JP2011522994A - Turbo blower and high-speed rotating body used therefor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a turbo blower capable of minimizing an axial load and a radial load acting on a high-speed rotating body and a bull gear.
The present invention relates to a turbo blower and a high-speed rotating body used therefor. The turbo blower includes i) a motor having a motor shaft, ii) a gear housing containing a bull gear fastened to the motor shaft and a pinion gear meshing with the bull gear, iii) a rotating shaft having a pinion gear formed on the outer peripheral surface, and a rotating shaft An impeller coupled to one end of the shaft, a rotating shaft, a pinion gear, and at least one first composite bearing, and a rotating body housing partly incised so that the pinion gear is exposed. A high-speed rotating body incorporated and coupled; and iv) a scroll unit that discharges compressed air while surrounding the impeller.
[Selection] Figure 1

Description

  The present invention relates to a turbo blower, and more particularly to a turbo blower capable of minimizing an axial load and a radial load generated during driving, and a high-speed rotating body used in the turbo blower.

  The turbo blower uses a high-speed rotating body to obtain a high output with a small volume. High-speed rotating bodies are classified into a direct drive system that is directly connected to a high-speed motor by a drive system and an indirect drive system that is connected to a general motor through a gear speed increasing device that increases the rotational speed.

  A high-speed rotating body of a direct drive system is usually supported by an air bearing. However, since air bearings do not have high durability, many restrictions are imposed on long-term use (for example, three years or more).

  A normal gear speed increaser used in the indirect drive system is formed by a bull gear fixed to a motor shaft and a pinion gear that is installed on a high-speed rotating body and meshes with the bull gear. However, a turbo blower equipped with a gear speed increaser generates a radial load and an axial load on the high-speed rotating body and the bull gear during its operation, and thus a structural improvement is required to reduce this.

  In addition, turbo blowers equipped with gearboxes use gearboxes with built-in bull gears and pinion gears, but in order to assemble gearboxes in turbomachines, not only the gearbox itself is divided horizontally. The bearing that supports the gear shaft must also be divided horizontally.

  When the gear box is divided and manufactured in this way, the manufacturing precision becomes a problem. When the gear shaft is centered for high-speed rotation after assembling the turbo machine, the assembling precision is high. It is difficult to plan. In addition, the number of parts increases and manufacturing costs increase.

  The indirect drive type turbo blower has to include an oil pump in order to supply the lubricating oil, which increases the number of parts. Further, since the bull gear and the motor shaft are conventionally fixed by shrink fitting, there is a problem that it is difficult to disassemble and assemble the bull gear when it is necessary to replace the bull gear due to wear of the teeth of the bull gear.

Korean Patent Registration No. 10-0723040

  An object of the present invention is to provide a turbo blower capable of minimizing an axial load and a radial load acting on a high-speed rotating body and a bull gear.

  Another object of the present invention is to form an oil circulation structure in the turbo blower and circulate and supply the lubricating oil to the high speed rotating body without installing an oil pump for supplying the lubricating oil. It is to provide a turbo blower capable of

  Furthermore, another object of the present invention is to provide a turbo blower capable of simply assembling and disassembling a high-speed rotating body, a bull gear, and a motor.

  A turbo blower according to an embodiment of the present invention includes: i) a motor including a motor shaft; ii) a gear housing including a bull gear fastened to the motor shaft and a pinion gear meshing with the bull gear; and iii) a pinion gear formed on the outer peripheral surface. A rotating body housing that includes a rotating shaft, an impeller coupled to one end of the rotating shaft, a rotating shaft, a pinion gear, and at least one first composite bearing, and is partially cut to expose the pinion gear. A high-speed rotating body that is partially incorporated in the gear housing and coupled thereto, and iv) a scroll portion that discharges compressed air while surrounding the impeller.

  The first compound bearing is i) a compound bearing block integrally including a slide bearing block and a ball bearing block, and ii) formed on the outer peripheral surface of the rotating shaft, and is incorporated in the slide bearing block so that the slide bearing is mounted together with the slide bearing block. It may comprise a sliding bearing shaft that constitutes, and iii) a ball bearing that is built into the ball bearing block.

  The first composite bearing is located on both sides of the pinion gear, and the set gap of the slide bearing can be larger than the set gap of the ball bearing. The slide bearing shaft is formed so that a plurality of oil grooves and a plurality of taper grooves for forming an oil film are inclined on the surface, and the slide bearing block forms a side pressure buffer groove in a portion of its inner surface facing the bull gear. Thus, the side pressure caused by the bull gear can be absorbed.

  The high-speed rotating body forms a vent hole at the end of the rotating body housing toward the impeller, the pinion gear is formed in a helical gear shape, and the direction of the helical gear is a force that pulls the rotating shaft in the direction opposite to the impeller direction when the rotating shaft rotates. Set to occur.

  The gear housing forms an arcuate guide cover having a plurality of oil guide grooves while enclosing a part of the bull gear on its inner wall surface, and forms an oil box connected to the end of the guide cover on the inner upper part thereof. be able to.

  The gear housing has an oil pipe formed therein, and the lubricating oil collected in the oil box is supplied by the first composite bearing, and one end of the oil pipe is connected to an oil discharge port formed in the oil box, The other end of the pipe is connected to an oil supply port formed in the first composite bearing.

  The rotating body housing may form a steam outlet for discharging oil vapor, and the turbo blower may further include an oil steam cooler connected to the steam outlet and the oil box. The oil vapor cooler can condense the oil vapor discharged to the steam discharge port and supply it to the oil box.

  The gear housing has an oil storage tank formed in a lower portion thereof, the oil storage tank has a pair of upper and lower holes formed in a side wall thereof, and the gear housing is provided in a communication pipe having the pair of holes communicated with each other, and the communication pipe. A control valve can further be included.

  The bull gear is directly fastened to the motor shaft, and the gear housing forms a coupling surface having an opening larger than the diameter of the bull gear on the side facing the motor, and the coupling surface can be coupled to the motor.

  A high-speed rotating body according to an embodiment of the present invention includes: i) a rotating shaft having a pinion gear meshing with a bull gear formed on an outer peripheral surface; ii) an impeller coupled to one end of the rotating shaft; and iii) a pair provided on both sides of the pinion gear. And iv) a rotating body housing that incorporates a rotating shaft, a pinion gear, and a pair of first compound bearings, and is partially cut to expose the pinion gear.

  Each of the pair of first compound bearings includes i) a compound bearing block integrally including a sliding bearing block and a ball bearing block, and ii) formed on the outer peripheral surface of the rotating shaft, and incorporated in the sliding bearing block together with the sliding bearing block. A sliding bearing shaft constituting the sliding bearing, and iii) a ball bearing incorporated in the ball bearing block.

  The set gap of the slide bearing is larger than the set gap of the ball bearing, and the slide bearing shaft is formed to incline a plurality of oil grooves and a plurality of taper grooves for forming an oil film on the surface, and the slide bearing block is formed on the inner surface thereof. In order to absorb the side pressure caused by the bull gear, a side pressure buffering groove can be formed in the direction opposite to the direction exerted by the side pressure.

