KR20240033814A - Double spool valve system - Google Patents

Abstract

The present invention relates to a valve applied to a rotor blade cooling system and, more specifically, to a double spool valve system. according to the present invention, the double spool valve system comprises a spool valve sensing viscosity, temperature, internal pressure, and the like of oil to generate an electrical signal based on the sensed viscosity, temperature, internal pressure, and the like, and controlling all the total flow rate toward a heat exchanger by the generated electrical signal. therefore, the number of components is minimized, and an unnecessary flow rate toward the heat exchanger is selectively adjusted to improve fuel efficiency.

Description

Double spool valve system {Double spool valve system}

The present invention relates to a valve applied to a rotor blade cooling system, and more specifically to a double spool valve system.

A rotary-wing aircraft is an aircraft that is capable of vertical take-off and landing and back-and-forth/left-right flight, and uses the propulsion and control power generated by transmitting axial power from the engine to the rotor system through the power transmission system. At this time, the main gearbox of the power transmission system is a major driving part, and oil is needed inside the gearbox for lubrication or cooling required for gears and bearings. Lubricating and cooling oil comes into contact with the gearbox components in the form of direct cooling or indirect cooling. In more detail, in the case of the direct cooling method, an oil pump is used to spray the sucked oil into the necessary gears or bearings by creating a flow path, and in the case of the indirect cooling method, oil is sprayed in the form of mist on the gears and bearings by gear churning. It is a way of conveying it.

In other words, in order to improve the transmission efficiency and fuel efficiency of the gearbox, it is necessary to maintain the appropriate temperature of the lubricating oil and appropriately control the supply flow rate. Accordingly, in the prior art shown in FIG. 1, a heat exchanger bypass valve (hereinafter referred to as HBV) and a thermal valve (hereinafter referred to as a thermal valve) communicate with a heat exchanger and an oil filter. Control the oil flow rate, including TV).

More specifically, if foreign matter flows into the oil passage and the internal pressure increases, the HBV can be opened and a passage through which it can flow into the gearbox can be added. In addition, when the oil temperature is low during initial operation and the oil viscosity is high, fuel efficiency and transmission efficiency may increase due to an increase in drag torque inside the gearbox. Therefore, in order to maximize the initial oil temperature rise and lower the viscosity, the TV is opened and the HE is activated. Prevent heat exchange through

However, in this conventional technology, a large number of components such as HBV and TV must be included to control the flow of oil, thereby increasing the manufacturing cost. In addition, in the case of HBV and TV, there was a problem in that the issue was not resolved quickly as it was a technology that diverted only a portion of the total oil flow rate.

In addition, the conventional oil pump is engaged with the external gear inside the gearbox and has a discharge flow rate proportional to the RPM of the external gear. This means that as the RPM value increases, the actual required oil flow rate exceeds, and each gear and bearing of the gearbox There was a problem that more flow than necessary was supplied. Supplying more oil than necessary increased drag torque and served as a factor in reducing fuel efficiency.

Republic of Korea public utility model 20-1998-0041282 “Oil bypass structure” (1998.09.15.)

The present invention was created to solve the above problems, and the purpose of the present invention is to sense the viscosity, temperature, internal pressure, etc. of the oil, generate an electric signal based on this, and generate an electric signal to the heat exchanger using the generated electric signal. By including a spool valve that can control all flow rates, we provide a double spool valve system that can improve fuel efficiency by minimizing the number of parts and selectively controlling unnecessary flow rates toward the heat exchanger.

In order to solve the problems described above, the double spool valve system according to an embodiment of the present invention is applied to a rotary wing cooling system to control the flow path of lubricating or cooling oil, the viscosity of the oil, A sensor unit that measures at least one of temperature and hydraulic pressure, a first outlet in communication with the heat exchanger of the rotor blade cooling system, a second outlet in direct communication with the main gearbox of the rotor blade cooling system, and an oil pump in the rotor blade cooling system. A valve housing portion including a first inlet, a spool portion interpolated into the valve housing portion to open one of the first discharge port and the second discharge port and closing the other, connected to the spool portion, and receiving a control signal to spool. It is characterized by including a moving part that adjusts the position of the and a control part that receives oil information from the sensor part and generates a control signal to the moving part.

