KR101792795B1 - Gas turbine engine with oil pump assembly - Google Patents

Abstract

Gas turbine engines include turbine rotor assemblies, generators, and oil pump assemblies. The turbine rotor assembly includes a turbine wheel rotating at high speed by combustion gas and a compressor impeller coupled to the turbine wheel by a rotation support shaft. The generator includes a generator rotor coupled to the front of the compressor impeller by a shaft coupling. The oil pump assembly includes a primary pinion gear fixed to an outer peripheral surface of a shaft coupling, a plurality of primary bogies engaged with a primary pinion gear, a plurality of primary bogies and a plurality of secondary pinion gears sharing an axis, A plurality of secondary bogies engaged with the secondary pinion gears, a plurality of secondary bogies, a plurality of drive gears sharing an axis, and a plurality of driven gears meshing with the plurality of drive gears do.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a gas turbine engine including an oil pump assembly,

The present invention relates to a gas turbine engine, and more particularly to a gas turbine engine including an oil pump assembly that obtains power from a turbine rotor assembly.

A micro gas turbine engine generally consists of a single stage centrifugal compressor impeller that compresses air, a combustion chamber that injects fuel into the compressed air and combusts the fuel, a single-core centrifugal turbine wheel that generates combustion power through the combustion gas, . Some of the rotational power generated by the turbine wheel is used as a power source for direct or indirectly coupled generators, etc., and the rest is used to compress air in the compressor described above.

In most cases, load devices such as generators (collectively generators) are indirectly connected via shaft couplings and gearboxes, and the turbine wheel and compressor impellers are assembled on one shaft to provide rotational power from the turbine wheel to the compressor impeller. Directly. At this time, the shaft coupling mainly applied to the micro gas turbine engine is a type having a spline for power transmission at both ends of a shaft having a small diameter.

In addition, an assembly that is made up of a turbine wheel, a compressor impeller, a rotation support shaft, and the like and is rotating integrally is referred to as a turbine rotor assembly. Various types of bearings are used to support a turbine rotor assembly that rotates at high speeds, typically ball bearings or sleeve bearings.

In order to lubricate these bearings, lubricating oil must be supplied and the oiling and sealing structure should be provided so that the oil vapor generated from the oil and oil splashes out of the oil lubrication space. The oil cooler for cooling the heated oil due to the heat transmitted through the turbine wheel and the compressor impeller and the bearing frictional heat, the oil tank for storing the oil, the oil filter for filtering the impurities of the oil, And a sensor capable of measuring the temperature of the liquid.

Most of the high speed rotating bearing lubricating pumps employ external gear pumps. The external gear pump is a simple structure pump in which the oil is sucked and discharged by the rotation of the two drive gears and the driven gear. Oil-lubricated micro gas turbine engines typically have a feed pump for oil feed and an oil feed pump for oil feed.

On the other hand, the bearings for supporting the turbine rotor assembly can be variously constructed, but the positioning of the bearing housing on the front of the air intake of the compressor impeller is a serious problem. Except that the bearing supporting the turbine rotor assembly is located between the turbine wheel and the compressor impeller and the rear surface of the turbine wheel and the rear surface of the compressor impeller are opposed to each other. Generally, the bearing housing is located on the front surface of the air intake portion of the compressor impeller .

In the above-described arrangement, it is advantageous in various aspects such as cooling the generator to be positioned in front of the air intake portion of the compressor impeller, which is a relatively low temperature region in the turbine exhaust side direction (behind the compressor impeller) This is because it is advantageous to position the bearing housing on the front face of the air inlet of the compressor impeller in order to stably support the turbine rotor assembly when a shaft coupling or the like is installed for power transmission to the generator.

However, the air suction portion of the compressor impeller maintains a weak vacuum pressure lower than the atmospheric pressure due to the suction force of the compressor. Therefore, when the bearing housing is located on the front surface of the air intake part, there is a high possibility that the oil and the oil vapor scattered from the bearing housing pass through the air seal and the oil seal and enter the air intake part by the vacuum pressure.

When oil or vapor is introduced into the compressor, problems such as incomplete combustion, deterioration of efficiency and soot may occur. Conventionally, various seals are installed between the air inlet portion of the compressor inlet pellet and the bearing housing , There is a problem that leakage of oil and vapor can not be completely prevented when the pressure inside the bearing housing rises or the oil drainage is not smooth.

In the installation of the oil pump, in the conventional case, it is installed in the gear box for decelerating the rotational power mainly transmitted from the turbine rotor assembly for driving the generator. However, when the generator connected to the gas turbine engine is operated at the same rotation speed as the turbine rotor assembly of the gas turbine engine without the reduction gear, the oil pump must be driven by an electric motor or a separate speed reducer for driving the oil pump .

When an oil pump is driven by an electric motor, the bearing lubrication that supports the turbine rotor assembly immediately becomes a problem in the event of a problem of control and power supplied to the motor and the motor, which can seriously damage the gas turbine engine. Accordingly, it is desirable to provide a separate speed reducer so that the oil pump can be driven by the power of the turbine rotor assembly until the turbine rotor assembly is finished rotating.

However, in order to install a separate speed reducer for only the oil pump, the position becomes a problem. First, the method of directly engaging the reduction gear by forming a gear directly on the turbine rotor assembly or the generator rotor may adversely affect the rotation stability of the turbine rotor assembly and the generator rotor rotating at a high speed, for example, 30,000 RPM or more.

Next, when the oil pump is installed by using a separate shaft coupling at the end of the generator rotor remote from the turbine rotor assembly, the cooling channel for cooling the generator is difficult to construct and the oil supply and drainage lines And the shaft coupling needs to be additionally installed.

Finally, when the oil pump is positioned between the turbine rotor assembly and the generator, there is a shaft coupling between the turbine rotor assembly and the generator to transfer the rotational power of the turbine rotor assembly to the generator. The problem remains.

