KR101162708B1 - High speed motor for vertical type turbo blower - Google Patents

Abstract

The present invention provides a vertical turbo blower configured to cool the inside of a high speed motor while effectively supporting a load generated during driving and a high speed motor used therein. The high speed motor of the present invention includes: (i) a stator having a hollow core and a plurality of slots, a coil wound around the slot, and receiving a current to generate a magnetic force, and ii) an air gap between the stator's hollows. It includes a rotor that is rotatably installed and rotated by a magnetic force, and iii) a motor housing that surrounds the stator with a gas passage communicating with the outside air, and is in close contact with both ends of the iron core to support the stator.

Description

High speed motor for vertical turbo blower {HIGH SPEED MOTOR FOR VERTICAL TYPE TURBO BLOWER}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vertical turbo blower, and more particularly, to a vertical turbo blower configured to cool the inside of a high speed motor while effectively supporting a load generated during driving and a high speed motor used therein.

A turbo blower is a mechanical device that rotates an impeller by using a rotational force of a high speed motor, and accelerates and compresses air by blowing the impeller. Conventional turbo blowers are manufactured in such a way that the rotating shaft of the impeller is directly coupled to the rotor of the high speed motor. And it is made of a structure for supporting the rotating shaft by installing a bearing such as a ball bearing or an air bearing on both ends of the rotating shaft arranged horizontally.

In such a turbo blower, a load is generated in the axial direction of the rotary shaft by the pressure difference between the impeller inlet and the impeller outlet, and a load is also generated by the weight of the impeller and the rotary shaft. However, since the load due to the weight is generated in the radial direction of the rotating shaft, the bearing can support the load only in the lower region of the rotating shaft relative to the rotating shaft.

Therefore, in the conventional turbo blower, the load supporting action by the bearing is not effectively performed and driving stability is lowered. And as the rotation axis becomes longer, bending due to load may occur, which may cause a failure.

Meanwhile, the high speed motor used in the turbo blower may be a permanent magnet embedded high speed motor. These high speed motors generate a lot of heat in the stator and the rotor when driven, so it is necessary to remove this heat quickly to increase efficiency. To this end, conventionally, cooling means are provided, such as mounting a separate motor for driving the cooling fan. However, in this case, the overall structure is complicated, cooling efficiency is not high compared to the power consumption, driving noise is increased, there is a demand for a technique for improving this.

The present invention effectively supports the load due to the axial load and the weight generated during driving in the entire region of the rotating body, and is configured so that bearings of different characteristics are selectively loaded according to the driving region (rotation speed) to improve driving stability. It is intended to provide an increased vertical turbo blower.

An object of the present invention is to provide a vertical turbo blower capable of efficiently cooling the inside of a high speed motor by forming a space in which a cooled lubricating fluid flows inside the high speed motor and the rotating shaft. In addition, the present invention is to provide a high-speed motor that can quickly release the heat generated in the high-speed motor to the outside.

A high speed motor for a vertical turbo blower according to an embodiment of the present invention includes: i) a stator having a hollow core and a plurality of slots, a coil wound around the slot, and receiving a current to generate a magnetic force, ii ) It is installed rotatably with air gap in the hollow of stator, and it rotates by magnetic force, and iii) It surrounds stator with gas passage through open air and closes to both ends of iron core to support stator. It includes a motor housing.

The motor housing includes a pair of inner housings in close contact with both ends of the iron core, an outer housing surrounding the iron core with the gas passage therebetween, and a plurality of supports integrally connecting the inner housing and the outer housing while allowing the gas passage to communicate with the outside air. It may include.

Each of the pair of inner housings is formed in an annular shape to surround the coil and the rotor, and the outer diameter of the inner housing may be smaller than or equal to the outer diameter of the iron core.

The motor housing may be assembled after being separately manufactured as a first housing surrounding the upper part of the stator and a second housing surrounding the lower part of the stator, and the first housing and the second housing may form an assembly step on the mating surface. have.

The iron core is composed of a laminate in which a plurality of steel sheets are laminated and bonded, and may form a plurality of heat dissipation protrusions extending along the axial direction of the iron core on the entire outer circumferential surface facing the gas passage.

The high speed motor may further include a plurality of long bolts penetrating the support of the first housing and the support of the second housing to be coupled to the first housing and the second housing and fitted between the plurality of heat dissipation protrusions to be in close contact with the outer surface of the stator. Can be.