In addition, the valve housing portion includes a first discharge port, a second discharge port spaced apart from one side of the first discharge port at a predetermined distance, and a second discharge port formed on the opposite side of the first discharge port and spaced from a position that is opened and closed together with the first discharge port at a predetermined interval from the other side. A first valve housing including a second inlet formed at a position and a third inlet formed on an opposite side of the first discharge port and formed at a position opened and closed together with the second discharge port, the first inlet and the first inlet It is formed on the opposite side and includes a first intermediate discharge port connected to the second inlet, and a second valve housing formed on the opposite side of the first inlet and connected to the third inlet. Do it as

In addition, the spool portion is interpolated into the inside of the first valve housing to open either the first discharge port or the second discharge port and close the other, the first spool portion is interpolated inside the second valve housing to open either the first discharge port or the second discharge port and the first intermediate discharge port and the second valve housing. Characterized in that it includes a second spool that opens one of the second intermediate discharge ports and closes the other.

In addition, the first spool may have a plurality of protruding blocking parts on the side, each blocking part is spaced apart from each other by a predetermined opening distance, and the second inlet is a distance shorter than the opening distance to the other side from the position where it is opened and closed together with the first discharge port. It is characterized by being formed in a spaced apart position.

In addition, the moving part is a first solenoid valve that is connected to one end of the first spool and moves the first spool to the other side when receiving power from the control unit, and is connected to one end of the second spool to move the second spool to the other side when receiving power from the control unit. It is characterized in that it includes a second solenoid valve that moves to the other side and two or more springs respectively coupled between the other end of the first spool and the first valve housing and the other end of the second spool and the second valve housing.

In addition, when the pressure of the oil received from the sensor unit is greater than a predetermined standard value, the control unit cuts off the power of both the first solenoid valve and the second solenoid valve to open the second discharge port.

In addition, when the temperature of the oil received from the sensor unit is below a predetermined reference value, the control unit cuts off the power of both the first solenoid valve and the second solenoid valve to open the second discharge port.

In addition, when the pressure of the oil received from the sensor unit is less than the predetermined reference value and the temperature of the oil is above the predetermined reference value, the control unit supplies power to the first solenoid valve and cuts off power to the second solenoid valve. 1 Characterized by opening the discharge port.

In addition, the first valve housing is located at a predetermined distance from the first discharge port in the other direction of the first discharge port, and is located at a predetermined distance from the first discharge port in the other direction of the third discharge port and the first discharge port connected to the heat exchanger. It is characterized in that a fourth discharge port connected to the lower part of the main gear box is further formed.

In addition, the sensor unit further receives the RPM value of the external gear of the main gearbox, and the control unit stores the main driving conditions of the main gearbox and the required flow rate accordingly, and receives the RPM of the external gear to determine the discharge flow rate of the oil pump. is calculated, and when the difference between the discharge flow rate and the required flow rate is greater than a predetermined standard value, power is supplied to both the first solenoid valve and the second solenoid valve to open the third discharge port and the fourth discharge port.

The double spool valve system of the present invention with the above configuration senses the viscosity, temperature, and internal pressure of the oil, generates an electrical signal based on this, and can control the entire flow rate toward the heat exchanger by the generated electrical signal. By including a spool valve, the number of parts can be minimized and unnecessary flow to the heat exchanger can be selectively adjusted to improve fuel efficiency.

1 is a schematic diagram of the prior art of the present invention.
Figure 2 is a schematic diagram of a rotor cooling system to which the double spool valve system of the present invention is applied.
Figure 3 is a plan view showing a first driving example of the double spool valve system of the present invention.
Figure 4 is a schematic diagram showing the oil flow direction in the first operating example of the double spool valve system of the present invention.
Figure 5 is a plan view showing a second driving example of the double spool valve system of the present invention.
Figure 6 is a schematic diagram showing the oil flow direction in a second operation example of the double spool valve system of the present invention.
Figure 7 is a plan view showing a first driving example of the double spool valve system of the present invention.
Figure 8 is a graph showing the flow rate of the oil pump according to the RPM value of the external gear.
Figure 9 is a schematic diagram showing the oil flow direction in the first driving example of the double spool valve system of the present invention.

Hereinafter, the technical idea of the present invention will be described in more detail using the attached drawings. Prior to this, the terms or words used in this specification and claims should not be construed as limited to their usual or dictionary meanings, and the inventor should appropriately define the concept of terms in order to explain his or her invention in the best way. It must be interpreted as meaning and concept consistent with the technical idea of the present invention based on the principle of definability.