On the other hand, when the gas turbine engine is driven, the pressure of the turbine side bearing housing is increased due to the high-pressure combustion gas leaking to the back side of the turbine wheel and the high-pressure compressed air leaking to the back side of the compressor impeller. Of course, the flow of gas and air from the outside of the bearing housing to the interior reduces the likelihood that the oil or vapor will leak in the opposite direction.

However, when the turbine side bearing housing and the compressor side bearing housing located on the front side of the compressor impeller are connected to each other through the oil drain pump, when the combustion gas and the compressed air pressure are greatly increased according to operating conditions, The increase in the amount of combustion gas and compressed air leaking into the turbine side bearing housing exceeds the suction capacity of the oil drain pump, resulting in an increase in the pressure of the bearing housing located at the front of the compressor impeller. In this case, there arises a problem that the oil and the vapor are leaked to the air suction portion of the compressor impeller as described above.

The present invention relates to a gas turbine engine having a turbine rotor assembly and a generator connected to the turbine rotor assembly by a shaft coupling and rotating at the same speed without a speed reducer so that the rotation stability of the turbine rotor assembly and the generator rotor, And at the same time to minimize the vibration generated in the shaft coupling.

Another object of the present invention is to provide a gas turbine engine capable of preventing leakage of oil and vapor within the bearing housing due to a pressure difference between the bearing housings.

A gas turbine engine according to an embodiment of the present invention includes a turbine rotor assembly, a generator, and an oil pump assembly. The turbine rotor assembly includes a turbine wheel rotating at high speed by combustion gas and a compressor impeller coupled to the turbine wheel by a rotation support shaft. The generator includes a generator rotor coupled to the front of the compressor impeller by a shaft coupling. The oil pump assembly includes a primary pinion gear fixed to an outer peripheral surface of a shaft coupling, a plurality of primary bogies engaged with a primary pinion gear, a plurality of primary bogies and a plurality of secondary pinion gears sharing an axis, A plurality of secondary bogies engaged with the secondary pinion gears, a plurality of secondary bogies, a plurality of drive gears sharing an axis, and a plurality of driven gears meshing with the plurality of drive gears do.

The shaft coupling can be coupled to the shaft coupling connection of the compressor impeller and generator rotor by forming a first spline at both ends and engaging the primary pinion gear shaft by forming a second spline in the center. The primary pinion gear shaft can be supported by the primary pinion gear shaft bearings at the front and rear.

A plurality of primary bull gears may be equally distributed on a circumference located at a first distance about a shaft coupling and a plurality of secondary bull gears may be arranged on a circumference located at a second distance about the shaft coupling Can be arranged to be equally divided. The second distance may be greater than the first distance.

The plurality of pump gear sets may include a feed pump gear set, a generator and a compressor side feed pump gear set, and a turbine side feed oil feed pump gear set. Each of the feed pump gear set, the generator and compressor side feed pump gear set, and the turbine side feed oil feed oil pump gear set may each be located in a pump gear set internal portion formed in the pump gear housing.

The pump gear housing may include three oil passages located on the inside of the pump gear set internal portion and axially closed on the opposite side and opened on the opposite side, and may be assembled inside the oil filter housing. An oil distributor assembly with a filter therein can be attached to the side of the oil filter housing.

The three oil passages include a supply oil discharge passage communicating with the first discharge port of the supply pump gear set, an oil discharge oil discharge passage communicating with the second discharge port of the generator and compressor-side oil discharge pump gear set and the turbine- , And a supply oil distribution passage supplied with the oil filtered through the filter.

The supply pump gear set can suck the oil through the tank oil inlet formed on the outer circumferential surface of the pump gear housing and the oil pump housing and can discharge the oil through the first outlet to the supply oil discharge channel after pressurization. The feed oil drain can be connected to the inlet of the filter through the feed oil inlet of the oil distributor assembly.

When the pressure relief valve is installed in the oil passage supplied to the filter from the oil distributor assembly, the oil can be supplied to the oil suction passage through the oil bypass passage so that the supply pump can be re-suctioned.

The turbine-side oil-drain oil-drain pump gear set can suck the oil discharged from the turbine-side bearing housing through the turbine-side oil-discharge oil inlet formed on the outer circumferential surface of the pump gear housing and discharge oil through the second oil- can do.

The generator and the compressor side oil pump gear set can suck the oil into the generator and the compressor side oil drain oil flow path through the oil drainage inlet on the side of the generator and the oil drain on the side of the compressor, Can be discharged.

The oil discharged from the turbine side oil feed oil pump gear set and the generator and the compressor side oil feed pump gear set is merged in the oil discharge oil discharge passage and discharged to the oil cooler through the oil discharge oil outlet formed on the outer periphery of the pump gear housing and the oil pump housing .

According to the embodiment of the present invention, the power can be transmitted to the generator rotating at the same speed as that of the gas turbine engine using one shaft coupling, and at the same time, the oil pump assembly can be driven as a speed reducer. In addition, during high-speed rotation, circumferential side pressure is not generated in the shaft coupling, vibration is minimized and it does not adversely affect the turbine rotor assembly or generator rotor, and oil or vapor can be prevented from leaking to the air intake portion of the compressor impeller have.

In addition, a complicated circuit according to a plurality of oil pump configurations is formed inside the oil pump housing, and the oil filter and the various sensors are also assembled into one block, thereby minimizing the oil piping exposed to the outside.