  A turbo blower according to another embodiment of the present invention includes: i) a motor including a motor shaft; ii) a bull gear which is detachably coupled to the motor shaft and forms a hollow for installing a fixed shaft at the center thereof; iii 2) a second composite bearing provided between the fixed shaft and the bull gear and provided with a tapered roller bearing and a ball bearing adjacent to each other in a direction parallel to the motor shaft; and iv) a pinion gear that meshes with the bull gear on the outer peripheral surface. And a high-speed rotating body including an impeller coupled to one end of the rotating shaft.

  The turbo blower includes i) a motor cover that is fastened to the motor and supports the motor shaft, and ii) a gear housing that incorporates a bull gear and a pinion gear, and has an opening having a diameter larger than the diameter of the bull gear on the side surface that is fastened to the motor cover. Can further be included.

  The motor shaft forms a flange on the outer peripheral surface of the end toward the bull gear, the bull gear is fastened to the motor shaft by a plurality of coupling bolts that penetrate the bull gear and the flange, and the gear housing is coupled to any one of the plurality of coupling bolts. An opening part can be formed in the site | part facing a volt | bolt. The motor cover includes a recess formed in a convex shape toward the motor, and a part of the high-speed rotating body can be accommodated in the recess.

  The high-speed rotating body includes i) a pair of first compound bearings disposed on both sides of the pinion gear, and ii) a rotation shaft and a pair of first compound bearings, and is assembled to the gear housing so that the pinion gear is disposed inside the gear housing. The rotating body housing may be further cut partially to expose the rotating body housing.

  Each of the first compound bearings includes i) a compound bearing block integrally including a sliding bearing block and a ball bearing block, and ii) formed on the outer peripheral surface of the rotating shaft, and is incorporated in the sliding bearing block so as to slide together with the sliding bearing block. And iii) a ball bearing built in the ball bearing block.

  The set gap of the slide bearing is larger than the set gap of the ball bearing, and the slide bearing shaft can be formed such that a plurality of oil grooves and a plurality of tapered grooves for forming an oil film are inclined on the surface thereof.

  The gear housing has an arcuate guide cover that encloses a part of the bull gear on its inner wall surface, and a stepped protrusion located outside the side surface of the bull gear, and the protrusion is inside the assembly of the gear housing and the motor cover. Temporary storage tanks can be formed.

  The guide cover can be formed with a plurality of oil guide grooves that are long connected along the rotational direction of the bull gear on the inner surface thereof. The gear housing may further include a first oil pipe that forms a first through hole at a portion where the temporary storage tank is formed, and connects the first through hole and the fixed shaft outside the gear housing.

  The fixed shaft is fastened to the gear housing, the fixed shaft forms an oil port therein, a flow path is formed between the fixed shaft and the motor shaft, and lubricating oil supplied to the oil port is supplied to the second composite bearing. I can guide you.

  The projecting portion forms a second through hole at the lower end, the gear housing forms a third through hole at a portion in contact with the rotating body housing, and connects the first through hole and the third through hole inside the gear housing. A second oil pipe may be further included.

  The rotating body housing has an oil flow path for connecting the first composite bearing on the impeller side of the pair of first composite bearings and the third through hole therein, and the pair of first composite bearings outside the pair of first composite bearings. A third oil pipe that connects the first composite bearing on the opposite side of the impeller and the oil passage may be further included.

  The high-speed rotating body further includes a support body positioned between the first compound bearing on the impeller side and the impeller. The support body and the rotating body housing form an oil discharge port, and the rotating body housing has an oil discharge port outside thereof. A fourth oil pipe may be further included for connecting the outlet and the gear housing to collect the lubricating oil.

  The turbo blower includes i) a bearing and a sealing member provided parallel to the outer peripheral surface of the motor shaft along the direction away from the bull gear, and ii) lubrication that reaches the sealing member by connecting the sealing member and the inside of the motor cover. A fifth oil pipe for collecting oil may be further included.

  A turbo blower according to another embodiment of the present invention includes: i) a motor including a motor shaft and assembled with a motor cover; ii) a hollow for detachably coupling to the motor shaft and installing a fixed shaft at the center thereof. A bull gear to be formed; iii) a rotating shaft having a pinion gear meshing with the bull gear on the outer peripheral surface; an impeller coupled to one end of the rotating shaft; at least one first composite bearing supporting the rotating shaft; 1 A high-speed rotating body including a rotating body housing that has a built-in composite bearing and is partially cut so that the pinion gear is exposed; iv) is installed between the fixed shaft and the bull gear and is adjacent in the direction parallel to the motor shaft Second compound bearing with tapered roller bearing and ball bearing, v) Built-in bull gear and pinion gear, and fastened with motor cover Gear housing forming an opening of larger diameter than the diameter of the bull gear on the side surfaces, and vi) includes a scroll portion for discharging the compressed air while surrounding the impeller.

  In accordance with the present invention, a composite bearing is employed to absorb all axial and radial loads of high speed rotating bodies and bull gears, and to provide high precision assembly using an integral composite bearing block. It can be used in a wide range of turbo blower fields.

  ADVANTAGE OF THE INVENTION According to this invention, the efficient lubricating oil provision system can be provided and the turbo blower which can be operated stably for a long term, without using an oil pump can be provided.

  According to the present invention, power can be transmitted to the bull gear without using a bull gear rotating shaft for transmitting power to the bull gear as in the prior art, and it is economical and has a long life even if a small amount of parts are used. A turbo blower can be provided.

  According to the present invention, it is possible to easily assemble and disassemble the high-speed rotating body, the bull gear, and the motor when the bull gear needs to be replaced or repaired.

1 is a front view of a turbo blower according to a first embodiment of the present invention. It is a left view of the turbo blower shown in FIG. It is the perspective view which looked at the gear housing of the turbo blower shown in FIG. 1 from the impeller side. It is the perspective view which looked at the gear housing of the turbo blower shown in FIG. 1 from the motor side. It is sectional drawing which shows the high-speed rotary body among the turbo blowers shown in FIG. It is a front view which shows the rotating shaft of the turbo blower shown in FIG. It is the schematic which shows a lubricating oil circulation system using the front sectional view and side sectional view of a gear housing among the turbo blowers shown in FIG. 1, and sectional drawing of a high-speed rotary body. It is a top view of the turbo blower concerning a 2nd embodiment of the present invention. It is sectional drawing which looked at the motor shaft and the bull gear of the turbo blower shown in FIG. 8 from the A direction. FIG. 10 is a partially enlarged view of FIG. 9. It is the elements on larger scale which show the gear housing and the part of a bull gear among the turbo blowers shown in FIG. It is the perspective view which looked at the motor cover of the turbo blower shown in FIG. 8 from the B direction. It is the perspective view which looked at the gear housing of the turbo blower shown in FIG. 8 from the C direction. It is sectional drawing along the II line | wire of FIG. It is the front view which looked at the gear housing shown in FIG. 13 from the D direction. It is the front view which looked at the turbo blower shown in FIG. 8 from the C direction. It is the right view which looked at the turbo blower of FIG. 8 from the B direction. It is a front view which shows the high-speed rotary body among the turbo blowers shown in FIG.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings so that those skilled in the art to which the present invention pertains can easily carry out the embodiments.
The present invention can be implemented in a variety of different forms and is not limited to the embodiments described herein.
FIG. 1 is a front view of a turbo blower 100 according to a first embodiment of the present invention, in which a high-speed rotating body 20 is cut away. FIG. 2 is a left side view of the turbo blower 100 shown in FIG.