According to an embodiment of the present invention, by using the upper composite bearing and the lower composite bearing it is possible to effectively support the load by the axial load and the weight generated when driving in the entire region of the rotating body. In addition, by supplying compressed air to the pressurizing disk and the pressurizing piston to pressurize the rotating body downward, the axial load generated during driving can be actively canceled. Therefore, the driving stability of a rotating body can be improved.

In addition, since the ball bearings support the load during the starting operation and the stopping operation of the rotating body, the starting friction load and the driving friction load are low, so that power consumption can be reduced, and wear and damage of the sliding bearing can be suppressed. And since the sliding bearing supports the load at high speed rotation, it is possible to suppress the occurrence of vibration due to unbalance during rotation.

In addition, by providing the lubricating fluid cooled inside the high speed motor and at the same time increasing the heat radiation efficiency of the high speed motor, the efficiency and stability of the high speed motor are increased, and safe operation is possible in the long term.

1 is a cross-sectional view of a vertical turbo blower according to a first embodiment of the present invention.
FIG. 2 is a partially enlarged view of the vertical turbo blower shown in FIG. 1.
3 is a partially enlarged view of the vertical turbo blower shown in FIG. 1.
FIG. 4 is an enlarged view illustrating a sliding bearing in the vertical turbo blower shown in FIG. 1, showing a cross section of the sliding bearing.
FIG. 5 is a view illustrating a circulation path of compressed air in the vertical turbo blower shown in FIG. 1.
FIG. 6 is a view showing a circulating path of lubricating fluid in the vertical turbo blower shown in FIG. 1.
7 is a sectional view of a vertical turbo blower according to a second embodiment of the present invention.
8 is a perspective view illustrating a stator and a motor housing of the high speed motor illustrated in FIG. 1.
FIG. 9 is a cross-sectional view illustrating a detached state of a motor housing among the high speed motors illustrated in FIG. 8.
FIG. 10 is a perspective view illustrating an iron core of the stator illustrated in FIG. 8.
11 is a sectional view of a vertical turbo blower according to a third embodiment of the present invention.
12 is an exploded view of the rotor, the support shaft, and the rotating shaft of the vertical turbo blower shown in FIG.
FIG. 13 is a view illustrating a circulation path between compressed air and lubricating fluid in the vertical turbo blower shown in FIG. 11.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings so that those skilled in the art may easily implement the present invention. As those skilled in the art would realize, the described embodiments may be modified in various different ways, all without departing from the spirit or scope of the present invention.

1 is a cross-sectional view of a vertical turbo blower according to a first embodiment of the present invention.

Referring to FIG. 1, the vertical turbo blower 100 of the first embodiment includes a high speed motor 10 having a stator 11, a rotor 12, and a motor housing 13, a rotation shaft 21, and an impeller. An air compression section 20 having a diffuser passage 23 and an upper support shaft 31 and an upper compound bearing 32 and a lower support shaft 33 and a lower compound bearing 34. And a load support.

In addition, although not shown in FIG. 1, the turbo blower 100 of the first embodiment cools the inside of the high speed motor 10 and the inside of the rotating shaft 21, and at the same time, the upper composite bearing 32 and the lower composite bearing 34. It also includes a cooling lubrication unit for lubricating.

The high speed motor 10 may be a brushless DC motor with a permanent magnet embedded therein. The high speed motor 10 includes a stator 11, a rotor 12 rotatably installed inside the stator 11, and a motor housing 13 coupled to the stator 11 to support the stator 11. It includes. In the first embodiment, in the high speed motor 10, the stator 11 and the motor housing 13 are not in close contact with each other, and the motor housing 13 has the stator with the gas passage 14 interposed outside the stator 11. It consists of a structure surrounding (11).

Therefore, the heat generated in the stator 11 is directly communicated with the outside air of the gas passage 14 without passing through the motor housing 13, so that the high-speed motor 10 quickly discharges the heat generated in the stator 11 to the outside. It is possible to increase the heat dissipation efficiency. Specific coupling structure and details of the high speed motor 10 will be described later.