1 is a cross-sectional view of a gas turbine engine according to an embodiment of the invention.
2 is a partially enlarged view of Fig.
3 is an exploded perspective view of the oil pump assembly shown in Fig.
Figure 4 is an exploded perspective view of the oil distributor assembly shown in Figure 3;
FIGS. 5A to 5F are perspective views illustrating the oil pump assembly shown in FIG.
FIG. 6 is a perspective view showing the front and rear surfaces of the pump gear housing of the oil pump assembly shown in FIG. 3;
7 is a cross-sectional view and a circuit diagram of the oil pump assembly shown in Fig.
8 is a configuration diagram of an oil lubrication system according to an 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.

1 is a sectional view of a gas turbine engine according to an embodiment of the present invention, and Fig. 2 is a partial enlarged view of Fig. First, the construction and operation principle of the micro gas turbine engine 100 will be described with reference to FIGS. 1 and 2. FIG.

The air sucked from the outside through the air suction duct 101 flows into the inlet of the centrifugal compressor impeller 102 and is accelerated by the action of the centrifugal force generated by the high speed rotation so as to be accelerated at a high speed along the circumferential direction of the compressor impeller 102 Can be discharged. The discharged high-speed air can be converted to pressure at a speed while passing through the compressor diffuser 103.

Compressed air having passed through the compressor diffuser 103 can be introduced into the combustion chamber 105 provided in a communicated space through the compressed air chamber 104. The combustion gas is supplied to the turbine scroll 106, passes through the turbine nozzle 107, and is supplied to the turbine wheel 109 And can be discharged to the outside.

In order to support the turbine wheel 109 rotating at a high speed and to transmit the rotational power obtained from the turbine wheel 109 to the load device such as the compressor impeller 102 and the generator 400, An axis 130 is required. In the case of a micro gas turbine engine, the compressor impeller 102 is directly connected to the rotary support shaft 130 to simplify the construction of the turbine rotor assembly 117. The turbine wheel 109, the rotary support shaft, and the compressor impeller 102 may be configured in various combinations according to various conditions such as the type of bearings and the bearing position.

However, in the gas turbine engine 100 according to the present embodiment, the gas turbine engine 100 includes the single-ended centrifugal turbine wheel 109, the turbine-side radial bearing 110, and the thrust bearing 111 A single-stage centrifugal compressor impeller 102, and a compressor-side radial bearing 114 in this order. This configuration will be described below, but the basic principle of the present invention is not limited to such a configuration.

Also, the gas turbine engine 100 according to the present embodiment can be used by fastening the generator 400 to the turbine rotor assembly 117. At this time, a shaft coupling 239 is used to transmit the rotational force of the turbine rotor assembly 117 to the generator 400. Although the shape of the shaft coupling 239 is variously known, the shaft coupling 239, which is suitable for transferring a power of at least 100 horsepower at a high speed of at least 30,000 RPM, is generally processed in the form of splines at both ends, And is fastened with a uniform clearance to a relative shaft where the groove is machined.

In the case of the generator 400, various types of generators may be used. However, the generator 400 according to the present embodiment employs a high-speed rotating permanent magnet type synchronous motor having a small weight and high efficiency.

The generator 400 includes a housing made of a permanent magnet and a can surrounding the permanent magnet, a generator rotor 401 having a center shaft and the like, and a generator stator 403 having windings wound around the stacked silicon steel plates. And is connected to the rotor assembly 117 and the shaft coupling 239 to rotate the generator rotor 401 at the same speed to produce electric power. This configuration will be described below, but the basic principle of the present invention is not limited to such a configuration.

FIG. 3 is an exploded perspective view of the oil pump assembly shown in FIG. 1, and FIG. 4 is an exploded perspective view of the oil distributor assembly shown in FIG. FIGS. 5A to 5F are perspective views illustrating the oil pump assembly shown in FIG. FIG. 6 is a perspective view showing the front and rear surfaces of the pump gear housing of the oil pump assembly shown in FIG. 3, and FIG. 7 is a sectional view and a circuit diagram of the oil pump assembly shown in FIG.

The configuration of the oil pump assembly 200 of the gas turbine engine 100 according to the present embodiment will be described with reference to Figs. 1 to 7. Fig.

An oil pump assembly 200 is positioned between the gas turbine engine 100 and the generator 400. [ In order to concentrate the gas turbine engine 100 and the generator 400, the intake housing 119 of the gas turbine engine 100, the both side fastening portions of the oil pump assembly 200, and the coupling- Each of the housings 408 is formed to have an assembling step, and both side fastening portions of the oil pump assembly 200 can be assembled with precise dimensions with the mating housing at the inner diameter portion or the outer diameter portion. As a result, the gas turbine engine 100, the oil pump assembly 200, and the generator 400 are configured to be concentric.

A shaft coupling 239 is provided for transferring the power generated in the gas turbine engine 100 to the generator 400. [ One end of the shaft coupling 239 is connected to the spline formed at the end of the turbine rotor assembly 117 toward the generator 400 and the other end is connected to the spline formed at the end of the generator rotor 401 toward the turbine rotor assembly 117 As shown in Fig. The shaft coupling is configured to transmit power by engagement of these splines.

In order to drive the oil pump assembly 200 while supporting the center of the elongated shaft coupling 239 as the oil pump assembly 200 is positioned between the gas turbine engine 100 and the generator 400, The first pinion gear shaft 201 of the oil pump assembly 200 is formed so that the center spline is formed at the middle portion of the shaft coupling 239 and can engage with the first spline shaft.

The shaft coupling 239 may be configured with an axis of smaller diameter than the turbine rotor assembly 117 or the generator rotor 401. In Fig. 2, reference numeral 239a denotes a first spline formed at both side ends of the shaft coupling 239, and reference numeral 239b denotes a second spline formed at the center of the shaft coupling 239. [

The shaft coupling 239 may be installed through the interior of the primary pinion gear shaft 201. The primary pinion gear shaft 201 is formed in a cylindrical shape so that the shaft coupling 239 can pass through the center thereof and a spline for meshing with the second spline 239b of the shaft coupling 239 is formed therein . A primary pinion gear shaft 201 for supporting the primary pinion gear shaft 201 at the front and rear of the primary pinion gear shaft 201 is provided at the outer diameter portion of the primary pinion gear shaft 201, ) Can be inserted.