  As shown in FIGS. 1 and 2, the turbo blower 100 of the first embodiment includes a support base 10, a motor 11, a gear housing 12, and a scroll portion 13. A motor 11 and a gear housing 12 are fixed on the support base 10, and a part of a high-speed rotating body 20 described later is located inside the gear housing 12.

  In the turbo blower 100 of the first embodiment, the motor shaft 14 coupled to the motor 11 and the rotating shaft 21 of the high-speed rotating body 20 are not directly connected but are eccentrically positioned. That is, the bull gear 15 is directly fastened to the motor shaft 14 and the pinion gear 16 is formed on the rotary shaft 21, and the bull gear 15 and the pinion gear 16 are engaged with each other to increase the power of the motor 11, so that the high-speed rotating body 20. Drive.

  In the first embodiment, by adopting the power transmission structure described above, the bull gear shaft that supports the bull gear in the conventional speed increasing gear box can be removed, and the motor and the gear box should be sealed. In addition to solving the problem, the number of parts can be reduced, so that the manufacturing cost can be lowered.

  Thus, in order to directly fasten the bull gear 15 to the motor shaft 14, as shown in FIGS. 3 and 4, the gear housing 12 is integrally manufactured, and one side surface of the gear housing 12 to be fastened to the motor 11 is formed. The bull gear 15 is made larger than the diameter of the bull gear 15. At the same time, the motor 11 is provided with a bracket 17 for fastening the gear housing 13.

  3 is a perspective view of the gear housing 12 of the turbo blower 100 shown in FIG. 1 seen from the impeller 22 side, and FIG. 4 is a perspective view of the gear housing 12 of the turbo blower 100 shown in FIG. 1 seen from the motor 11 side. FIG.

  A reference numeral 121 in FIG. 3 is a first coupling surface for fastening the high-speed rotating body 20 and the scroll portion 13 to the gear housing 12. Reference numeral 122 in FIG. 4 is a second coupling surface for fastening the gear housing 12 itself to the bracket 17 of the motor 11.

  As a method of fastening the high-speed rotating body 20 or the bracket 17 of the motor 11 to the first and second coupling surfaces 121 and 122 of the gear housing 12, a general mechanical coupling method such as a bolt and a nut can be used. The first and second coupling surfaces 121 and 122 are provided with a general sealing device such as a rubber pad for blocking the outside and the inside of the gear housing 12 and sealing the inside. Since this is normal, detailed description thereof will be omitted.

  By providing the gear housing 12 described above, a bull gear having a large diameter is first assembled to the motor shaft 14 during assembly, the second coupling surface 122 of the gear housing 12 is assembled to the bracket 17 of the motor 11, and then the gear housing 12 is assembled. The high-speed rotating body 20 and the scroll unit 13 can be assembled sequentially on the first coupling surface 121.

  Hereinafter, the high-speed rotating body 20 will be described in detail with reference to FIG. FIG. 5 is a cross-sectional view showing the high-speed rotating body 20 of the turbo blower 100 shown in FIG. 1, and the dotted line portion is an exploded view showing only the first composite bearing 26.

  As shown in FIG. 5, the high-speed rotating body 20 includes a rotating shaft 21, a rotating body housing 23 incorporating the rotating shaft 21, a pair of first composite bearings in which a slide bearing 24 and a ball bearing 25 are integrally formed. 26 and an impeller 22 coupled to one end of the rotating shaft 21.

  The rotating body housing 23 is formed in a cylindrical shape as a whole, and is integrally manufactured so as to be different from a divided type used in a normal high-speed rotating body. The rotating body housing 23 is partially cut at a portion where the pinion gear 16 formed on the rotating shaft 21 is located so that the pinion gear 16 is exposed to the outside of the rotating body housing 23. The pinion gear 16 thus exposed meshes with the bull gear 15 inside the gear housing 12.

  Further, a flange 27 is formed in an intermediate portion of the rotating body housing 23, and a plurality of fastening holes 271 are formed in the flange 27 so that the rotating body housing 23 is assembled on the first coupling surface 121 of the gear housing 12. To. The rotating body housing 23 forms a plurality of holes for supplying and discharging lubricating oil to a first composite bearing 26 described later. This hole will be described later.

  The first compound bearings 26 are located on both sides of the pinion gear 16 with the pinion gear 16 formed on the rotating shaft 21 as the center. The first composite bearing 26 has a configuration in which a slide bearing shaft 241 and a ball bearing 25 are both provided in one composite bearing block 28.

  As shown in the dotted line portion of FIG. 5, the first composite bearing 26 includes a composite bearing block 28, a sliding bearing shaft 241, and a ball bearing 25. The composite bearing block 28 includes a sliding bearing block 281 and a ball bearing block 282 integrally. The sliding bearing shaft 241 is formed on the outer peripheral surface of the rotating shaft 21 and is built in the sliding bearing block 281 to constitute the sliding bearing 24 together with the sliding bearing block 281. The ball bearing 25 is built in the ball bearing block 282. The ball bearing 25 includes a ball 251 that directly supports a load during low-speed operation, and an outer ring 252 and an inner ring 253 that surround the ball 251.

  5, a reference numeral 261 indicates a ring fastened between the composite bearing block 28 and the rotating body housing 23, and a reference numeral 262 indicates that the ball bearing 25 is fastened to the composite bearing block 28. The fastening ring is shown. Reference numeral 263 denotes a nut for fixing the composite bearing block 28 to the rotating shaft 21.

  The reason why the first composite bearing 26 is used for the high-speed rotating body 20 in the turbo blower 100 of the first embodiment is as follows.

  If only a sliding bearing is used for a high-speed rotating body, a high load can be supported by the hydraulic pressure formed by the high-speed rotation, but the sliding bearing block and the rotary shaft are directly connected to each other during start / stop or low-speed operation without high-speed rotation. Make contact. This not only makes starting difficult, but also generates heat and wear problems due to friction, and in order to solve this problem, it is necessary to forcibly lubricate using an oil pump.

  On the other hand, if only a ball bearing is used for a high-speed rotating body, the friction problem can be solved during starting, stopping, or low-speed operation, and only lubricating oil that is not pressurized without an oil pump is supplied. There is an advantage that it is good, but since the ball bearing is responsible for a high load during high-speed rotation, there is a disadvantage that durability is lowered.

  Therefore, the turbo blower 100 according to the first embodiment can solve all of these problems by providing the high-speed rotating body 20 with the first composite bearing 26 including the slide bearing 24 and the ball bearing 25.

  Thus, by applying the first composite bearing 26 to the high-speed rotating body 20, the rotary shaft 21 and the composite bearing block 28 are structurally prevented from being in direct contact by the ball bearing 25.

  Therefore, the turbo blower 100 can support the driving of the high-speed rotating body 20 by the ball bearing 25 during the initial low-speed driving, and can support the driving of the high-speed rotating body 20 by the sliding bearing 24 during the high-speed driving.

  Due to the structure of the first composite bearing 26 described above, when the high-speed rotating body 20 is driven, the load supporting action is automatically changed depending on the operation region (rotational speed).