Hereinafter, the basic configuration of the double spool valve system 1000 of the present invention and the connection relationship between the double spool valve system 1000 and the rotor blade cooling system will be described with reference to FIG. 2.

The purpose of the present invention is to adjust the flow path of lubricating or cooling oil by applying it to the rotor blade cooling system, and the double spool valve system 1000 of the present invention is a sensor that measures at least one of oil viscosity, temperature, and hydraulic pressure. It may include a control unit 400 that receives oil information from the unit 500 and the sensor unit 500 and generates a control signal to the solenoid valve. The sensor unit 500 may be attached to the main gear box (M) or the oil pump (OP) to detect the state of the internal oil. The control unit 400 can remotely communicate with the sensor unit 500. By including the sensor unit 500 and the control unit 400, the complex state of the oil can be easily detected compared to existing bypass valves and thermal valves.

Additionally, the double spool valve system 1000 of the present invention may include a valve housing portion 100. The valve housing portion 100 has a first outlet 111 that communicates with the heat exchanger (H) of the rotor blade cooling system, a second outlet 112 that directly communicates with the main gear box (M) of the rotor blade cooling system, and a rotor blade cooling system. It may include a first inlet 123 that communicates with the oil pump (OP) of the system. In more detail, the first inlet 123 is connected to the oil supply passage 2300 in communication with the oil pump (OP) and the oil filter (OF) to allow the oil inside the oil pump (OP) to be supplied to the inside of the valve housing. The first outlet 111 can cool the oil by being connected to the cooling passage 2100 communicating with the valve housing heat exchanger (H), and the second outlet 112 communicates with the heat exchanger (H). The temperature of the oil inside the valve housing can be maintained at a high temperature by being connected to the non-cooled flow path 2200, which bypasses the valve and directly communicates with the main gear box (M).

In addition, the double spool valve system 1000 of the present invention is inserted into the valve housing portion 100 to open one of the first discharge port 111 and the second discharge port 112 and close the other spool portion ( 200). In more detail, the spool unit 200 may include a first spool 210 and a second spool 220, and each of the first spool 210 and the second spool 220 extends in a predetermined direction, and The blocking portion 230 may have a protruding shape in the lateral direction. A plurality of blocking portions 230 may be formed, and each blocking portion 230 may be formed to be spaced apart by a certain opening distance. The diameter of the portion where the blocking portion 230 is formed may be the same as the inner diameter of the valve housing or may be as small as a slight gap. Accordingly, when the blocking portion 230 of the spool portion 200 comes into contact with the first discharge port 111 or the second discharge port 112, the first discharge port 111 and the second discharge port 112 may be closed. That is, the spool unit 200 can adjust the opening and closing of the first discharge port 111 or the second discharge port 112 as the position changes.

Additionally, the double spool valve system 1000 of the present invention may include a moving part 300. The moving unit 300 is connected to one end of the spool, and can open and close the first discharge port 111 or the second discharge port 112 by receiving a control signal and adjusting the position of the spool.

Hereinafter, the detailed configuration and first driving example of the double spool valve system 1000 of the present invention will be described with reference to FIGS. 3 and 4.

As shown in FIG. 3, the valve housing unit 100 may include a first valve housing 110 and a second valve housing 120. It is preferable that the internal spaces of the first valve housing 110 and the second valve housing 120 are separated from each other, and the internal spaces of the first valve housing 110 and the second valve housing 120 may be in communication with each other. there is. The first spool 210 may be interpolated into the interior of the first valve housing 110, and the second spool 220 may be interpolated into the interior of the second valve housing 120.

In more detail, the first valve housing 110 may have a first outlet 111 and a second outlet 112 formed on one side. The first outlet 111 and the second outlet 112 may be spaced apart by a certain opening distance, and the opening distance may be equal to the distance between the blocking portions 230 of the first spool 210. Accordingly, when the first discharge port 111 is closed by the blocking portion 230 of the first spool 210, the second discharge port 112 can be opened, and similarly, when the second discharge port 112 is closed When the first discharge port 111 is opened.

Additionally, the first valve housing 110 may have a second inlet 115 and a third inlet 116 formed on the other side. The second inlet 115 may be formed at a position spaced apart from the position corresponding to the first discharge port 111 by a predetermined distance shorter than the opening distance of the first spool 210. At this time, the direction of separation may be an outward direction rather than between the first discharge port 111 and the second discharge port 112. Accordingly, depending on the position of the first spool 210, it is closed and opened together with the first discharge port 111, or when the first discharge port 111 is closed, only the second inlet port 115 is opened and a third discharge port to be described later is opened. (113) and the fourth discharge port 114 can be opened.

