KR100799199B1 - Turbo compressor - Google Patents

Abstract

A turbo compressor is disclosed. The turbo compressor of the present invention is connected to a drive motor, a drive shaft of the drive motor, a high speed rotatable bull gear, and a pinion gear that rotates in accordance with the rotation of the bull gear in engagement with teeth of the bull gear. (Pinion Gear), a compression vane connected to the axis of rotation of the pinion gear to compress air, a gear box surrounding and enclosing the bull gear and the pinion gear, and located on the front and rear walls of the gear box and the bull gear And a plurality of bearings for supporting the pinion gear, an engagement portion of the bull gear and the pinion gear, an oil supply portion for supplying oil to the bearing, and a lower portion in the gear box, whereby the oil is scattered to the bull gear. It characterized in that it comprises an oil catcher (Oil Catcher) to block the phenomenon of disturbing the rotation.

Description

Turbo compressor

1 is a cross-sectional view showing a conventional turbo compressor mainly on a driving part;

2A is a cross-sectional view showing a gear box of a conventional turbo compressor.

FIG. 2B is a cross-sectional view taken along the line A-A of FIG. 2A

3a is a sectional view showing a gearbox of a turbocompressor according to the invention

3B is a cross-sectional view taken along the line B-B in FIG. 3A

4A and 4B are a perspective view and a plan view of the oil catcher of FIG. 3.

<Brief description of symbols for the main parts of the drawings>

10 ... drive motor 11,30,100 ... bull gear

12,13,31,32,101,102 ... pinion gear 20,33,103 ... gear box

14,15,16 Compressor 21,22,23 Bearing

50a, 50b ... guide plate 200 ... oil catcher

The present invention relates to a turbocompressor, and more particularly, to a turbocompressor whose output can be raised by having an oil catcher installed at a predetermined position inside the gearbox of the turbocompressor.

Typically, a turbo compressor serves to deliver high pressure air to the required equipment by compressing the air to high pressure. An example of a turbo compressor is a gas turbine. The gas turbine compresses air into a compressor and sends it to a combustor, and mixes fuel to ignite and burns it to produce a combustion gas of high temperature and high pressure. It is a prime mover that drives the turbine to get output. Here, the effective output is the difference between the turbine generating power and the compressor driving power, which is used for driving a generator, a vehicle, and the like as the shaft output. Turbo compressors can be divided into Integral Geared Type and Single Shaft Multi-stage Type. Integral Geared Types are mainly used as industrial turbo compressors that require relatively large amounts of compressed air at low pressure.

1 is a cross-sectional view mainly showing a driving part of a conventional Integral Geared Type turbo compressor. Referring to the drawings, the drive motor 10 is connected to a bull gear 11 through a drive shaft, and pinion gears 12 and 13 on both sides that follow the rotation of the bull gear 11 are connected. The plurality of compression vanes 14, 15, and 16 are driven by rotating at high speed. The bull gear 11 and the pinion gears 12 and 13 are installed in the gear box 20 and the gears 11 by the bearings 21, 22, 23 at predetermined positions on the gear box 20. 12 and 13 are supported. When the drive motor 10 is operated and external air flows through the inlet guide vanes (not shown), the first compression vanes 14 and the first intercooler (not shown) are respectively compressed and cooled in one stage. Again two stages are compressed and cooled in the second compression vane 15 and the second intercooler (not shown), and again in the third compression vanes 16. The compressed air that has passed through the third compression vane 16 is temporarily stored in a storage tank (not shown), and is then sent to a combustor of a gas turbine.

Figure 2a is a cross-sectional view showing a gear box and the inside of a conventional turbo compressor, Figure 2b is a cross-sectional view taken along the line A-A of Figure 2a. Referring to the drawings, the bull gear 30 is located in the inner center portion of the gear box 33 and pinion gears 31 and 32 are connected to both side ends of the bull gear 30. Nozzles 40, 41 for injecting oil, which lubricate and cool the contact portion between the pinion gears 31, 32 and the bull gear 30, are provided at predetermined positions. Oil outflow hole through which oil supplied from the outside of the gear box 33 flows into the gear box to lubricate and cool the bull gear 30 support bearing 34 and the pinion gears 31 and 32 support bearings (not shown). 42, 43, and 44 are formed at the front and rear inner walls of the gear box 33, and oil discharge holes 45 through which the oil is discharged are formed at the lower end of the gear box 33. Guide plates 50a and 50b for guiding oil interspersed on the inner wall of the gear box 33 to the oil discharge hole 45 are formed on the front and rear inner walls of the gear box 33. The guide plates 50a and 50b have a bottom surface having a depth enough to cover the oil outflow holes 43 and 44 and a joining flange at both ends that can be joined to the front and rear inner walls of the gear box 33. One plate. Guide plates (50a, 50b) is the oil flowing in the gear box 33 from the oil ejection nozzles (40, 41) and oil outlet holes (42, 43, 44) both ends of the guide plate (50a, 50b) Through the inclined surface 46 to be discharged to the oil discharge hole (45).