  For this reason, the set gap of the slide bearing 24 is formed larger than the set gap of the ball bearing 25. Here, the setting gap of the sliding bearing 24 means a difference between the diameter of the inner surface of the sliding bearing block 281 and the diameter of the sliding bearing shaft 241, and the setting gap of the ball bearing 25 means the inner diameter of the outer ring 252 and the inner ring 253. The difference from the outer diameter means a limit value of the diameter of the ball 251.

  The difference with respect to the setting gap will be described as an example. When the setting gap of the sliding bearing 24 is 0.2 mm, the setting gap of the ball bearing 25 may be 0.1 mm.

  The principle that the load supporting action is automatically changed by the operating range (rotational speed) in the first composite bearing 26 when the high-speed rotating body 20 is driven is disclosed in Korean Patent Registration No. 10-0723040 of the present applicant. Since it is the same as that of the bearing assembly, its detailed description is omitted.

  On the other hand, in the first embodiment, the sliding bearing 24 of the first composite bearing 26 can form an oil film without installing a separate oil pump. Hereinafter, the advantages will be described with reference to FIG.

  FIG. 6 is a front view showing the rotating shaft 21 of the turbo blower 100 shown in FIG. 1, and shows both a left side view and a right side view of the rotating shaft 21.

  Referring to FIG. 6, a plurality of oil grooves 242 and a plurality of taper grooves 243 for supplying oil are formed on the surface of the sliding bearing shaft 241 formed on the rotary shaft 21. The oil groove 242 and the taper groove 243 are formed so as to be inclined in the direction of the rotating shaft 21. The inclination direction of the oil groove 242 and the taper groove 243 located on one side of the pinion gear 16 is opposite to the inclination direction of the oil groove 242 and the taper groove 243 located on the other side of the pinion gear 16. Further, each tapered groove 243 is formed so that a portion in contact with the oil groove 242 is deep and the depth decreases in a direction away from the oil groove 242.

  Thus, the oil groove 242 formed on the surface of the sliding bearing shaft 241 plays a role of supplying oil, and the taper groove 243 generates a pressure to the oil supplied to the oil groove 242 to form an oil film. Fulfill. Therefore, the oil groove 242 and the taper groove 243 serve as an oil pump when the rotary shaft 21 rotates.

  That is, when the rotating shaft 21 is rotated at a high speed, a wedge effect is induced in the rotating direction, and a part of oil forms a high pressure on the sliding bearing 24 by centrifugal force. As a result, the rotating shaft 21 is separated from the sliding bearing block 281 while floating, and the rotating shaft 21 can rotate at high speed while floating. If the rotating shaft 21 rotates at a high speed in this state, the ball bearing 25 does not play a role as a bearing (that is, does not come into contact with the rotating shaft 21). Can be extended.

  Therefore, if only the lubricating oil is supplied to the first composite bearing 26, the turbo blower 100 can solve all the problems of friction due to high-speed rotation and pressurization of the lubricating oil without installing an oil pump.

  On the other hand, the turbo blower 100 has a structure in which the rotational speed of the rotary shaft 21 is increased by the bull gear 15 and the pinion gear 16, so that a side pressure is inevitably generated due to gear driving. Such a side pressure is normally applied from the bull gear 15 having a large diameter to the pinion gear 16 having a small diameter, and the substantial direction in which the side pressure acts is a direction perpendicular to the vertical line at the center of the rotating shaft 21 3 It acts in the direction of about 5 o'clock below it, not in the hour direction.

  Therefore, a means for buffering the side pressure acting on the pinion gear 16 of the rotating shaft 21 must be applied. For this purpose, a side pressure buffering groove 29 (see the dotted line in FIG. 5) is formed on the inner surface of the sliding bearing block 281. The side pressure buffering groove 29 is formed in a portion of the inner surface of the sliding bearing block 281 toward the bull gear 15 (a direction opposite to the direction in which the side pressure is exerted). The length and depth of the side pressure buffering groove 29 are determined by load calculation according to the specifications of the high-speed rotating body 20. The side pressure buffering groove 29 can be formed in an arc shape of 180 ° or less.

  An oil film is not formed in a portion of the composite bearing block 28 where the side pressure buffering groove 29 is formed, and an oil film is formed only on the opposite side, that is, the side on which the side pressure is exerted. Therefore, the side pressure caused by the bull gear 15 is eliminated and smooth high-speed rotation is possible.

  The method for eliminating the radial load of the high-speed rotating body 20 has been described above. However, when the high-speed rotating body 20 rotates at high speed, an axial load is applied to the high-speed rotating body 20 due to the difference in pressure acting on the inlet of the impeller 22 and the outlet of the impeller 22. Therefore, a method for eliminating the axial load exerted on the high-speed rotating body 20 will be described below.

  An impeller 22 is provided on one side (left side with reference to FIG. 5) of the rotating shaft 21 in the high-speed rotating body 20.

  In this case, a negative pressure (−) is formed at the inlet of the impeller 22, and a positive pressure (+) is formed at the outlet of the impeller 22. Therefore, an axial load is generated in the direction (left side in FIG. 5) in which the impeller 22 is provided with the rotating shaft 21 as a reference.

  In order to eliminate the axial load, in the first embodiment, i) a vent hole 231 is formed at the end of the rotating body housing 23 toward the impeller 22, and ii) a helical gear of the pinion gear 16 formed on the rotating shaft 21. Iii) The ball bearing 25 is provided on the composite bearing block 28.

  The positive pressure (+) formed behind the impeller 22 is removed by the vent hole 231 of the rotor housing 23. The pinion gear 16 is formed in the shape of a helical gear. The direction of the helical gear is set so as to generate a force that pulls the rotating shaft 21 in the direction opposite to the direction of the impeller 22 (the right side in FIG. 5) when the rotating shaft 21 rotates, thereby eliminating the axial load. When necessary, the axial load is relaxed by the supporting force of the basic axial load of the ball bearing 25.

  Next, the lubricating oil circulation system of the turbo blower 100 will be described with reference to FIG. The lubricating oil circulation system plays a role of circulating and supplying lubricating oil to the high-speed rotating body 20 without using an oil pump.

  FIG. 7 is a schematic view showing a lubricating oil circulation system using a front sectional view and a side sectional view of the gear housing 12 of the turbo blower 100 shown in FIG. 1 and a sectional view of the high-speed rotating body 20.

  Referring to FIG. 7, a guide cover 30 surrounding the bull gear 15 is formed on the inner wall surface of the gear housing 12. A plurality of oil guide grooves 301 are formed in the guide cover 30. In addition, an oil box 31 connected to an end portion of the guide cover 30 is formed on the inner upper portion of the gear housing 12.

  Therefore, if the bull gear 15 rotates, the lubricating oil in the oil storage tank 32 at the lower part of the gear housing 12 moves along the guide cover 30 and the oil guide groove 301 while being scattered by the gear teeth of the bull gear 15, and due to gravity. It falls into the oil box 31 and is collected in the oil box 31. At this time, the lubricating oil remaining on the surface of the bull gear 15 acts to lubricate the bull gear 15 and the pinion gear 16 at the moment when the bull gear 15 and the pinion gear 16 come into contact with each other.

