before the final discharge after passing through the low-pressure water separator while keeping the low temperature to the required temperature. In this case, the temperature control is mainly performed by the high- And the like.

However, in this case, there is a problem that the humidity of the mixed air rises. For example, if the atmospheric air temperature is 30 ° C and the relative humidity is 90%, the absolute water content at atmospheric pressure is about 25g per kg of dry air. Compressing atmospheric air of this condition in an external independent compressor maintains relative humidity but absolute humidity. Assuming that the conditions of the low pressure air passing through the cooling turbine and the water separator are, for example, 0.3 barG, 0 캜, and a relative humidity of 100%, the absolute moisture content is about 3 g per kg of dry air. In order to raise the temperature of the low-pressure air, when the high-pressure air having the absolute moisture of about 25 g per 1 kg of the compressed dry air is mixed in the compressor, the relative humidity of the mixed air is greatly increased . In this case, there is a problem in meeting the low relative humidity standards supplied to the aircraft.

1 is a configuration diagram of an air cycle system according to a first embodiment of the present invention. The air cycle system according to the first embodiment will be described with reference to FIG.

The high-temperature, high-pressure compressed air supplied from the outside is first introduced into the primary heat exchanger 10 for heat exchange with the atmospheric air for cooling. The high-pressure air supplied from the outside is a high-pressure and high-pressure condition at a pressure of 2.5 to 3.5 barG and a temperature of 180 to 200 ° C, depending on the compression ratio and efficiency when the atmospheric condition is the standard atmospheric condition, Of compressed air. The high-pressure air cooled by the atmospheric air in the primary heat exchanger (10) flows into the primary temperature control valve (30) composed of a three-way valve.

The primary temperature control valve 30 is composed of a housing in which a plurality of air flow paths are formed and a valve body and a single actuator that are configured to open or close a plurality of air flow paths in accordance with rotation or linear motion by the actuator . The first inlet 31 of the primary temperature control valve 30 communicates with the primary heat exchanger 10 and the second inlet 32 communicates with the high pressure air pipe before the primary heat exchanger 10 , And the outlet (33) communicates with the inlet (41) of the secondary temperature control valve (40).

The primary temperature control valve 30 is configured to similarly form the cross-sectional area of the flow path of the first inlet 31 and the cross-sectional area of the flow path of the second inlet 32 and to adjust the cross-sectional area of the flow path in inverse proportion to each other by the operation of the valve actuator do. For example, when the cross-sectional area of the flow path of the first inlet 31 decreases, the cross-sectional area of the flow path of the second inlet 32 increases, and when the flow path of the first inlet 31 is completely closed, It is preferable that the inverse relationship be configured to be inversely proportional.

Since the three-way valve applicable to the primary temperature control valve 30 of this embodiment is variously used, any type of three-way valve that satisfies the above-described purpose is applicable. At this time, a high-pressure water separator (not shown) is provided between the primary heat exchanger 10 and the first inlet 31 of the primary temperature control valve 30 to pass through the primary heat exchanger 10 and remove condensed water from the high- (20) can be installed.

The high-pressure air having passed through the primary temperature control valve 30 flows into the inlet 41 of the secondary temperature control valve 40 constituted by four-way valves. The second temperature control valve 40 is provided with a housing having a plurality of air flow paths formed therein and a plurality of air flow paths for opening and closing the plurality of air flow paths as the first and second temperature control valves 30, And a valve body and an actuator.

The first outlet 42 of the second temperature control valve 40 communicates with the inlet of the cooling turbine 51 and the second outlet 43 communicates with the inlet of the high pressure side channel of the second heat exchanger 70, The third outlet (44) communicates with the low-pressure air pipe (L10) which has passed through the low-pressure side oil path of the low-pressure water separator (60) and the secondary heat exchanger (70).

The first outlet (42) and the second outlet (43) have a similar flow cross-sectional area and are configured to be able to adjust the cross-sectional area of the flow passage in inverse proportion to each other. That is, when the flow path cross-sectional area of the first outlet 42 decreases, the flow path cross-sectional area of the second inlet 43 increases, and when the flow path of the first outlet 42 is completely closed, And the opposite case is preferably configured to be in an inverse proportion relationship.