In order to support the primary pinion gear shaft bearing 202, a primary pinion gear shaft bearing cage 203 may be provided which applies a preload to the primary pinion gear shaft bearing 202 in the axial direction, A spring for attenuation and an O-ring may be incorporated, and an O-ring for circumferential shock damping may be installed at the outer diameter portion. In this case, various bearings can be used as the first pinion gear shaft bearing 202, but a ball bearing suitable for a low-consumption, small-diameter and high-speed rotation characteristic may be used.

The primary bull gear and the secondary pinion gear shaft assembly 204 include a primary bull gear and a secondary pinion gear fixed to the primary bull gear shaft. The primary bull gear engaged with the primary pinion gear may be formed on a circumference at a certain distance from the center of rotation of the shaft coupling 239. The primary bull gear may be composed of two or more in accordance with the configuration of the oil pump assembly 200, and in this embodiment, three primary bull gears will be described.

At this time, the primary bull gear shaft does not necessarily have to be arranged in an equally divided manner, but may be arranged to be equally divided by 120 degrees in order to prevent unnecessary circumferential side pressure from being applied to the shaft coupling 239. A primary bogie gear and a secondary bogie gear shaft assembly bearing 205 for supporting the primary bogie gear and the secondary pinion gear shaft assembly 204 are provided at both ends of the primary bogie gear and the secondary pinion gear shaft assembly 204, Can be installed. At this time, various methods can be used for the primary bull gear and the secondary pinion gear shaft assembly bearing 205, but a ball bearing as described above can be applied.

The secondary bull gear 206 meshing with the secondary pinion gear may be constituted by one or more in the circumferential position located at a certain distance from the secondary pinion gear shaft. The secondary bull gear 206 may be configured in various numbers according to the configuration of the oil pump assembly 200. In this embodiment, the case of two primary bull gears 206 is described.

Accordingly, when the primary bogie and the secondary pinion gear shaft assembly 204 are three, the secondary bogies 206 may be composed of six, and a plurality of first bogies and gears Each of the plurality of second bull gears 206 may be equally or equally spaced on a circumference located at a distance from the shaft coupling 239.

The gears and the bearings for supporting the gears communicate with the oil storage space inside the compressor housing bearing housing 115 of the gas turbine engine 100, It is possible to lubricate the radial bearing 114 by the oil scattered after the bearing lubrication.

The pump gear set consists of a drive gear and a driven gear that rotates in engagement with the drive gear. The pump gear set sucks the oil by rotation of the two gears and discharges the oil by engagement of the two gears. A pump gear bearing 211 in the form of a pad bearing may be installed to support the pump gear drive gear shaft 209 and the pump gear driven gear shaft 210 in the circumferential and axial directions.

The pump gear bearing 211 is located on both sides of the drive gear and the driven gear, and has two hollows for supporting the respective gear shafts, and oil is supplied to each hollow gap. Further, the pump gear bearing 211 is configured to contact the axial end face of the drive gear and the driven gear and to supply the oil to the gap. At this time, a pump gear bearing seal 212 for preventing oil leakage may be installed on the opposite side of the pump gear of each pump gear bearing 211 to the opposite cover.

On the other hand, the secondary bull gear 206 is assembled to the pump gear driving gear shaft 209 to rotate the driving gear. The pump gear drive gear shaft 209 is supported by the two pump gear bearings 211 described above, so that additional bearings may not be necessary. However, in order to support the secondary bull gear 206, the secondary bull gear 206 and the pump gear driving gear shaft 209 may be provided with secondary bull gears 210a, 210b, A bearing 207 may be additionally provided.

The pump gear drive gear shaft 209, the pump gear driven gear shaft 210 and the pump gear bearing 211 constitute a plurality of pump gear sets, and the pump gear housing 213 includes a plurality of pump gear sets And a plurality of pump gear set built-in portions (214) The pump gear housing 213 can form a plurality of pump gear set built-in portions 214 passing through the inside of the disk-shaped workpiece with the above-described driving gears as reference points.

At this time, the angle of the pump gear set may be differently applied depending on the configuration of the oil passage formed in the pump gear housing 213. However, in order to construct an efficient oil passage, the center of the pump gear drive gear shaft 209 The center of the pump gear driven gear shaft 210 may also be located on the same circumference as the pump gear drive gear shaft 209. [ The suction port of the pump gear set can be directed to the outer peripheral surface of the pump gear housing 213 and the discharge port can be directed to the center of the pump gear housing 213.

At least one of the plurality of pump gear sets serves as a supply pump, and at least one of them serves as an oil feed pump. In the case of this embodiment, although a combination of one feed pump and five feed pumps is described, various combinations of at least one feed pump and at least one feed pump are possible. The oil passage of the pump gear housing 213 is as follows.

The pump gear housing 213 includes three oil passages located inside the pump gear set built-in portion 214, one side of which is closed in the axial direction and the other side is opened. One of which is in communication with the outlet of the supply pump gear set 222 as the supply oil discharge passage 223 and the other is in communication with the discharge port of the oil discharge pump gear set as the oil discharge oil discharge passage 236. And the other one is supplied with the oil filtered through the filter 302 inside the oil distributor assembly 300 attached to the side surface of the oil pump housing 219 as the oil supply oil passage 226 to be distributed to the generator side and the compressor side have.

At this time, when the filter 302 is not used, the supply oil distributing passage 226 is unnecessary, and a hole penetrating through the supply oil discharging passage 223 in the axial direction is formed, and the generator side and the compressor side are communicated with each other to supply oil .