  Part of the lubricating oil collected in the oil box 31 is discharged to the oil discharge port 311 by gravity, and is supplied to the oil supply port 232 formed in the rotating body housing 23 of the high-speed rotating body 20 along the oil pipe. The

  Lubricating oil supplied to the oil supply port 232 of the rotating body housing 23 is divided into two directions, a small amount is supplied to the ball bearing 25, and most is supplied to the sliding bearing 24. When the rotating shaft 21 rotates at a high speed, the lubricating oil supplied to the sliding bearing 24 forms a pressurized oil film by the tapered groove 243 formed on the sliding bearing shaft 241 and supports the rotating shaft 21. The lubricating oil used for the sliding bearing 24 moves in a direction opposite to the supplied direction, and is discharged to an incision portion of the rotating body housing 23 for exposing the pinion gear 16, so that an oil storage tank below the gear housing 12. Falls to 32.

  On the other hand, if the high-speed rotating body 20 rotates at a high speed, the lubricating oil supplied to the first composite bearing 26 can generate oil vapor while evaporating.

  The oil vapor is discharged to the inside of the gear housing 12 and the outside of the gear housing 12 around the flange 27 of the rotating body housing 23. The oil vapor discharged to the inside of the gear housing 12 is further supplied to the first composite bearing 26 by the lubricating oil circulation structure, so there is no particular problem. However, the oil vapor discharged to the outside of the gear housing 12 is not used. Subsequent processing is required.

  Part of the oil vapor discharged from the inside of the first composite bearing 26 toward the impeller 22 to the outside of the gear housing 12 condenses, and the remaining part maintains the vapor state. The condensed lubricating oil is recovered to the oil recovery port 33 of the oil storage tank 32 through the recovery port 233. The vapor-state oil vapor is discharged through the vapor discharge port 234, condensed in the oil vapor cooler 34, and re-supplied to the oil box 31 through the condensed oil supply port 35 of the oil box 31.

  The lubricating oil supplied to the oil box 31 through the condensed oil supply port 35 in this manner is collected in the oil storage tank 32 through the oil pipe 36, and a small amount of oil vapor remaining in the oil box 31 is discharged from the exhaust port 37 of the oil box 31. It is discharged to the outside through. Here, the oil box 31 is provided with a partition wall 38 having an upper portion opened and a through hole formed therein. Therefore, the oil box 31 roughly separates the lubricating oil collected by the guide cover 30 and the oil guide groove 301 and the condensed lubricating oil supplied from the oil vapor cooler 34, and temporarily stores them. Can do.

  On the other hand, lubricating oil is stored in an oil storage tank 32 formed by sealing the gear housing 12, and holes are formed in the upper and lower sides of the side wall of the oil storage tank 32. And the control valve 39 is provided in the communicating pipe which connected this hole. Therefore, the control valve 39 can be adjusted to maintain an appropriate amount of lubricating oil necessary for driving the high-speed rotating body 20 in the oil storage tank 32.

  More specifically, when the high-speed rotating body 20 is driven for the first time, a large amount of lubricating oil is necessary in consideration of the scattering of the lubricating oil. If the control valve 39 is closed, the lubricating of the oil storage tank 32 is performed. Oil is depleted. Therefore, if the amount of lubricating oil supplied to the control valve 39 is appropriately controlled, the amount of lubricating oil required for driving the high-speed rotating body 20 can be maintained.

  Reference numeral 40 in FIG. 7 denotes a pressure adjusting valve for adjusting the pressure difference between the front and rear of the impeller 22 in communication with the vent hole 231.

  FIG. 8 is a partially cutaway plan view of a turbo blower 110 according to the second embodiment of the present invention. The same members as those in the first embodiment will be described with the same reference numerals.

  Referring to FIG. 8, the turbo blower 110 of the second embodiment includes a motor shaft 14, a bull gear 15, a high-speed rotating body 20, and a second composite bearing 42.

  The motor shaft 14 is coupled to the motor 11 and rotates at a high speed when the motor 11 is operated. The bull gear 15 is detachably coupled to the motor shaft 14 and forms a hollow where the fixed shaft 41 and the second composite bearing 42 are located at the center. The high-speed rotating body 20 includes a rotating shaft 21 formed with a pinion gear 16 that meshes with the bull gear 15, and an impeller 22 coupled to one end of the rotating shaft 21.

  The turbo blower 110 further includes a motor cover 43, a gear housing 120, an inlet guide vane 44, and a scroll part 13. The motor cover 43 is fastened in front of the motor 11 toward the impeller 22, and the gear housing 120 is fastened in front of the motor cover 43 toward the impeller 22. Inside the assembly of the motor cover 43 and the gear housing 120, the motor shaft 14 and the entire bull gear 15 and a part of the high-speed rotating body 20 are located. The inlet guide vane 44 is installed in the suction flow path and adjusts the flow rate of the gas flowing into the impeller 22.

  When the motor shaft 14 is rotated by the operation of the motor 11, the power of the motor 11 is increased while the bull gear 15 and the pinion gear 16 are rotated, and the high-speed rotating body 20 is driven. Accordingly, the external gas flows into the rotating impeller 22 through the suction flow path, is accelerated and compressed while passing through the impeller 22, and the compressed gas is discharged to the scroll unit 13 through the diffuser passage. In FIG. 8, the inflow direction and the discharge direction of the gas are indicated by arrows.

  During the operation of the turbo blower 110 described above, a radial load is generated on the bull gear 15 due to the load of the bull gear 15 itself and the force with which the pinion gear 16 presses the bull gear 15. Also occurs. The second composite bearing 42 described below supports the bull gear 15 inside the dollar gear 15, thereby effectively reducing the radial load and the axial load acting on the bull gear 15.

  9 is a cross-sectional view of the motor shaft 14 and the bull gear 15 in the turbo blower 110 shown in FIG. 8 as viewed from the direction A, and FIG. 10 is a partially enlarged view of FIG.

  Referring to FIGS. 9 and 10, the second composite bearing 42 includes a tapered roller bearing 45 and a ball bearing 46 provided along a direction parallel to the motor shaft 14 between the fixed shaft 41 and the bull gear 15. The tapered roller bearing 45 includes a roller 451 fitted in an inclined direction, and an inner ring 452 and an outer ring 453 that surround the roller 451. The ball bearing 46 includes a ball 461 and an inner ring 462 and an outer ring 463 that surround the ball 461. The inner ring 462 is fitted to the fixed shaft 41, and the outer ring 463 is coupled to the bull gear 15.

  The taper roller bearing 45 simultaneously reduces the radial load and the axial load acting on the bull gear 15, and the ball bearing 46 once again reduces the radial load acting on the bull gear 15. Therefore, the turbo blower 110 of the second embodiment minimizes the radial load and the axial load acting on the bull gear 15 through the second composite bearing 42. As a result, it is possible to prevent the generation of noise due to the movement of the position of the bull gear 15, breakage of the bull gear 15, and deformation of the motor shaft 14.

  The fixed shaft 41 is fastened to the gear housing 120 using the fixed block 47 and the bolt 48 and is positioned so that the center thereof coincides with the center of the motor shaft 14. An oil port 411 for supplying lubricating oil to the second composite bearing 42 is formed inside the fixed shaft 41 along a direction parallel to the fixed shaft 41. At this time, a predetermined interval exists between the fixed shaft 41 and the motor shaft 14 to form a flow path for guiding the lubricating oil to the second composite bearing 42.