The third outlet (44) is configured such that the second outlet (43) is fully opened and the first outlet (42) is gradually opened in a fully closed state. It is preferable that the second outlet 43 is completely opened and the first outlet 42 is completely closed even when the third outlet 44 is fully opened. Particularly, when the third outlet 44 is fully opened, the second outlet 43 may be partially closed. However, in cooperation with the flow rate of the air discharged to the third outlet 44, A flow path for passing a flow rate at which a minimum number of revolutions can be generated should be secured in the second outlet 43.

The high pressure air passing through the second outlet 43 of the secondary temperature control valve 40 passes through the cooling turbine 51 in the secondary heat exchanger 70 and is cooled and then removed in the low pressure water separator 60 Heat exchange with the low pressure air. Since the temperature of the high-pressure air is always higher than the temperature of the low-pressure air passed through the low-pressure water separator 60, the high-pressure air passes through the second outlet 43 of the secondary temperature control valve 40, Pressure air flowing through the low-pressure side flow path of the secondary heat exchanger 70 increases as the flow rate of the high-pressure air passing through the side flow path increases.

Further, since the high-pressure air passing through the secondary heat exchanger 70 is cooled by the low-pressure air, the high-temperature high-pressure air supplied from the outside is mixed with the low-pressure air as it is to raise the temperature of the low- More work can be recovered. Particularly, since the temperature is indirectly increased, the absolute humidity is maintained, and the temperature is raised, thereby reducing the relative humidity.

The high pressure air passing through the second heat exchanger 70 through the second outlet 43 of the second temperature regulating valve 40 flows into the high pressure air passing through the first outlet 42 of the second temperature regulating valve 40 And supplied to the cooling turbine 51. The air that has passed through the nozzle 54 of the cooling turbine 51 and converted the pressure energy into velocity energy collides with the cooling turbine 51 so that the cooling turbine 51 rotates and the air pressure And the temperature is lowered. The low-pressure air passing through the cooling turbine 51 includes condensed water generated when the temperature is lowered. The low-pressure air passes through the low-pressure side oil passage of the secondary heat exchanger 70 while passing through the low-pressure water separator 60.

On the other hand, the high-pressure air passing through the third outlet 44 of the second temperature regulating valve 40 is mixed with the low-pressure air passing through the low-pressure side channel of the secondary heat exchanger 70. The primary temperature regulating valve 30 Is passed through the second heat exchanger (70) communicated with the second outlet (43) of the second temperature control valve (40), it is used when the temperature does not rise by the target temperature set by the user. For example, although depending on the aircraft, some aircraft may also need to supply hot air of approximately 90 ° C to 100 ° C.

Thus, the second outlet 43 of the second temperature regulating valve 40 is completely opened and the third outlet 44 is gradually opened with the first outlet 42 completely closed, so that the temperature of the low- Can be further increased. Or the second outlet 43 of the second temperature regulating valve 40 is not fully opened or the first outlet 42 is not fully closed but the third outlet 44 may be opened, The flow path cross-sectional area of the first, second, and third outlets 42, 43, and 44 and the interlocking relationship of opening and closing can be adjusted depending on the operating temperature, the capacity of the cooling turbine 51,

However, it is preferable that the first outlet 42 and the second outlet 43 are basically inversely proportional to each other and the third outlet 44 is opened after at least half of the second outlet 43 is opened . &Lt; / RTI > Since the four-way valve applicable to the second temperature control valve 40 of this embodiment is variously used, any type of three-way valve that satisfies the above-described purpose is applicable.

The low-pressure air having passed through the secondary heat exchanger 70 flows into the flow rate control valve 80 after passing through the mixing section with the high-temperature, high-pressure air communicated with the third outlet 44 of the secondary temperature control valve 40. The flow rate control valve 80 is divided into a main flow path 81 connected to the discharge box 100 having a discharge port for finally supplying low pressure air to the outside, and a bypass flow path 82 for bypassing a surplus flow rate. Accordingly, it is preferable that the main flow passage 81 and the bypass flow passage 82 are inversely proportional to each other in accordance with the adjustment of the actuator.