In addition, the third inlet 116 is closed together when the blocking portion 230 of the first spool 210 is located at the position corresponding to the second discharge port 112, that is, the second discharge port 112. 2 When the portion where the blocking portion 230 of the first spool 210 is not formed is located in the discharge port 112, it may be formed in a position that is opened together.

Additionally, the second valve housing 120 may have a first intermediate outlet 121 and a second outlet 112 formed on one side, and a first inlet 123 may be formed on the other side. As described above, the first inlet 123 may be connected to the oil pump (OP) or oil filter (OF) of the main gear box (M) to receive oil. Additionally, the first intermediate outlet 121 may be connected to the second inlet 115 of the first valve housing 110, and the second intermediate outlet 122 may be connected to the third inlet 116 of the first valve housing 110. ) It is desirable to communicate with. That is, the double spool valve system 1000 of the present invention includes a second valve housing 120 separated from the first valve housing 110, thereby primarily classifying the oil flowing in through the first inlet 123. and the direction of oil flow can be controlled more accurately.

The moving unit 300 may include a first solenoid valve 310 and a second solenoid valve 320 connected to one end of the first spool 210 and the second spool 220, respectively. In more detail, the first solenoid valve 310 and the second solenoid valve 320 may move the first spool 210 and the second spool 220 to the other side when receiving power from the control unit 400. In addition, the moving part 300 may include a spring 330, where the spring 330 is connected to the other end of the first spool 210 and the second spool 220, the first valve housing 110, and the second spool 220, respectively. It can be coupled by being inserted between two valve housings 120. Accordingly, when power is supplied to the first solenoid valve 310 and the second solenoid valve 320 and driven, the first spool 210 and the second spool 220 can move in the other direction, and the first spool 210 and the second spool 220 can move in the other direction. When the solenoid valve 310 and the second solenoid valve 320 are not driven because the power is cut off, the first spool 210 and the second spool 220 may move in one direction due to the repulsive force of the spring 330. there is.

The double spool valve system 1000 having this structure can be driven in multiple driving examples depending on the condition of the internal oil. Among them, the first driving example is preferably performed when the oil pressure is above a predetermined reference value, the oil temperature is below a predetermined reference value, or the oil viscosity is above a predetermined reference value. In other words, when the internal oil does not flow smoothly, the oil is cooled as it passes through the heat exchanger (H) to prevent the viscosity from increasing.

Accordingly, the control unit 400 operates when the pressure of the oil received from the sensor unit 500 is greater than a predetermined standard value or when the temperature of the oil received from the sensor unit 500 is less than a predetermined standard value, as shown in FIG. , the power to both the first solenoid valve 310 and the second solenoid valve 320 can be cut off to open the second discharge port 112.

When the second discharge port 112 is opened in this way, as shown in FIG. 4, oil is supplied into the interior of the second valve housing 120 through the oil supply passage and is discharged through the second intermediate discharge port 122. It may be supplied into the inside of the first valve housing 110 through the third inlet 116. Thereafter, oil may be discharged through the second discharge port 112 that opens together with the third inlet port 116. The discharged oil may bypass the heat exchanger (H) along the uncooled flow path 2200 and flow into the main gear box (M) in an uncooled state.

Below, a second driving example of the present invention will be described with reference to FIGS. 5 and 6.

The second driving example is preferably performed when the oil pressure is below a predetermined reference value, the oil temperature is above a predetermined reference value, or the oil viscosity is below a predetermined reference value. That is, when the internal oil flows smoothly and in a normal state, the heat received as the oil cools through the heat exchanger (H) and cools the main gear box (M) is re-supplied to the main gear box (M). It can be allowed to re-cool previously.

Accordingly, the control unit 400 operates when the pressure of the oil received from the sensor unit 500 is less than a predetermined reference value or when the temperature of the oil received from the sensor unit 500 is greater than a predetermined reference value, as shown in FIG. , power may be supplied to the first solenoid valve 310 and power may be cut off to the second solenoid valve 320 to open the first discharge port 111.