The supply pump gear set 222 sucks the oil through the pump gear housing 213 and the tank oil suction port 220 formed on the outer circumferential surface of the oil pump housing 219, And is connected to the oil line 223 to discharge the oil. The supply oil discharge passage 223 may be connected to the oil supply inlet 309 of the oil distributor assembly 300 through a passage penetrating the pump gear housing 213 and the outer circumferential surface of the oil pump housing 219 again.

The turbine side oil drain oil pump gear set 235 sucks the oil discharged from the turbine side bearing housing 112 through the turbine side oil drain oil inlet 233 formed on the outer peripheral surface of the pump gear housing 213, And is discharged to the oil discharge oil discharge passage 236 through the discharge port formed in the oil discharge oil passage 236.

The generator and compressor side oil pump gear set 232 sucks the oil through the generator side oil drain oil inlet 229 and the compressor side oil drain oil inlet 230 to the generator and compressor side oil drain oil inlet channel 231. The sucked oil joins the exhaust oil discharged from the turbine side exhaust oil drainage pump gear set 235 through the exhaust port formed in the direction of the center of the support at the exhaust oil drainage passage 236. The merged oil is discharged to the oil cooler through the pump gear housing 213 and the oil drain oil outlet 237 formed on the outer peripheral surface of the oil pump housing 219.

In this embodiment, the number of the drainage pumps is five, so that all the drainage pumps can be connected to each other so that the oil drains of all the drainage pumps can use one drainage oil discharge passage 236. [ On the other hand, when the number of the supply pumps also increases, they can be positioned successively to use one supply oil discharge passage 223. The length of each flow path can be increased or decreased according to the number of pump gear sets.

A disk-shaped pump gear housing cover 216 is attached to the pump gear housing 213 in the direction of the compressor to seal the pump gear set internal portion 214 of the pump gear housing 213. The pump gear housing cover 216 may house the primary bull gear and the secondary pinion gear shaft assembly bearing 205 in the direction of the pump gear housing 213.

The pump gear housing cover 216 is formed with a hole through which a plurality of pump gear drive gear shafts 209 pass, and each hole is provided with a pump gear drive gear shaft seal 208 ) Can be installed. The oil pump seal 215 is attached to the contact surface between the pump gear housing 213 and the pump gear housing cover 216 to prevent the oil from leaking through the clearance between the pump gear set- Can be installed.

On the other hand, a hollow is formed in the center of the pump gear housing 213, and a part of the generator side of the first pinion gear shaft bearing cage 203 may be mounted thereon. The pump gear housing 213 and the pump gear housing cover 216 may be provided at a lower portion thereof with a compressor-side oil-discharge oil inlet 230 connected to the generator-side and oil-side oil-drain oil-suction passages 231.

A pump side oil supply port 228 is formed in the pump gear housing cover 216 to supply oil from the oil supply distribution path 226 to the compressor side bearing housing 115, The pipe 238 can be assembled.

In order to support a part of the primary side of the primary pinion gear shaft bearing cage 203 and the primary side bull gear and the secondary pinion gear shaft assembly bearing 205 opposite to the pump gear housing 213, (217) can be installed. The oil pump bearing housing 217 can support the secondary bull gear 206 and the secondary bull gear bearing 207. Further, the oil pump bearing housing cover 218 may be installed to axially support a portion of the first pinion gear shaft bearing cage 203 on the compressor side.

The oil pump housing 219 seals the opposite side of the pump gear set built-in portion 214 of the pump gear housing 213 and connects the oil supply passage 223, the supply oil distribution passage 226, 236 are closed and the pump gear housing 213, the pump gear housing cover 216 and the oil pump bearing housing 217 are coaxially fitted. Further, it tightly contacts the outer circumferential surface of the pump gear housing 213 to seal the oil passage formed in the oil pump housing 219.

The side surface in the direction of the compressor of the oil pump housing 219 is opened so that the pump gear housing 213, the pump gear housing cover 216, the oil pump bearing housing 217, The oil pump bearing housing 217 and the oil pump housing 219 can be fastened with bolts tightly with the components in close contact.

The oil pump housing 219 forms a hollow having a small diameter at its center so that the shaft coupling 239 can penetrate. A plurality of grooves having a predetermined width and a predetermined depth are formed along a circumference of the inner circumference of the oil pump housing 219 in a part of an axial pump gear housing 213 assembly section. The outer circumference of the pump gear housing 213, So that the turbine-side oil-drain oil suction passage 234 and the generator-side oil-drain oil suction oil passage 231 can be formed in close contact with each other.

The generator fan side bearing housing 406 and the oil discharged from the coupling side bearing housing 408 are formed in the lower portion of the oil pump housing 219 in the lower portion of the oil pump housing 210 and on the compressor side oil drain oil suction passage 231 The oil drainage inlet 229 of the generator side can be located.

A generator side supply oil supply port 227 is formed at the position of the supply oil distribution passage 226 to supply oil to the coupling side bearing housing 408 in order to supply oil from the supply oil distribution passage 226 to the generator bearing 405 housing. And the fan-side bearing housing (406).

A hole is formed on the outer circumferential surface of the oil pump housing 219. This hole includes a turbine side oil drainage inlet 233 formed on the outer circumferential surface of the pump gear housing 213, an oil drain oil outlet 237 connected to the oil cooler, a tank oil inlet 220, a supply oil outlet 224, And then connected to a supply oil inlet 225 which is again connected to the oil pump assembly 200 after passing through the filter 302 of the assembly 300.

Particularly, a plane section is formed on the side surface of the oil pump housing 219, and the oil distributor assembly 300 can be closely assembled to the oil pump housing 219. This allows the oil distributor assembly 300 to communicate with the tank oil inlet 220, the feed oil outlet 224, and the feed oil inlet 225 in one assembly to remove the complicated piping.