The oil supplied into the gear box 33 through the oil spray nozzles 40, 41 or the oil outlet holes 42, 43, 44 is caused by the high speed rotation of the bull gear 33 after the lubrication and cooling action. Can be wound up 33) or strongly pressed against the inner wall of the gearbox 33. The oil splashed strongly on the inner wall prevents stable high-speed rotation of the bull gear 33 connected to the driving motor again, resulting in power loss.

The present invention has been made to solve the above problems, an object of the present invention is to prevent the loss of power by the oil for lubrication and cooling does not interfere with the stable high-speed rotation of the bull gear in the gearbox It is to provide a compressor.

In order to achieve the above object, the present invention is connected to a drive motor, a drive shaft of the drive motor, a high speed rotatable bull gear (Bull Gear), the teeth of the bull gear in engagement with the rotation of the bull gear ( Pinion gear (Pinion Gear) to be driven along the rotation, the compression vane is connected to the rotation axis of the pinion gear and compresses air, a gear box containing and enveloping the bull gear and the pinion gear, the front and rear of the gear box A plurality of bearings located on a wall to support the bull gear and the pinion gear, an engagement portion of the bull gear and the pinion gear, an oil supply unit for supplying oil to the bearing, and a lower side in the gear box, Oil catcher, characterized in that the oil catcher (block) that blocks the rotation of the gear by being scattered by the bull gear It provides a compressor.                     

According to the present invention, the oil catcher is parallel to the front and rear surfaces of the bull gear and is separated from the width between the front and rear inner surfaces of the gear box and is less than or equal to the width of the bull gear to form an empty space therein. It provides a turbo compressor characterized in that it has a side and a bottom formed with a through-hole so as to be discharged to the lower portion of the gear box without obstruction.

The present invention provides a turbo compressor, characterized in that the side of the oil catcher is tapered at a predetermined angle so as to maintain a substantially constant distance from one outer circumference of the bull gear.

Hereinafter, a turbo compressor according to the present invention will be described in detail with reference to the accompanying drawings.

 The turbo compressor of the present invention is composed of basic components similar to the conventional turbo compressor of FIG. 1 and has been described above in terms of its operation mechanism.

Figure 3a is a cross-sectional view showing an embodiment of a gear box of the turbo compressor according to the present invention, Figure 3b is a cross-sectional view along the line B-B of Figure 3a. Referring to the drawings, the bull gear 100 is located in the inner center portion of the gear box 103 and pinion gears 101 and 102 are connected to both side ends of the bull gear 100. Nozzles 110 and 111 for injecting oil for lubricating and cooling the gears 100, 101 and 102 to the contact portions of the pinion gears 101 and 102 and the bull gear 100 are installed at predetermined positions. Oil outflow from which oil supplied from outside gear box 103 flows into gear box 103 for lubricating and cooling bull gear 100 support bearing 104 and pinion gears 101 and 102 support bearing (not shown). Balls 112, 113, and 114 are formed in the front and rear inner walls of the gear box 103, and oil discharge holes 115 through which the oil is discharged are formed in the lower end of the gear box 103. The oil catcher 200 is installed at the lower end of the gear box 103 so as to cover the lower part of the bull gear 100.