At this time, the surplus air discharged to the bypass flow path 82 flows into the atmospheric air inflow path of the primary heat exchanger 10, so that it cools the high pressure air together with the atmospheric air. The low pressure air that has passed through the main flow path 81 flows into the discharge box 100 through the flow meter 90 and then is supplied to the outside through a hose or the like connected to the final discharge port. At this time, the flowmeter 90 can be applied to various flowmeters such as orifice and venturi.

The cooling turbine assembly 50 includes a nozzle 54 spaced apart from the outer diameter of the cooling turbine 51 by a certain distance. The nozzle 54 may be any one of a fixed vane nozzle having a fixed flow passage cross-sectional area and angle and a variable variable vane nozzle. In particular, in the case of the variable vane nozzle, the amount of high-pressure air supplied from the outside can be controlled. When the cross-sectional area of the flow path of the nozzle 54 is reduced, the amount of air supplied to the cooling turbine 51 decreases, And the opposite is also possible.

However, since the cooling turbine assembly 50 of the present embodiment includes the generator 53 for control, if the cross-sectional area of the flow path of the nozzle 54 is excessively reduced, the rotation speed of the cooling turbine 51 is reduced, Generates a drop in the voltage generated by the generator (53). Therefore, it is preferable that the nozzle 54 applied to the cooling turbine assembly 50 limits the adjustment range so as to have the minimum number of revolutions required of the generator 53.

Alternatively, the nozzle 54 may be completely closed so that no high-pressure air is supplied from the outside. In this case, the power generated by the generator 53 is supplied to the generator 53 to supply power to the actuator for adjusting the variable- It is necessary to store them in a capacitor (capacitor) or a battery so that they can be used for a certain period of time even while the rotation is decreasing. If the battery is used for a long time, it may be preferable to apply the capacitor because the storage capacity may be reduced and eventually become unusable.

The fan (52) attached to the coaxial shaft of the cooling turbine (51) rotates by the rotational force obtained from the cooling turbine (51) and sucks atmospheric air so that the compressed air can exchange heat with the atmospheric air. The air having passed through the primary heat exchanger (10) by the fan (52) is again discharged to the atmosphere.

The power generated in the above-described generator 53 is supplied to the controller 120 and utilized for control and power storage. Although it is desirable that the controller 120 and the various sensors and actuators used in this embodiment are electronic and electric for rapid control, some pneumatic and mechanical sensors and actuators may be applied.

A control method of the air cycle system of the first embodiment will be described based on the above-described configuration.

First, the discharge flow rate of the air-conditioning air supplied to the user is controlled by the flow control valve 80 because the flow rate can not be controlled by the nozzle when the flow channel is fixed. When the flow rate measured by the flow meter 90 is larger than the user-set flow rate, the outlet of the main flow path 81 of the flow control valve 80 is closed and the bypass flow path 82 is opened, The flow rate to the main flow path 81 can be reduced.

Conversely, when the flow rate measured by the flow meter 90 is smaller than the set flow rate, the flow rate of the gas flowing into the main flow path 81 can be increased by opening the outlet of the main flow path 81 of the flow rate control valve 80 and closing the bypass flow path 82 have. However, this type of flow control wastes energy by consuming more of the high pressure air supplied from the outside than the final exhaust air. Therefore, it is more efficient to control the flow rate by controlling the variable vane nozzle 54 alone or the variable vane nozzle 54 and the flow rate control valve 80 rather than the flow rate control valve 80.

When the variable vane nozzle 54 is mounted, the air conditioning air discharge flow rate supplied to the outside can be adjusted by adjusting the air flow rate of the variable vane nozzle 54 in accordance with the flow rate set by the user, Increase or decrease the flow cross-sectional area to increase or decrease the flow rate. When the flow rate set by the user is reached, the actuator for actuating the variable vane nozzle 54 stops operating. At this time, when the cross sectional area of the flow path of the variable vane nozzle 54 is reduced, the air supplied to the cooling turbine 51 is completely cut off, and the cooling turbine 51 loses its rotational force and stops.