The oil distributor assembly 300 is attached to the side of the oil pump housing 219 as described above and includes a pressure relief valve 304, an oil pressure sensor 305, an oil temperature sensor 306, a filter 302, . A tank oil inlet 307 is formed in the distributor block 301 of the oil distributor assembly 300 so that the oil is sucked from the oil tank by the suction force of the supply pump gear set 222, An oil suction passage to be connected can be formed.

The supply oil outlet 224 is in communication with the supply oil inlet 309 to allow the pressurized oil from the supply pump gear set 222 to flow into the inlet of the filter 302. When the pressure relief valve 304 is provided in the oil passage supplied to the filter 302 and exceeds the set pressure, the oil is supplied to the oil suction passage through the oil bypass passage so that the supply pump is sucked in again.

A part of the oil that has passed through the filter 302 returns to the oil pump assembly 200 through the oil supply inlet 225 communicated with the oil supply port 310 of the supply oil oil pump, Side supply oil supply port 228 and the generator-side supply oil supply port 227 via the first oil supply port 227 and the second oil supply port 227, respectively. And the remainder is introduced into the external piping through the supply oil turbine side supply port 311 of the oil distributor assembly 300 to be supplied to the turbine side radial bearing 110 to be supplied to the turbine oil pipe assembly 120 of the gas turbine engine 100 ).

The oil pressure sensor 305 is installed before and after the filter 302 to measure the differential pressure across the filter 302 and measure the oil pressure supplied to the bearing. The oil temperature sensor 306 may be installed at a suitable one of the above-described supply oil passages.

The principle of operation will be described based on the above-described configuration.

First, when the gas turbine engine 100 is started, the turbine rotor assembly 117 rotates, and the rotational power of the turbine rotor assembly 117 is transmitted to the shaft coupling 239 and the generator rotor 401 without acceleration or deceleration . Accordingly, the turbine rotor assembly 117, the shaft coupling 239, and the generator rotor 401 rotate at the same speed.

The primary pinion gear shaft 201 also rotates at the same speed as the turbine rotor assembly 117 due to the engagement of the shaft coupling 239 and the primary pinion gear shaft 201. [ When the primary pinion gear rotates, the primary primary gear engaged with it rotates in accordance with the gear reduction ratio, and the secondary pinion gear coaxially assembled with the primary primary gear rotates at the same speed as the primary primary gear.

When the secondary bull gear 206 engaged with the secondary pinion gear rotates in accordance with the gear reduction ratio, the driving gear of the pump gear set coaxially assembled with the secondary bull gear 206 is also engaged with the secondary bull gear 206 It rotates at the same speed. As the drive gear of the pump gear set rotates, the driven gear meshing with the drive gear also rotates at the same speed, which causes the oil to be sucked and discharged.

At this time, the reduction ratio of each of the pinion gear and the bull gear can be determined by various factors such as the rated rotation speed of the gas turbine engine 100, the flow rate of the oil pump assembly 200, and the like. However, if the rotational speed of the gas turbine engine 100 is relatively low and the required reduction ratio is small, the secondary bull gear 206 is engaged with the primary pinion gear without any primary bogie gear and secondary bogie gear described above, The oil pump assembly 200 may be driven with deceleration. However, in this case, since the size of the circumference where the center axis of the secondary bull gear 206 is located becomes small, the number of pump gear sets and oil flow path formation can be restricted.

In general, in the case of the shaft coupling 239, assuming that the shaft coupling 239 having the same diameter is assumed, the longer the length of the shaft coupling 239, the longer the section that can take stress, . At the same time, however, if the length of the shaft coupling 239 is increased, the weight between both end portions supporting the shaft coupling 239 is increased, so that a lot of bending and vibration occur during high-speed rotation. Therefore, as the distance between the two rotating shafts connecting is increased, the vibration increases at high speed.

Therefore, when the oil pump assembly 200 is constructed between the turbine rotor assembly 117 and the generator rotor 401 of the gas turbine engine 100 according to the present embodiment, The turbine rotor assembly 117 and one end of the pinion gear shaft are connected by a single shaft coupling and the other end of the pinion gear shaft and the generator rotor 401) to the other shaft coupling.

However, in the above case, the length of the shaft coupling is excessively shortened, and the size of the power that can be transmitted is limited. In order to solve this problem, there is a problem that the diameters of the rotating shafts There is nothing.

However, in the present embodiment, the front and rear of the primary pinion gear shaft 201 are respectively supported by bearings, and the primary pinion gear shaft 201 is made hollow to form a spline capable of meshing with the shaft coupling 239 therein And the shaft coupling 239 passes through the primary pinion gear shaft 201 to transfer power to the generator rotor 401 and the primary pinion gear. The center of the shaft coupling 239 can be supported within the proper clearance range by the second spline 239b of the shaft coupling 239 while maintaining the length of the shaft coupling 239, Excessive bending and vibration can be prevented.

Although not shown, O-rings are coupled to the outer diameter and side surfaces of the first pinion gear shaft bearing cage 203 so that vibration and shock transmitted to the first pinion gear shaft 201 can be attenuated, 239 can be further attenuated.

The oil passage will be described as follows. First, the supply flow from the oil tank is started from the oil tank, through the tank oil inlet 307 and the tank oil inlet 308 of the oil distributor assembly 300, the tank oil inlet 220 of the oil pump assembly 200, And the inlet of the feed pump gear set 222.

The oil pressurized in the feed pump gear set 222 starts from the outlet of the feed pump gear set 222 and is supplied to the supply oil discharge passage 223 and the oil supply outlet 224 of the oil pump assembly 200, Through the supply oil intake port 309 of the oil pump assembly 300, the filter 302, the supply oil pump side supply port 310, the supply oil inlet port 225 of the oil pump assembly 200, and the supply oil distribution channel 226 Side supply oil supply port 227 and the compressor-side supply oil supply port 228 and is supplied to each bearing oil supply passage.