4A and 4B are perspective and plan views of the oil catcher shown in FIGS. 3A and 3B. Referring to the drawings, the oil catcher 200 has an internal space formed so as to cover one end of the bull gear 100 of FIGS. 3A and 3B. As shown in FIG. 3B, the width t2 between the front and rear surfaces of the oil catcher exceeds the cross-sectional thickness t1 of the bull gear 100 and is at a distance less than the width t3 between the front and rear walls of the gear box 103. Is determined. The side surfaces 205 and 206 and the lower surface 204 of the oil catcher 200 maintain a substantially constant distance from the gear teeth of the bull gear 100 side end located inside the oil catcher 200. 205 and 206 are tapered. Therefore, the oil catcher has a square skirt shape when viewed from the front. The upper surface of the oil catcher 200 is open so that the side end of the bull gear 100 can rotate inside the oil catcher 200, and the lower surface 204 has the first and second oil spray nozzles of FIG. 3A ( A plurality of fine through holes 210 are formed to discharge oil introduced into the gear box 103 from the 110 and 111 in the direction of the bull gear 100 without being returned. As shown in FIG. 3A, the second oil spray nozzle 111 injects oil from the top of the pinion gear 102, so that a relatively large amount of oil is discharged to the bottom thereof. Therefore, a long hole 212 is formed at one side of the oil catcher 200 positioned below the oil injection nozzle 111 to help smooth discharge of oil. The right side 205 of the oil catcher 200 is provided with a recessed pan seat 211 in which the first oil spray nozzle 110 for spraying oil from the bottom of FIG. 3A can be located. A flange 213 is formed at the upper boundary of the front and back surfaces 202 and 203 so that the oil catcher 200 can be fixed to the gear box 103 of FIG. 3B.

Referring to the operation of the oil catcher 200 in the gear box 103 with reference to Figures 3a and 3b and 4a and 4b, the oil injected from the first oil injection nozzle 110 is the pinion gear 101 and the bull gear Lubricates and cools the engagement portion of the 100 and flows down and is discharged from the oil discharge hole 115 to the outside of the gear box 103 through the fine through hole 210 of the oil catcher 200. The oil sprayed from the second oil spray nozzle 111 lubricates and cools the engagement of the pinion gear 102 and the bull gear 100 and flows downward to flow the oil discharge hole 115 through the long hole 212 of the apparatus 200. ) Is discharged to the outside of the gear box 103. Oil lubricated and cooled by the bull gear support bearing 104 and the pinion gear support bearing (not shown) and the oil spilled through the oil outlet holes 112, 113 and 114 flows through the front and rear surfaces 202 and 203 of the oil catcher 200 and the oil outlet hole. It is discharged from 115 to the outside of the gear box 103.

Experiments on a turbocompressor with a drive motor of 600 hp (about 450 kW) showed the following results.

   Power Loss (kW) Remarks Before installing oil catcher 53.3 24% less than before oil catcher After installing oil catcher 40.5

Thus, after installing the oil catcher than before installing the oil catcher, the output of the turbo compressor is increased by 12.8 kW, which reduces the output loss by about 24%.

As described above, the turbo compressor according to the present invention can reduce the output loss of the turbo compressor by preventing the oil for lubrication and cooling from disturbing the stable high speed rotation of the bull gear in the gear box.

Although the present invention has been described with reference to the embodiments shown in the drawings, this is merely exemplary, and it will be understood by those skilled in the art that various modifications and equivalent other embodiments are possible. Therefore, the true scope of protection of the present invention should be defined only by the appended claims.

Claims (3)

A high speed rotatable bull gear connected to the rotational shaft of the drive source; A pinion gear engaged with teeth of the bull gear and driven to rotate according to the rotation of the bull gear; A compression vane connected to the rotation shaft of the pinion gear to compress air; A gear box including and enclosing the bull gear and the pinion gear; A plurality of bearings positioned on the front and rear walls of the gear box and supporting the bull gear and the pinion gear; An oil supply unit for supplying oil to the engaged portion of the bull gear and the pinion gear and the bearing; And an oil catcher installed at the lower side of the gear box so as to cover the lower part of the bull gear and preventing the oil from scattering on the bull gear and preventing its rotation. The oil catcher is a parallel front and rear surface larger than the cross-sectional thickness of the bull gear, spaced apart by a width less than the width between the front and rear inner surfaces of the gear box to form a space for accommodating the lower portion of the bull gear therein; And a side surface and a bottom surface of the through hole formed so that the oil can be discharged to the lower portion of the gear box without disturbing the rotation of the bull gear. delete The method of claim 1, And the side surface is tapered at a predetermined angle to maintain a substantially constant distance from one outer circumference of the bull gear.

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