When the first discharge port 111 is opened in this way, as shown in FIG. 6, oil is supplied into the interior of the second valve housing 120 through the oil supply passage and is discharged through the first intermediate discharge port 121. It may be supplied into the first valve housing 110 through the second inlet 115. Thereafter, oil may be discharged through the first discharge port 111 that opens together with the second inlet port 115. The discharged oil may flow into the main gear box (M) in a re-cooled state through the heat exchanger (H) along the cooling passage 2100.

Below, a third driving example of the present invention will be described with reference to FIGS. 7 to 9.

As shown in FIG. 7, the first valve housing 110 may have a third outlet 113 and a fourth outlet 114 formed on one side, and the third outlet 113 and the fourth outlet 114 The gap between them may be narrower than the gap between the blocking parts 230 of the first spool 210. Accordingly, the third outlet 113 and the fourth outlet 114 can be opened and closed at the same time. It is preferable that the third discharge opening 113 and the fourth discharge opening 114 are formed not between the first discharge opening 111 and the second discharge opening 112, but outside it, that is, on the other side of the first discharge opening 111. . Accordingly, the third outlet 113 and the fourth outlet 114 can receive oil when the first middle outlet 121 of the second valve housing 120 is opened.

In addition, the third outlet 113 is in communication with the heat exchanger (H), and is preferably in communication with the first flow passage provided separately from the cooling passage 2100, and the fourth discharge opening 114 is in communication with the main gear box (M ) It is preferable that it communicates with the second flow rate control passage 2500, which communicates with the lower end of the. By adopting this structure, the oil flow method in the third driving example in which the third discharge port 113 and the fourth discharge port 114 are opened and the first driving example in which the second discharge port 112 is open can be completely separated. In the third driving example, the ratio of the oil heading to the heat exchanger (H) and the oil heading to the bottom of the main gear box (M) is the ratio of the first flow rate control flow path 2400 and the second flow rate control flow path 2500. It can only be determined by the diameter ratio.

This is to prevent the drag torque from increasing due to the cooling oil interfering with the driving of the gear. More specifically, as shown in FIG. 8, the oil pump (OP) is connected to the external gear inside the main gear box (M). It is driven in engagement with and has a discharge flow rate proportional to the RPM value of the external gear. However, in reality, the gears of the main gear box (M) are designed so that the required flow rate for cooling does not increase proportionally even if the RPM increases, so the discharge flow rate increases in proportion to the gear RPM value and the actual need to cool the gears. A gap (unnecessary flow rate) occurred between the flow rates, and it became worse as the RPM value of the gear increased. To overcome this, the double spool valve system 1000 of the present invention allows the sensor unit 500 to further receive the RPM value of the external gear of the main gear box (M), and the control unit 400 allows the main gear box (M )'s main driving conditions and corresponding required flow rate can be stored, and the discharge flow rate of the oil pump (OP) can be calculated by receiving the RPM of the external gear.

Thereafter, the control unit 400 may perform the third driving example when the difference between the discharge flow rate and the required flow rate is greater than or equal to a predetermined reference value. In the third driving example, when the drag torque of the gear in the main gear box (M) increases due to a large difference between the discharge flow rate and the required flow rate, a portion of the flow rate flowing into the valve housing portion 100 is transferred to the bottom of the main gear box (M). This can be adjusted by discharging (the oil does not come into contact with the gear). That is, the control unit 400 may supply power to both the first solenoid valve 310 and the second solenoid valve 320 to open the third outlet 113 and the fourth outlet 114.

Accordingly, as shown in FIG. 9, oil is supplied into the interior of the second valve housing 120 through the oil supply passage, and is discharged to the first intermediate discharge port 121 and the second inlet port 115. 1 Can be supplied into the interior of the valve housing 110. Afterwards, the second inlet 115 is opened, and oil can be discharged through the third outlet 113 and the fourth outlet 114. The discharged oil may be transferred to the heat exchanger (H) along the first flow rate control flow path 2400, and may flow into the bottom of the main gear box (M) along the second flow rate control flow path 2500.

The technical idea of the present invention should not be interpreted as limited to the above-described embodiments. Not only is the scope of application diverse, but various modifications can be made at the level of those skilled in the art without departing from the gist of the present invention as claimed in the claims. Therefore, such improvements and changes fall within the scope of protection of the present invention as long as they are obvious to those skilled in the art.