If the number of revolutions of the cooling turbine 51 is reduced and the generator 53, which is coaxially connected to the cooling turbine 51, becomes difficult to produce sufficient electric power while reducing the flow cross sectional area of the variable vane nozzle 54, control may become impossible . Therefore, a capacitor or a battery can be provided so that the power can be controlled by the charged power without the power generated by the generator 53. However, since the flow rate may be reduced immediately after the start of the air cycle system, the charging power of the capacitor or the battery may be insufficient.

Therefore, it is more desirable to set the minimum number of revolutions required for power generation of the generator 53 or the minimum power required for the control so that the flow passage cross-sectional area of the variable vane nozzle 54 is not further reduced if the number of revolutions falls or the power drops. Control is required. Further, when the variable vane nozzle 54 is adjusted to the minimum limit as described above and the additional flow rate reduction is required, the flow rate can be adjusted by adjusting the flow rate control valve 80.

Another method of controlling the flow rate is to provide a supply flow rate control valve 110 before the high pressure air supplied from the outside is branched into the primary heat exchanger 10 and the bypass line to regulate the amount of air supplied from the outside, The air flow rate of the air discharged to the outside can be adjusted. However, in this case, if the amount of air is reduced below a certain level, the efficiency of the cooling turbine nozzle 54 is drastically lowered, thereby reducing the rotation of the fan 52, so that sufficient atmospheric air necessary for the primary heat exchanger 10 is not introduced The number of revolutions of the required generator 53 may not be adjusted. Therefore, in the case of adjusting the flow rate by providing the supply flow rate control valve 110, it is preferable to set the minimum flow rate limit so as to limit the supply flow rate control valve 110 so that the supply air amount does not fall below a certain level.

On the other hand, the control of the air-conditioning air temperature and the humidity to be supplied to the outside are as follows. As described above, in the present embodiment, the temperature of the air discharged from the cooling turbine 51 is kept as low as possible within a range that the condensed water does not freeze, thereby generating a large amount of condensed water. In the case of the above-mentioned method. If the pressure of the high-pressure air is sufficient in most of the atmospheric conditions and the expansion ratio in the cooling turbine 51 is sufficient and the amount of moisture in the air is not large and the condensation heat generated during the condensation process of the steam is not large, The air falls into freezing and freezing occurs.

In this embodiment, the temperature of the high-pressure air supplied to the cooling turbine 51 is adjusted to freeze the low-pressure air discharged from the cooling turbine 51, . For this purpose, the first temperature control valve 30 is used to regulate the temperature by regulating the amount of high-pressure air passing through the primary heat exchanger 10 and the amount of high-pressure air bypassing and merging.

However, the air that has passed through the primary temperature control valve 30 is finally supplied to the cooling turbine 51 according to the amount of the air passing through the secondary heat exchanger 70 from the secondary temperature control valve 40, It is necessary to provide a temperature sensor 121 for preventing freezing between the cooling turbine 51 and the low-pressure water separator 60 and to provide a temperature control range for preventing freezing in the controller 120, The primary temperature control valve 30 is adjusted so that the low-pressure air temperature discharged from the cooling turbine 51 is constantly within the temperature control range regardless of whether or not the temperature control valve 40 is operated.

Therefore, if the temperature measured by the anti-freezing temperature sensor 121 is lower than the anti-freezing temperature of the controller 120, for example, 0 ° C, the primary temperature control valve 30 can be operated through the primary heat exchanger 10 The flow path cross-sectional area of the first inlet 31 into which the air flows is reduced, the flow path cross-sectional area of the second inlet 32 bypassing the primary heat exchanger 10 is increased to raise the temperature, If the temperature is higher than the anti-freezing temperature stored in the controller 120, the temperature is lowered.

Further, if the actuator rotates or advances in one direction due to the above-described configuration, the temperature rises. If the actuator rotates or reverses in the opposite direction, the temperature can be lowered, and simple control is possible. For this control to vary quickly and continuously, it is desirable to provide electrically controlled electric actuators and electronic temperature sensors rather than pneumatic actuators or mechanical sensors.