  On the other hand, the motor shaft 14 does not overlap the bull gear 15, and a flange 141 is fixed to the outer peripheral surface of the end of the motor shaft 14 facing the bull gear 15. The bull gear 15 can be fastened to the motor shaft 14 by a mechanical coupling method using a plurality of coupling bolts 49 penetrating the bull gear 15 and the flange 141. In this case, the bull gear 15 is coupled to the motor shaft 14 in a detachable manner that is not permanent coupling such as shrink fitting. Therefore, when the bull gear 15 needs to be replaced or repaired, the bull gear 15 and the motor shaft 14 are connected. Can be easily assembled and disassembled.

FIG. 11 is a partially enlarged view showing the gear housing 120 and the bull gear 15 portion of the turbo blower 110 shown in FIG.
Referring to FIG. 11, the gear housing 120 forms an opening 123 at a portion facing any one of the plurality of coupling bolts 49. A tool (not shown) can be inserted through the opening 123 to separate the coupling bolt 49. That is, after separating the coupling bolt 49 using a tool, the bull gear 15 is manually turned to place another coupling bolt 49 at the position of the opening 123, and then a tool is further inserted to separate the coupling bolt 49. . By repeating such a process, all of the plurality of coupling bolts 49 can be separated.

  The bull gear 15 from which all the coupling bolts 49 are removed is supported by the second composite bearing 42. If the gear housing 120 and the motor cover 43 are separated in this state, the motor 11 and the motor shaft 14 are connected to the bull gear 15 and the gear housing. 120 can be easily disassembled.

Since the configurations and functions of the high-speed rotating body 20 and the first composite bearing 26 in the turbo blower 110 of the second embodiment are the same as those of the first embodiment described above, detailed description thereof is omitted.
Next, the shapes of the motor cover 43 and the gear housing 120 will be described.
FIG. 12 is a perspective view of the motor cover 43 of the turbo blower 110 shown in FIG. 8 as viewed from the B direction.
Referring to FIGS. 8 and 12, the motor cover 43 forms a hollow 431 that houses the motor shaft 14, and forms a third coupling surface 432 that is fastened to the motor 11 along the periphery of the hollow 431. Further, the motor cover 43 is provided with a recess 50 formed in a convex shape toward the motor 11, and the internal space of the assembly of the motor cover 43 and the gear housing 120 is enlarged toward the motor 11 side.

  As the capacity of the turbo blower 110 increases, the length of the rotating shaft 21 increases, so that a space for accommodating the rotating shaft 21 is required. In the turbo blower 110 of the second embodiment, by forming the recess 50 in the motor cover 43, the portion of the high speed rotating body 20 opposite to the impeller 22 can be accommodated in the recess 50, so that the large high speed rotating body 20 is also easy. Can be installed.

13 is a perspective view of the gear housing 120 of the turbo blower 110 shown in FIG. 8 as viewed from the C direction, and FIG. 14 is a cross-sectional view taken along the line II of FIG.
Referring to FIGS. 13 and 14, the gear housing 120 is configured in such a manner that the side fastened to the motor cover 43 is opened larger than the diameter of the bull gear 15. That is, the gear housing 120 includes a vertical wall 51 that forms two hollows for accommodating the fixed shaft 41 of the bull gear 15 and the high-speed rotating body 20, and a side wall that extends from the periphery of the vertical wall 51 toward the motor cover 43. 52, and the side that is fastened to the motor cover 43 is open.

  Therefore, as shown in FIG. 8, after the bull gear 15 and the motor shaft 41 are assembled and the gear housing 120 is fastened to the motor cover 43 so as to surround the bull gear 15, the fixed shaft 41 and the high-speed rotating body 20 are mounted on the gear housing 120. Are assembled, and the scroll portion 13 is sequentially assembled to the rotating body housing 23. Disassembly is performed in the opposite order of the assembly sequence described above. The turbo blower 110 can be easily assembled and disassembled by the detachable coupling structure of the bull gear 15 and the motor shaft 14 and the shape of the gear housing 120 with one side greatly opened.

Next, the lubricating oil circulation system of the turbo blower 110 according to the second embodiment will be described.
FIG. 15 is a front view of the gear housing 120 shown in FIG. 13 as viewed from the D direction.
Referring to FIGS. 14 and 15, a substantially arc-shaped guide cover 30 surrounding a part of the bull gear 15 is formed on the inner surface of the vertical wall 51 of the gear housing 120. The guide cover 30 protrudes from the inner surface of the vertical wall 51 toward the motor cover 43, and its width (see w1, FIG. 14) matches the width of the side wall 52 of the gear housing 120 (see w2, FIG. 14). . The guide cover 30 is formed to have an inner diameter larger than the diameter of the bull gear 15 and is located at a distance from the bull gear 15.

  In FIG. 15, the rotation direction of the bull gear 15 is counterclockwise, and the guide cover 30 has a shape in which a quarter-quarter plane is incised with reference to FIG. 15. An oil guide groove 301 is formed on the inner surface of the guide cover 30 along the rotational direction of the bull gear 15. A plurality of such oil guide grooves 301 are provided at a distance from each other along a direction parallel to the motor shaft 14 (see FIG. 14).

  Then, a stepped protrusion 53 is formed on the upper surface of the vertical wall 51 of the gear housing 120, that is, on the outer side surface of the bull gear 15. The protrusion 53 forms a step that decreases toward the side wall 52. One end of the protrusion 53 is connected to the side wall 52, and the other end is located at a distance from the upper end of the guide cover 30 along the horizontal and vertical directions with reference to FIG. The width of the protrusion 53 is the same as the width of the guide cover 30.

  When the gear housing 120 described above is fastened to the motor cover 43, a predetermined internal space is formed while the side wall 52, the guide cover 30 and the protrusion 53 are in close contact with the motor cover 43. That is, an oil storage tank 32 is formed in the lower part of the assembly of the gear housing 120 and the motor cover 43, an oil passage is formed between the bull gear 15 and the guide cover 30, and the lubricating oil is collected on the protrusion 53. Thus, a temporary storage tank 54 for further circulating the collected lubricating oil is formed.

  Therefore, when the bull gear 15 rotates, the lubricating oil in the oil storage tank 32 travels along the oil guide groove 301 formed in the guide cover 30 while being scattered by the gear teeth of the bull gear 15, but the protruding portion 53 is caused by gravity. It is collected on the temporary storage tank 54. The lubricating oil collected in the temporary storage tank 54 is supplied to the second composite bearing 42 of the bull gear 15 and the first composite bearing 26 of the high-speed rotating body 20 by the circulation structure described below.

  In the structure of the gear housing 120 described above, the guide cover 30 and the protrusion 53 are formed integrally with the gear housing 120. Therefore, after manufacturing a separate oil storage tank and a temporary storage tank, it is possible to avoid the hassle of assembling the oil storage tank and the temporary storage tank inside the gear housing. By fastening the gear housing 120 and the motor cover 43 in an airtight state, the oil storage tank The tank 32 and the temporary storage tank 54 can be easily formed.

FIG. 16 is a front view of the turbo blower 100 shown in FIG. 8 as viewed from the C direction, and a part of the outer surface of the gear housing 120 is shown inside the dotted line.
Referring to FIGS. 15 and 16, a first oil pipe 55 that connects the temporary storage tank 54 and the fixed shaft 41 of the bull gear 15 is provided outside the vertical wall 51 of the gear housing 120. That is, the first through hole 56 is formed in the vertical wall 51 of the gear housing 120 at a position corresponding to the temporary storage tank 54, and one end of the first oil pipe 55 is connected to the first through hole 56. The other end of the first oil pipe 55 is connected to an oil port 411 formed in the fixed shaft 41.