Part of the oil that has passed through the filter 302 of the oil distributor assembly 300 is discharged to the supply oil turbine side supply port 311 and supplied to the turbine oil pipe assembly 120 of the gas turbine engine 100 Side radial bearing 110 and the thrust bearing 111 oil supply passage.

In the case of the turbine side oil drainage passage, the oil flows from the turbine side bearing housing 112 through the turbine oil pipe assembly 120 to the turbine side oil drainage inlet 233 of the oil pump assembly 200, the turbine side drainage oil drainage passage 234 ), And sucked by the vacuum pressure to the suction port of the turbine-side oil-leaving oil-drain pump gear set 235.

1, both the compressor-side bearing housing 115 and the reduction gear installation space in the oil pump assembly, and the outlet ducts of the fan-side bearing housing 406 and the coupling-side bearing housing 408 of the generator 400, And communicates with the lower portion of the oil pump assembly 200.

Therefore, the generator and compressor discharge oil passages are connected to the inlet of the generator and compressor-side oil feed pump gear set 232 through the generator-side and oil-side oil drain oil suction passages 231 in the lower portion of the oil pump assembly 200, And is sucked by the vacuum pressure applied to the suction port of the generator and compressor-side drain pump gear set (232).

Both the turbine side oil drainage oil pump gear set 235 and the outlet of the generator and compressor side oil pump gear set 232 are connected to and joined to the oil drain oil drain line 236 of the oil pump assembly 200, The oil is discharged to the outside through the oil outlet 237 and supplied to the oil cooler, cooled by the oil cooler, and then returned to the oil tank.

8 is a configuration diagram of an oil lubrication system according to an embodiment of the present invention.

Referring to FIG. 8, the oil tank and the oil cooler may be separately installed separately. The oil tank may be connected to an oil supply pipe directed to the oil pump assembly 200 and an oil return pipe returning oil cooled by the oil cooler after lubrication. A vapor filter for separating the vapor can be installed in the upper part of the oil tank, and the air passing through the vapor filter can be discharged to the outside. The oil cooler receives lubricated high temperature oil from the oil feed pump and cools it with a fan or the like.

The pressure distribution of the bearing housing and the oil passage will be described with reference to FIGS. 1 and 8. FIG.

The high-pressure combustion gas leaking to the rear surface of the turbine wheel 109 and the high-pressure compression leaking to the back surface of the compressor impeller 102 are formed in the clearance between the turbine-side bearing housing 112 and the turbine rotor assembly 117, There is a high possibility that a pressure higher than atmospheric pressure is generated due to air. There is a high possibility that a vacuum pressure slightly lower than the atmospheric pressure is formed due to the suction vacuum pressure generated in the front portion of the compressor impeller 102 in the clearance between the compressor housing bearing housing 115 and the rotating body. There is a possibility that a pressure slightly higher than the atmospheric pressure is generated around the gap between the generator fan side bearing housing 406 and the coupling side bearing housing 408 and the rotation shaft due to the pressure of cooling air supplied from the fan 404 of the generator 400 high.

In order to prevent oil or vapor from leaking to the outside of the bearing housing, it is advantageous that the pressure inside the bearing housing is lower than the pressure of the circumference communicated with the gap. In the case of the compressor housing bearing housing 115, It is difficult to maintain the vacuum pressure lower than the vacuum pressure of the front portion of the impeller 102. Therefore, the pressure inside the bearing housing can be kept low by using the drain pump.

However, as described above, when the gas turbine engine 100 is driven, the high-pressure combustion gas leaking between the turbine wheel 109 and the turbine screen 108 and the high-pressure compressed air leaking to the back surface of the compressor impeller 102 The pressure of the turbine side bearing housing 112 can be increased.

Further, if the turbine side bearing housing 112, the compressor side bearing housing 115, the generator fan side bearing housing 406, and the generator coupling side bearing housing 408 are connected together through the drainage pump gear set, If the displacement of the exhaust pump gear set is not sufficiently large when the combustion gas and the compressed air pressure are greatly increased, the increase in the amount of combustion gas and compressed air leaked into the turbine side bearing housing 112 exceeds the suction capacity of the exhaust pump gear set , The pressure of the compressor-side bearing housing 115 may rise, and oil and vapor may leak to the air suction portion of the compressor impeller 102.

Therefore, in this embodiment, as described above, the turbine side oil drainage passage, the generator and the compressor side oil drainage passage are separated from each other, and a separate drainage pump gear set is provided in each of the oil drainage passages, 115 and the fan side of the generator 400 and the inside of the coupling side bearing housings 406, 408 can always maintain a low pressure.

In particular, the generator-and-compressor-side drain pump gear set 232 and the compressor-side bearing housing 115 communicate with each other at the shortest distance without any separate piping to minimize the suction differential pressure of the pump, It is more advantageous to keep the pressure inside the chamber 115 low. In addition, the oil-leaving oil that has passed through the oil-feeding pump gear set has the merit of joining to one oil-cooler by one outlet port without complicated piping configuration by joining to one exhaust passage.

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.