The second temperature control valve (40) is mainly used for controlling the exhaust temperature of the air-conditioning air supplied to the outside. Since the low-pressure air having passed through the low-pressure water separator 60 passes through the secondary heat exchanger 70 in the downstream stage, in order to raise the temperature of the low-pressure air, the high- .

As described above, the second outlet 43 of the second temperature regulating valve 40 is in communication with the high-pressure side flow path of the secondary heat exchanger 70, but passes through the low-pressure side flow path of the secondary heat exchanger 70 To effectively control the amount of high-pressure air sent to the secondary heat exchanger 40 in order to increase the temperature of the low-pressure air, the first outlet 42 of the secondary temperature control valve 40, that is, With the amount of high-pressure air to be introduced. That is, as the second outlet 43 is opened for rapid temperature control, the first outlet 42 is closed or the first outlet 42 is opened as much as the second outlet 43 is closed .

When the discharge temperature measured by the discharge temperature sensor 122 installed in the discharge box 100 is lower than the discharge temperature set by the user, the first and second temperature control valves 40, The first outlet 42 is closed at the same rate while opening the outlet 43. [ As the amount of high-pressure air supplied to the secondary heat exchanger (70) through the second outlet (43) increases, the temperature of the low-pressure air passing through the heat exchange with the high-pressure air rises.

Even though both the second outlet 43 and all of the first outlet 42 are closed to allow the entire high pressure air to pass through the secondary heat exchanger 70, the measured discharge temperature is lower than the user- , The temperature is raised while opening the third outlet (44). When the third outlet (44) is opened, since the high-temperature high-pressure air is directly mixed with the low-pressure air, the temperature rise can be performed quickly.

At this time, the second outlet 43 may be partially closed while the first outlet 42 is fully closed. However, the second outlet 43 may be partially closed to secure the flow path enough to supply the minimum amount of air for driving the generator 53, Thereby constituting the regulating valve 40. Further, due to the above-described configuration, as in the case of the primary temperature control valve 30, when the actuator rotates or advances in one direction, the temperature rises, and when the actuator rotates or reverses in the opposite direction, the temperature can be lowered so that simple control is possible .

Also, when the temperature of the atmospheric air is considerably low, the temperature of the exhaust air may not rise to the user-set temperature even if all of the third outlet 44 is opened when the airplane needs to be heated. In this case, the temperature of the low-pressure air discharged from the cooling turbine 51 can be further increased by using the primary temperature control valve 30, which has been kept low within a range where no freezing occurs.

That is, by controlling the amount of high-pressure air passing through the primary heat exchanger 10 by using the primary temperature control valve 30, the flow rate of heat exchange with the atmospheric air can be further reduced, or the high- Pressure air of the second temperature regulating valve 40 can be supplied to the second temperature regulating valve 40 as well as the temperature of the low-pressure air discharged from the cooling turbine 51, The temperature of the high-pressure air supplied through the outlet 44 rises together, so that the temperature of the air-conditioning air finally discharged can be easily raised.

Of course, it is also possible to open the second outlet 43 or the third outlet 44 of the second temperature control valve 40 while simultaneously raising the temperature of the finally discharged air-conditioning air using the primary temperature control valve 30 have. However, when the temperature is raised before passing through the low-pressure water separator 60, it is more preferable to adjust it by the above-described procedure because it does not sufficiently generate condensed water.

The actuators used in the primary temperature control valve 30 and the secondary temperature control valve 40 applied to the present embodiment are connected to an electropneumatic regulator using electric power generated by the generator 53 of the cooling turbine assembly 50 A pneumatic actuator operated by an electric motor or an electric actuator operated by an electric motor can be applied. Pure pneumatic actuators can be applied, of course, but are not desirable for fast and accurate control.

In addition, the above-mentioned actuators need no position control. That is, the controller compares the value measured by the temperature sensor with the value set by the user, and when the measured value is higher than the set value, it rotates or rotates in one direction until it becomes the same or vice versa. do. However, the actuator can incorporate a limit switch with an upper limit value and a lower limit value.