  In FIG. 9, a part of the first oil pipe 55 connected to the fixed shaft 41 is indicated by a dotted line. Referring to FIG. 9, the first oil pipe 55 provides the lubricating oil collected in the temporary storage tank 54 to the oil port 411 of the fixed shaft 41, and the lubricating oil provided to the oil port 411 is tapered with the ball bearing 46. The second composite bearing 42 is lubricated through the roller bearings 45 sequentially. Thereafter, the lubricating oil further falls into the oil storage tank 32 and is collected in the oil storage tank 32.

  FIG. 17 is a right side view of the turbo blower 110 of FIG. 8 as viewed from the direction B. A part of the motor cover 43 is cut away to show the inside of the gear housing 120. FIG. 18 is a front view showing the high-speed rotor 20 of the turbo blower 110 shown in FIG.

  Referring to FIGS. 17 and 18, a second oil pipe 57 for transmitting the lubricating oil collected in the temporary storage tank 54 to the high speed rotating body 20 is provided in the vertical wall 51 of the gear housing 120. For this purpose, a second through hole 58 is formed at the lower end of the protrusion 53, and one end of the second oil pipe 57 is connected to the second through hole 58. A third through hole 59 is formed in the vertical wall 51 of the gear housing 120 that overlaps the rotating body housing 23, and the other end of the second oil pipe 57 is connected to the third through hole 59.

  In the rotating body housing 23, the first composite bearing 26 on the impeller 22 side of the pair of first composite bearings 26 (the first composite bearing 26 on the left side with reference to FIG. 18) and the third through hole 59. Are formed. A third oil pipe 61 that connects the first composite bearing 26 on the opposite side of the impeller 22 (the first composite bearing 26 on the right side with reference to FIG. 18) and the oil passage 60 is provided outside the rotating body housing 23. Provided.

  Therefore, the lubricating oil collected in the temporary storage tank 54 is provided to the high-speed rotating body 20 through the second oil pipe 57, and the supplied lubricating oil passes through the oil passage 60 and the third oil pipe 61 on the impeller 22 side. The first composite bearing 26 and the first composite bearing 26 opposite to the impeller 22 are supplied separately.

  The lubricating oil provided to the first composite bearing 26 on the impeller 22 side passes through the sliding bearing 24 and the ball bearing 25 in order to lubricate these bearings. At this time, the lubrication port 63 is formed in the support body 62 located between the ball bearing 25 and the impeller 22 and the rotating body housing 23 surrounding the support body 62, and the fourth oil pipe 64 is lubricated outside the rotating body housing 23. It is provided so as to connect the port 63 and the gear housing 120. Accordingly, the used lubricating oil flows into the gear housing 120 through the fourth oil pipe 64 and is collected in the oil storage tank 32.

  Further, the lubricating oil provided to the first composite bearing 26 on the opposite side of the impeller 22 through the third oil pipe 61 is supplied to the sliding bearing 24 and the ball bearing 25 to lubricate these bearings, and used lubricating oil. Falls through the incision formed in the rotor housing 23 to expose the pinion gear 16 and is collected in the oil storage tank 32.

  Further, referring to FIG. 9, a bearing 65 and a sealing member 66 are provided in parallel on the outer peripheral surface of the motor shaft 14 along a direction away from the bull gear 15. As the bull gear 15 rotates, the lubricating oil scatters at a high speed toward the motor shaft 14, so that the bearing 65 can be sufficiently lubricated using the scattered lubricating oil. A fifth oil pipe 67 is installed in the sealing member 66, and the lubricating oil that has passed through the bearing 65 and reaches the sealing member 66 is collected in the oil storage tank 32.

  As described above, the turbo blower 110 according to the second embodiment can be connected to the second composite bearing 42 of the bull gear 15 and the first composite bearing 26 of the high-speed rotating body 20 without installing a separate oil pump for supplying lubricating oil. Lubricating oil can be circulated and supplied. Therefore, it is possible to simplify the lubricating oil supply structure and reduce the number of parts.

  The preferred embodiments of the present invention have been described above. However, the present invention is not limited thereto, and various modifications can be made within the scope of the claims, the detailed description of the invention, and the attached drawings. Of course, this is also within the scope of the present invention.

    DESCRIPTION OF SYMBOLS 10 ... Support stand, 11 ... Motor, 12 ... Gear housing, 13 ... Scroll part, 14 ... Motor shaft, 15 ... Bull gear, 20 ... High speed rotating body, 22 ... Impeller, 24 ... Sliding bearing, 25 ... Ball bearing, 32 ... Oil storage tank 26, 42 ... 1st and 2nd compound bearing, 41 ... fixed shaft, 47 ... fixed block, 48 ... bolt, 60 ... oil flow path, 55, 57, 61, 64, 67 ... 1st, 2nd, 3, 4, 5 oil pipe, 65 ... bearing, 66 ... sealing member, 100, 110 ... turbo blower.

Claims (30)