100: Gas turbine engine 101: Air intake duct
102: compressor impeller 103: compressor diffuser
104: Compressed air chamber 105: Combustion chamber
106: Turbine scroll 107: Turbine nozzle
108: Turbine screen 109: Turbine wheel
110: Turbine side radial bearing 111: Thrust bearing
112: turbine side bearing housing 113: turbine side seal
114: compressor side radial bearing 115: compressor side bearing housing
116: compressor side seal 117: turbine rotor assembly
118: Turbine rotor assembly shaft coupling connection
119: intake housing 120: turbine oil pipe assembly
130:
200: Oil pump assembly 201: First pinion gear shaft
202: First pinion gear shaft bearing
203: First pinion gear shaft bearing cage
204: Primary bogie and secondary pinion gear shaft assembly
205: Primary bogie and secondary pinion gear shaft assembly bearings
206: Secondary fire gears 207: Secondary fire gear bearings
208: Pump gear drive gear shaft seal 209: Pump gear drive gear shaft
210: Pump gear driven gear shaft 211: Pump gearing bearing
212: pump gear bearing seal 213: pump gear housing
214: pump gear internal part 215: oil pump seal
216: pump gear housing cover 217: oil pump bearing housing
218: Oil pump bearing housing cover
219: Oil pump housing 220: Tank oil inlet
221: Tank oil suction passage 222: Feed pump gear set
223: Supply oil discharge passage 224: Supply oil discharge hole
225: Supply oil inlet 226: Supply oil distribution channel
227: generator-side supply oil supply port 228: compressor-side supply oil supply port
229: Drain oil inlet of the generator side 230: Drain oil inlet of the compressor side
231: Drain oil in the side of generator and compressor
232: Drain pump gear set for generator and compressor side
233: Turbine side exhaust oil inlet 234: Turbine side exhaust oil suction side
235: Turbine side oil drain oil pump gear set
236: Exhaust oil discharge channel 237: Exhaust oil discharge port
238: Compressor side oil feed pipe 239: Shaft coupling
300: Oil distributor assembly 301: Distributor block
302: filter 302: filter housing
304: Pressure relief valve 305: Oil pressure sensor
306: Oil temperature sensor 307: Tank oil inlet
308: Tank oil supply port 309: Supply oil inlet port
310: Supply oil The oil pump side supply port
311: Supply The supply side of the oil turbine
400: generator 401: generator rotor
402: Generator rotor shaft coupling connection
403: generator stator 404: generator fan
405: Generator bearing 406: Generator fan-side bearing housing
407: Generator fan side bearing housing seal
408: Generator coupling side bearing housing
409: Generator coupling side bearing housing seal
410: Generator housing

Claims (11)

A turbine wheel rotating at high speed by the combustion gas and a compressor impeller coupled to the turbine wheel by a rotation support shaft,
A generator including a generator rotor coupled to the front of the compressor impeller by axial coupling, and
A plurality of primary pinion gears meshing with the primary pinion gears, a plurality of secondary pinion gears sharing an axis with the plurality of primary bull gears, a plurality of primary pinion gears fixed to the outer peripheral surface of the plurality of primary pinion gears, A plurality of secondary bogies engaged with the secondary pinion gears, a plurality of drive gears sharing an axis with the plurality of secondary bogies, and a plurality of driven gears meshing with the plurality of drive gears, Lt; RTI ID = 0.0 >
/ RTI >
Wherein the shaft coupling has a first spline formed at both ends thereof and is engaged with a shaft coupling connection portion of the compressor impeller and the generator rotor, and a second spline is formed at the center to engage with the first pinion gear shaft,
Wherein the primary pinion gear shaft is supported by the primary pinion gear shaft bearings in front and rear. delete The method according to claim 1,
Said plurality of primary bull gears being equally distributed on a circumference located at a first distance about said axis coupling,
Said plurality of secondary bull gears being equally distributed on a circumference located at a second distance about said axis coupling,
Wherein the second distance is greater than the first distance. The method according to claim 1,
Wherein the plurality of pump gear sets includes a feed pump gear set, a generator and a compressor-side feed pump gear set, and a turbine side feed oil feed pump set,
Wherein the feed pump gear set, the generator and compressor side feed pump gear set, and the turbine side feed oil feed pump set are each located in a pump gear set internal portion formed in a pump gear housing. 5. The method of claim 4,
The pump gear housing includes three oil passages located on the inside of the pump gear set built-in portion, one side of which is closed in the axial direction and the other side is opened, and is assembled inside the oil filter housing,
An oil splitter assembly having a filter therein is attached to a side surface of the oil filter housing. 6. The method of claim 5,
Wherein the three oil passages are formed in the three-
A supply oil discharge passage communicating with the first discharge port of the supply pump gear set,
An exhaust oil discharge passage communicating with the second outlet of the generator and compressor side drainage pump gear set and the turbine side drainage oil drainage pump gear set,
And a supply oil distributing passage supplied with oil filtered through the filter. The method according to claim 6,
The supply pump gear set sucks oil through a pump oil housing and a tank oil inlet formed on an outer circumferential surface of the oil pump housing, discharges oil to the supply oil discharge channel through the first outlet,
Wherein the feed oil discharge passage is connected to the inlet of the filter through a feed oil inlet of the oil distributor assembly. 8. The method of claim 7,
Wherein a pressure relief valve is provided in the oil passage supplied from the oil distributor assembly to the filter to supply oil to the oil suction passage through the oil bypass passage so that the supply pump is re-suctioned. 8. The method of claim 7,
The turbine-side oil-drain oil pump set includes a turbine-side oil-drain pump for receiving oil discharged from the turbine-side bearing housing through a turbine-side oil-discharge oil inlet formed on an outer circumferential surface of the pump gear housing, And the gas turbine engine. 10. The method of claim 9,
Wherein the generator and the compressor-side drain pump gear set suck oil through the generator-side exhaust oil inlet and the compressor-side exhaust oil inlet, and through the second outlet to the exhaust oil discharge channel A gas turbine engine that emits oil. 11. The method of claim 10,
The oil discharged from the turbine side oil drain oil pump set for turbine side and the oil discharged from the generator and the oil drain pump gear set on the side of the compressor join together in the oil drain oil flow path and the oil drain oil outlet formed on the outer peripheral surface of the pump gear housing and the oil pump housing To the oil cooler.

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