However, since the control range changes according to changes in the atmospheric conditions, the compression ratio of the external compressor, and the temperature change, the position control may be performed by previously incorporating the actual or predicted database into the controller 120 , And can be used to implement faster control through a separate function.

The condensed water discharged from the high-pressure water separator 20 and the low-pressure water separator 60 is directly injected into the atmospheric air inflow passage of the primary heat exchanger 10 to help heat exchange, Is supplied to a cooler (56) provided therein and used for cooling the lubricating oil, the housing and the like, and then is injected into the atmospheric air inflow passage of the primary heat exchanger (10) and used effectively for cooling the high pressure air together with the atmospheric air .

2 is a configuration diagram of an air cycle system according to a second embodiment of the present invention. Referring to FIG. 2, the air cycle system of the second embodiment will be described as follows.

The other configuration is the same as in the first embodiment, except that a four-way valve is applied to the first temperature control valve 30a and a three-way valve is applied to the second temperature control valve 40a. The first inlet 35 of the primary temperature control valve 30a communicates with the primary heat exchanger 10 and the second inlet 36 communicates with the high pressure air pipe before the primary heat exchanger 10 . The first outlet 37 is communicated with the inlet 45 of the second temperature regulating valve 40a and the second outlet 38 is communicated with the low pressure side oil separator 60 of the low pressure water separator 60 and the second heat exchanger 70, Pressure air pipe L10 that has passed through the low-pressure air pipe L10.

As in the first embodiment, the primary temperature control valve 30a is configured to similarly form the flow path cross-sectional area of the first inlet 35 and the flow path cross-sectional area of the second inlet 36, So that the cross-sectional area of the flow path can be adjusted. For example, when the cross-sectional area of the flow path of the first inlet 35 decreases, the cross-sectional area of the flow path of the second inlet 36 increases, and when the flow path of the first inlet 35 is completely closed, It is preferable that the inverse relationship be configured to be inversely proportional.

On the other hand, in the process that the first inlet 35 is closed and the second inlet 36 is opened, the opening of the second outlet 38 can be started and the closing of the first outlet 37 can be started. However, it is preferable that the first inlet 35 is completely closed and the second inlet 36 is completely opened when the second outlet 38 is all opened. However, as described above, the first outlet 37 must be partially opened even when the second outlet 38 is fully opened in order to secure a minimum number of revolutions for driving the generator 53.

The air having passed through the first outlet 37 of the first temperature control valve 30a flows into the inlet 45 of the second temperature control valve 40a. The second outlet port 47 communicates with the inlet of the cooling turbine 51 and the second outlet port 47 communicates with the inlet of the cooling turbine 51. The second outlet port 47 communicates with the inlet of the cooling turbine 51, And communicates with the inlet of the flow passage. The first outlet (46) and the second outlet (47) are configured to be able to adjust the cross-sectional area of the flow passage in inverse proportion to each other. That is, when the cross-sectional area of the flow path of the first outlet 46 decreases, the cross-sectional area of the flow path of the second outlet 47 increases, and when the flow path of the first outlet 46 is completely closed, And the opposite case is preferably configured to be in an inverse proportion relationship. The air that has passed through the second outlet port 47 passes through the first outlet port 46 and rejoins the air bypassing the second heat exchanger 70 to be introduced into the inlet of the cooling turbine 51 .

The temperature control method of the air cycle system of the second embodiment will be described as follows. The temperature control range for preventing freezing is provided between the cooling turbine 51 and the low-pressure water separator 60 in the same manner as in the first embodiment, and the temperature control range for preventing freezing is built in the controller 120, The first temperature regulating valve 30a is regulated so that the low-pressure air temperature discharged from the cooling turbine 51 is constantly within the temperature control range irrespective of whether or not the first temperature regulating valve 40a is operated. That is, the method of adjusting the temperature by adjusting the flow cross sectional area of the first inlet 35 and the second inlet 36 of the first temperature control valve 30a to be inversely proportional to each other is the same as that of the first embodiment.