Motor with motor shaft;
A gear housing containing a bull gear fastened to the motor shaft and a pinion gear meshing with the bull gear;
A rotary shaft having the pinion gear formed on the outer peripheral surface, an impeller coupled to one end of the rotary shaft, the rotary shaft, the pinion gear, and at least one first compound bearing are incorporated so that the pinion gear is exposed. A high-speed rotating body including a rotating body housing partly cut into the gear housing, and a part of which is built in and coupled to the gear housing; and a turbo blower that discharges compressed air while surrounding the impeller. The first composite bearing is:
Composite bearing block with integrated sliding bearing block and ball bearing block;
2. A slide bearing shaft formed on an outer peripheral surface of the rotating shaft and built in the slide bearing block to form a slide bearing together with the slide bearing block; and a ball bearing built in the ball bearing block. The turbo blower according to claim 1.   The turbo blower according to claim 2, wherein the first compound bearing is located on both sides of the pinion gear, and a set gap of the sliding bearing is larger than a set gap of the ball bearing.   The sliding bearing shaft is formed such that a plurality of oil grooves and a plurality of tapered grooves for forming an oil film are inclined on a surface thereof, and the sliding bearing block has a side pressure buffering portion at a portion of its inner surface facing the bull gear. The turbo blower of Claim 3 which forms a groove | channel and absorbs the side pressure by the said bull gear.   The high-speed rotating body forms a vent hole at the end of the rotating body housing toward the impeller, the pinion gear is formed in a helical gear shape, and the direction of the helical gear is such that the rotating shaft rotates when the rotating shaft rotates. The turbo blower according to claim 4, wherein the turbo blower is set so as to generate a force pulled in a direction opposite to the impeller direction.   The gear housing forms an arcuate guide cover having a plurality of oil guide grooves while enclosing a part of the bull gear on an inner wall surface thereof, and an oil box connected to an end of the guide cover at an inner upper portion The turbo blower as described in any one of Claims 1-5 which forms.   The gear housing has an oil pipe formed therein, and supplies the lubricating oil collected in the oil box to the first composite bearing, and one end of the oil pipe has an oil discharge port formed in the oil box. The turbo blower according to claim 6, wherein the other end of the oil pipe is connected to an oil supply port formed in the first composite bearing.   The rotating body housing forms a steam discharge port for discharging oil vapor, the turbo blower further includes an oil vapor cooler connected to the steam discharge port and the oil box, and the oil vapor cooler is connected to the steam blower. The turbo blower according to claim 7, wherein the oil vapor discharged to the discharge port is condensed and supplied to the oil box.   The gear housing has an oil storage tank formed in a lower portion thereof, the oil storage tank has a pair of upper and lower holes formed in a side wall thereof, and the gear housing has a communication pipe that communicates the pair of holes, The turbo blower according to claim 8, further comprising a control valve provided in.   The bull gear is directly fastened to the motor shaft, and the gear housing forms a coupling surface having an opening larger than a diameter of the bull gear on a side surface facing the motor, and the coupling surface is coupled to the motor. The turbo blower according to 6.   The bull gear is directly fastened to the motor shaft, and the gear housing forms a coupling surface having an opening larger than a diameter of the bull gear on a side surface facing the motor, and the coupling surface is coupled to the motor. The turbo blower as described in any one of 7-9. A rotating shaft having a pinion gear meshing with the bull gear formed on the outer peripheral surface;
An impeller coupled to one end of the rotating shaft;
A pair of first compound bearings provided on both sides of the pinion gear; and a rotating body housing that incorporates the rotating shaft, the pinion gear, and the pair of first compound bearings, and is partially incised so that the pinion gear is exposed High-speed rotating body including Each of the pair of first composite bearings is
Composite bearing block with integrated sliding bearing block and ball bearing block;
A sliding bearing shaft formed on an outer peripheral surface of the rotating shaft and built in the sliding bearing block to form a sliding bearing together with the sliding bearing block; and a ball bearing built in the ball bearing block. The high-speed rotating body described in 1.   A set gap of the slide bearing is larger than a set gap of the ball bearing, and the slide bearing shaft is formed such that a plurality of oil grooves and a plurality of tapered grooves for forming an oil film are inclined on a surface thereof, and the slide bearing is provided. The high speed rotating body according to claim 13, wherein the block forms a side pressure buffering groove in an opposite direction to a direction exerted by the side pressure in order to absorb a side pressure caused by the bull gear on the inner surface of the block. Motor with motor shaft;
A bull gear which is detachably coupled to the motor shaft and forms a hollow for installing a fixed shaft at the center thereof;
A second compound bearing provided between the fixed shaft and the bull gear and having a tapered roller bearing and a ball bearing adjacent to each other along a direction parallel to the motor shaft; and a pinion gear meshing with the bull gear is formed on an outer peripheral surface. A turbo blower including a high-speed rotating body that includes a rotating shaft and an impeller coupled to one end of the rotating shaft. The turbo blower is
A motor cover that is fastened to the motor and supports the motor shaft; and a gear housing that includes the bull gear and the pinion gear, and that has an opening having a diameter larger than the diameter of the bull gear on a side surface that is fastened to the motor cover. The turbo blower according to claim 15, further comprising:   The motor shaft has a flange formed on an outer peripheral surface of an end portion facing the bull gear, the bull gear is fastened to the motor shaft by a plurality of coupling bolts penetrating the bull gear and the flange, and the gear housing is coupled to the plurality of coupling bolts. The turbo blower according to claim 16, wherein an opening is formed at a portion facing any one of the coupling bolts.   The turbo blower according to claim 16, wherein the motor cover includes a recess formed in a convex shape toward the motor, and a part of the high-speed rotating body is accommodated in the recess. The high-speed rotating body is
A pair of first compound bearings disposed on both sides of the pinion gear; and the rotating shaft and the pair of first compound bearings are built in and assembled to the gear housing to expose the pinion gear inside the gear housing The turbo blower according to any one of claims 16 to 18, further comprising a rotor housing partly cut for the purpose. Each of the first compound bearings
Composite bearing block with integrated sliding bearing block and ball bearing block;
A slide bearing shaft formed on an outer peripheral surface of the rotating shaft and built in the slide bearing block to form a slide bearing together with the slide bearing block; and a ball bearing built in the ball bearing block. Turbo blower described in.   21. The set gap of the slide bearing is larger than the set gap of the ball bearing, and the slide bearing shaft is formed such that a plurality of oil grooves and a plurality of tapered grooves for forming an oil film are inclined on a surface thereof. Turbo blower described in.   The gear housing has an arcuate guide cover that surrounds a part of the bull gear on an inner wall surface thereof, and a step-like protrusion that is located on the outer side of the bull gear, and the protrusion includes the gear housing and the motor. The turbo blower according to claim 19, wherein a temporary storage tank is formed inside the cover assembly.   23. The turbo blower according to claim 22, wherein the guide cover has a plurality of oil guide grooves that are connected to each other along the rotation direction of the bull gear on the inner surface thereof.   The gear housing further includes a first oil pipe that forms a first through hole in a portion where the temporary storage tank is formed, and connects the first through hole and the fixed shaft outside the gear housing. The turbo blower according to claim 22.   The fixed shaft is fastened to the gear housing, the fixed shaft forms an oil port therein, a flow path is formed between the fixed shaft and the motor shaft, and lubrication supplied to the oil port The turbo blower according to claim 24, wherein oil is guided to the second composite bearing.   The projecting portion forms a second through hole at a lower end thereof, the gear housing forms a third through hole at a portion in contact with the rotating body housing, and the first through hole and the first inside the gear housing. The turbo blower according to claim 22, further comprising a second oil pipe connecting the three through holes.   The rotating body housing includes an oil passage that connects the impeller-side first composite bearing of the pair of first composite bearings and the third through-hole, and the pair of first composite bearings outside the pair of the pair of first composite bearings. 27. The turbo blower according to claim 26, further comprising a third oil pipe that connects the first composite bearing of the first composite bearing opposite to the impeller and the oil passage.   The high-speed rotating body further includes a support body positioned between the impeller-side first composite bearing and the impeller, wherein the support body and the rotating body housing form an oil discharge port, 28. The turbo blower according to claim 27, further comprising a fourth oil pipe that connects the oil discharge port and the gear housing outside to recover the lubricating oil. The turbo blower is
A bearing and a sealing member provided in parallel to the outer peripheral surface of the motor shaft along a direction away from the bull gear;
26. The turbo blower according to claim 25, further comprising a fifth oil pipe that connects the sealing member and the inside of the motor cover and collects the lubricating oil that has reached the sealing member. Motor with motor shaft and assembled with motor cover;
A bull gear which is detachably coupled to the motor shaft and forms a hollow for installing a fixed shaft at the center thereof;
A rotating shaft having a pinion gear meshing with the bull gear on an outer peripheral surface, an impeller coupled to one end of the rotating shaft, at least one first composite bearing supporting the rotating shaft, the rotating shaft and the first A high-speed rotary body including a rotary bearing housing that incorporates a composite bearing and is partially cut so that the pinion gear is exposed;
A second composite bearing provided between the fixed shaft and the bull gear and having a tapered roller bearing and a ball bearing adjacent to each other along a direction parallel to the motor shaft;
A gear housing that incorporates the bull gear and the pinion gear and that has an opening having a diameter larger than the diameter of the bull gear on a side surface that is fastened to the motor cover; and a scroll portion that discharges compressed air while surrounding the impeller. Including turbo blower.

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