1000: Double spool valve system
100: Valve housing part
110: first valve housing
111: first discharge port
112: second outlet
113: third outlet
114: fourth outlet
115: second inlet
116: third inlet
120: second valve housing
121: first intermediate outlet
122: second middle discharge port
123: first inlet
200: Spool part
210: 1st spool
220: 2nd spool
230: blocking unit
300: moving part
310: first solenoid valve
320: second solenoid valve
330: spring
400: control unit
500: sensor unit
2100: Cooling passage
2200: Uncooled flow path
2300: Oil supply channel
2400: 1st flow control flow path
2500: 2nd flow control flow path
F: fan
M: Main gearbox
OP: Oil pump
OF: Oil filter
H: heat exchanger

Claims (10)

In the double spool valve system applied to the rotor cooling system and controlling the flow path of lubricating or cooling oil,
A sensor unit that measures at least one of viscosity, temperature, and hydraulic pressure of the oil;
A valve housing portion including a first discharge port communicating with a heat exchanger of the rotor blade cooling system, a second discharge port directly communicating with the main gearbox of the rotor blade cooling system, and a first inlet communicating with an oil pump of the rotor blade cooling system;
a spool portion that is inserted into the valve housing portion to open one of the first discharge port and the second discharge port and close the other one;
A moving part connected to the spool part and receiving a control signal to adjust the position of the spool;
A control unit that receives information about the oil from the sensor unit and generates a control signal to the moving unit. A double spool valve system comprising a.
According to clause 1,
The valve housing portion,
The first outlet and the second outlet spaced apart from each other at a predetermined distance on one side of the first outlet,
a second inlet formed on the opposite side of the first outlet, and at a position spaced a predetermined distance from the position opened and closed together with the first outlet, and
A first valve housing formed on an opposite side of the first discharge port and including a third inlet port formed at a position that opens and closes together with the second discharge port,
The first inlet and a first intermediate discharge port formed on a side opposite to the first inlet and connected to the second inlet,
A double spool valve system comprising a second valve housing formed on a side opposite to the first inlet and having a second intermediate discharge port connected to the third inlet.
According to clause 2,
The spool part,
a first spool that is interpolated inside the first valve housing to open either the first discharge port or the second discharge port and close the other;
A double spool valve system comprising a second spool inserted into the second valve housing to open one of the first intermediate outlet and the second intermediate outlet and close the other.
According to clause 3,
The first spool may have a plurality of blocking parts protruding from the side, and each blocking part is spaced apart from each other by a predetermined opening distance,
A double spool valve system, characterized in that the second inlet is spaced apart from a position where it is opened and closed together with the first discharge port at a position spaced apart from the other side by a distance shorter than the opening distance.
According to clause 4,
The moving part,
A first solenoid valve connected to one end of the first spool and moving the first spool to the other side when power is received from the control unit,
A second solenoid valve connected to one end of the second spool and moving the second spool to the other side when power is received from the control unit, and
A double spool valve system comprising two or more springs respectively coupled between the other end of the first spool and the first valve housing and the other end of the second spool and the second valve housing.
According to clause 5,
The control unit,
When the pressure of the oil received from the sensor unit is greater than a predetermined standard value,
A double spool valve system, characterized in that the power to both the first solenoid valve and the second solenoid valve is cut off to open the second discharge port.
According to clause 5,
The control unit,
When the temperature of the oil received from the sensor unit is below a predetermined standard value,
A double spool valve system, characterized in that the power to both the first solenoid valve and the second solenoid valve is cut off to open the second discharge port. According to clause 5,
The control unit,
When the pressure of the oil received from the sensor unit is less than a predetermined standard value and the temperature of the oil is more than a predetermined standard value,
A double spool valve system, characterized in that power is supplied to the first solenoid valve and power is cut off to the second solenoid valve to open the first discharge port.
According to clause 5,
The first valve housing,
a third outlet located on the other side of the first outlet at a predetermined distance from the first outlet and connected to the heat exchanger;
A double spool valve system, characterized in that a fourth discharge port is further formed on the other side of the first discharge port at a predetermined distance from the first discharge port and connected to the lower end of the main gear box.
According to clause 9,
The sensor unit,
Further receiving the RPM value of the external gear of the main gearbox,
The control unit,
Stores the main driving conditions of the main gearbox and the required flow rate accordingly,
Receives the RPM of the external gear and calculates the discharge flow rate of the oil pump,
When the difference between the discharge flow rate and the required flow rate is greater than a predetermined standard value,
A double spool valve system, characterized in that power is supplied to both the first solenoid valve and the second solenoid valve to open the third discharge port and the fourth discharge port.

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