When the first temperature control valve 30a rotates or advances in one direction within a certain period, the flow path of the first inlet 35 decreases and the flow path of the second inlet 36 increases. The flow of the first inlet 35 increases and the flow of the second inlet 36 decreases. In particular, it is preferable that the flow path of the first inlet 35 is completely opened and the flow path of the second inlet 36 is completely closed at the starting point of the actuator operation.

The operating range of the primary temperature control valve 30a for preventing freezing ends at a point where the flow path of the first inlet 35 is completely closed and the flow path of the second inlet 36 is completely opened. As in the first embodiment, the temperature of the air flowing into the secondary temperature regulating valve 40a varies according to the amount of air passing through the secondary heat exchanger 70, The first temperature control valve 30a is continuously adjusted so that the temperature measured by the freezing prevention temperature sensor 121 is within the freezing prevention temperature range irrespective of the operation of the first temperature control valve 40a.

In order to control the temperature of the final exhaust air, first, the secondary temperature control valve 40a is used and then the primary temperature control valve 30a is used. As described in the first embodiment, when the flow rate of the high-pressure air passing through the secondary heat exchanger 70 is increased by using the secondary temperature control valve 40a, the temperature of the low-pressure air passing through the secondary heat exchanger 70 becomes Rise. However, if all of the high-pressure air introduced into the secondary temperature control valve 40a is passed through the secondary heat exchanger 70 and the user-set exhaust air temperature can not be adjusted, the temperature is increased by using the primary temperature control valve 30a .

That is, if the flow rate of the high-pressure air bypassing the primary heat exchanger 10 is increased while ignoring the freezing prevention temperature, heat exchange with the atmospheric air can not be performed, and the temperature rises. If all the high-pressure air supplied from the outside bypasses the primary heat exchanger 10 and the user-set exhaust air temperature can not be set, the second outlet 38 of the first temperature control valve 30a is opened to open the high- Pressure air that has passed through the secondary heat exchanger (70), thereby rapidly raising the temperature.

3 is a configuration diagram of an air cycle system according to a third embodiment of the present invention. Referring to FIG. 3, the air cycle system of the third embodiment will be described as follows.

The other configuration is the same as that of the first embodiment, except that the second temperature control valve 40b is a three-way valve instead of the four-way valve and a separate heating control valve 130 is added. The heating control valve 130 is installed on a connection pipe L20 for directly supplying high-pressure air supplied from the outside to the low-pressure air pipe L10 connected to the discharge box 100. [

The primary temperature control valve 30b is arranged such that the first inlet 31 communicates with the primary heat exchanger 10 and the second inlet 32 communicates with the high pressure air line before the primary heat exchanger 10, Sectional area of the flow path between the inlet 31 and the second inlet 32 is adjusted to be inversely proportional to each other. The second temperature control valve 40b has a first outlet 46 communicating with the inlet of the cooling turbine 51 and a second outlet 47 communicating with the second heat exchanger 70, The flow path cross-sectional areas of the second outlet (47) are configured to be adjusted in inverse proportion to each other.

In order to control the temperature of the exhaust air, firstly, the amount of high-pressure air passing through the secondary heat exchanger 70 is controlled by the secondary temperature control valve 40b, Next, the amount of air passing through the primary heat exchanger 10 is adjusted by the primary temperature control valve 30b. When the temperature rise amount is insufficient, the heating control valve 130 may be operated to mix the high-pressure air supplied from the outside directly into the finally discharged air. The third embodiment differs from the first and second embodiments in that three valves 30b, 40b, and 130 must be applied.

While the present invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, Of course.

10: Primary heat exchanger 20: High-pressure water separator
30, 30a, 30b: primary temperature control valve
40, 40a, 40b: Secondary temperature control valve
50: Cooling turbine assembly 51: Cooling turbine
52: fan 53: generator
54: nozzle 56: cooler
60: Low pressure water separator 70: Secondary heat exchanger
80: Flow control valve 90: Flow meter
100: Discharge box 110: Supply flow control valve
120: Controller 121: Temperature sensor for preventing freezing
122: exhaust temperature sensor 130: heating regulating valve

Claims

A cooling turbine for expanding and cooling high pressure air;
A primary heat exchanger for exchanging a part or the whole of the high-pressure air supplied from the outside with the atmospheric air;
A first inlet through which the high-pressure air having passed through the primary heat exchanger flows and a second inlet through which high-pressure air bypassed without passing through the primary heat exchanger flows in, and a cross-sectional area of the flow path between the first inlet and the second inlet A primary temperature control valve having an inverse relationship with each other;
A second heat exchanger for exchanging a part or all of the high-pressure air passing through the primary temperature control valve with the low-pressure air passing through the cooling turbine; And
A first outlet communicating with an inlet of the cooling turbine, and a second outlet communicating with a high-pressure-side flow passage inlet of the secondary heat exchanger, the first outlet communicating with the outlet of the first temperature regulating valve, And the second outlet are inversely proportional to each other,
.

The method according to claim 1,
Further comprising a high pressure water separator provided between the primary heat exchanger and the first inlet of the primary temperature control valve for removing condensed water in the high pressure air passing through the primary heat exchanger.

The method according to claim 1,
Further comprising a low pressure water separator installed between the outlet of the cooling turbine and the low pressure side flow passage inlet of the secondary heat exchanger to remove condensed water in the low pressure air passing through the cooling turbine.

The method according to claim 1,
The high-pressure air passing through the secondary heat exchanger joins the high-pressure air passing through the first outlet of the secondary temperature control valve and supplied to the cooling turbine,
And the low-pressure air passing through the low-pressure side flow path of the secondary heat exchanger is supplied to the discharge box via the low-pressure air piping.

5. The method of claim 4,
The second temperature control valve further comprises a third outlet communicating with the low-pressure air pipe,
And the third outlet is gradually opened to increase the temperature of the low-pressure air that is finally discharged when the first outlet is fully closed and the second outlet is partially or fully opened.

5. The method of claim 4,
Wherein the outlet of the primary temperature control valve is a first outlet,
Wherein the primary temperature control valve further comprises a second outlet communicating with the low pressure air line.

The method according to claim 6,
Wherein the closing of the first outlet is started and the opening of the second outlet is started in the course of the first inlet being closed and the second inlet being opened, thereby increasing the temperature of the low-pressure air to be finally discharged.

5. The method of claim 4,
Pressure air supplied directly from the outside to the low-pressure air pipe, and a heating control valve provided in the connection pipe,
And the temperature of the low-pressure air which is finally discharged by the operation of the heating regulating valve is increased.

5. The method of claim 4,
Further comprising a flow control valve installed in the low-pressure air pipe,
Wherein the flow rate control valve includes a main flow path for supplying low pressure air to the discharge box and a bypass flow path for bypassing surplus flow rate to an atmospheric air inflow path of the primary heat exchanger.

The method of claim 3,
An anti-freezing temperature sensor provided between the cooling turbine and the low-pressure moisture separator; And
A controller for controlling the primary temperature control valve such that the temperature of the low-pressure air discharged from the cooling turbine is within a control range by incorporating a temperature control range for preventing freezing of low-
Further comprising an air cylinder.

11. The method of claim 10,
Wherein when the temperature measured by the anti-freezing temperature sensor is lower than the anti-freezing temperature stored in the controller, the first temperature control valve is operated to reduce the cross-sectional area of the flow path of the first inlet and increase the cross-sectional area of the flow path of the second inlet The air cycle system.

11. The method of claim 10,
Wherein when the temperature measured by the anti-freezing temperature sensor is higher than the freezing prevention temperature built in the controller, the first temperature control valve operates to increase the cross-sectional area of the flow path of the first inlet and to reduce the cross-sectional area of the flow path of the second inlet The air cycle system.

13. The method according to any one of claims 1 to 12,
A nozzle for injecting high-pressure air into an inlet of the cooling turbine;
A generator coaxially coupled to the cooling turbine and generating electricity; And
A fan coupled to the cooling turbine coaxially and sucking atmospheric air into the primary heat exchanger,
Further comprising an air cylinder.

14. The method of claim 13,
Wherein the nozzle is constituted by a variable vane nozzle and the flow control range is limited to have the minimum number of revolutions required for the generator.