The rotor 12 is positioned with the stator 11 and the air gap therebetween, and the high speed motor 10 is disposed such that the central axis of the rotor 12 is perpendicular to the ground. The rotor 12 is formed to a greater length than the stator 11. The rotor 12 includes an upper rotor 121 protruding upward in the vertical direction of the stator 11 along the vertical direction, a permanent magnet embedding part 122 located inside the stator 11, and the stator 11. It includes a lower rotating body 123 protruding in the downward direction.

The air compressor 20 is connected to the impeller 22 and the rotating shaft 21 directly connected to the rotor 12, the diffuser passage 23 connected to the outlet of the impeller 22, and the diffuser passage 23. The discharge scroll 24 is provided, and the lower supporter 25 is installed below the impeller 22 and the rotating shaft 21 to support them. The diffuser passage 23 may be provided with a variable diffuser vane 26 for changing the cross-sectional area of the diffuser passage 23.

The impeller 22 is directly coupled to the lower end of the lower rotor 123. The rotating shaft 21 is installed to penetrate the inside of the impeller 22, and the rotating shaft 21 is also directly coupled to the lower end of the lower rotating body 123. The rotating shaft 21 is formed to have a greater length than the impeller 22 so that the lower portion of the rotating shaft 21 protrudes in the lower direction of the impeller 22. The lower part of the rotating shaft 21 is supported by being surrounded by the lower support 25.

The rotor 12 of the high speed motor 10 forms a first hollow 15 penetrating therein along the vertical direction. The rotary shaft 21 also penetrates the inside along the vertical direction to form a second hollow 27 that is connected to the first hollow 15. The first hollow 15 and the second hollow 27 may have the same diameter.

On the outer circumferential surface of the impeller 22, a plurality of blades 28 having a curved radial shape are formed. The impeller 22 accelerates and compresses the sucked air by high speed rotation and discharges it to the place of use via the diffuser passage 23 and the discharge scroll 24. The portion where the air flows into the impeller 22 becomes the impeller inlet, and the portion through which the compressed air passing through the blade 28 is discharged becomes the impeller outlet. In FIG. 1, the direction of movement of air passing through the impeller 22 is illustrated by an arrow.

As the rotating body composed of the rotor 12, the rotating shaft 21, and the impeller 22 is erected vertically, a bearing structure for stably supporting a large rotating body is essential. In the vertical turbo blower 100 of the first embodiment, the upper support shaft 31 and the lower support shaft 33 function as an inner diameter support shaft for supporting the inside of the rotating body, and the upper composite bearing 32 and the lower composite bearing 34 is installed at the top and bottom of the rotating body to stably support the large rotating body. At this time, the upper and lower composite bearings 32 and 34 are configured such that bearings of different characteristics selectively support the load according to the operating area (rotational speed).

FIG. 2 is a partially enlarged view of the vertical turbo blower shown in FIG. 1.

Referring to FIG. 2, the upper support shaft 31 is positioned in the first hollow 15 at a predetermined distance from the inner wall of the upper rotating body 121, and the upper supporting shaft 31 and the upper rotating body 121. An upper composite bearing 32 composed of a ball bearing 35 and a sliding bearing 36 is installed therebetween. The upper support shaft 31 is a non-rotating shaft that does not rotate when the turbo blower is driven.

3 is a partially enlarged view of the vertical turbo blower shown in FIG. 1.

Referring to FIG. 3, the lower support shaft 33 is positioned in the second hollow 27 at a predetermined distance from an inner wall of the lower portion of the rotation shaft 21, and a ball bearing is disposed between the lower support shaft 33 and the rotation shaft 21. A lower compound bearing 34 composed of a 35 and a sliding bearing 36 is installed. The lower support shaft 33 is also a non-rotating shaft that does not rotate when the turbo blower is driven.

2 and 3, the ball bearing 35 includes a ball 351, an inner ring 352 and an outer ring 353 surrounding the ball 351, and loads generated during low speed operation of the rotating body. Support. Here, the low speed operation includes a start operation and a stop operation. The ball bearing 35 of the upper composite bearing 32 may be assembled inside the upper rotating body 121, and may be provided in plural (for example, two) along the axial direction. The ball bearing 35 of the lower composite bearing 34 is assembled inside the rotating shaft 21 and may be provided in plural (for example, four) along the axial direction.

FIG. 4 is an enlarged view illustrating a sliding bearing in the vertical turbo blower shown in FIG. 1, showing a cross section of the sliding bearing.

Referring to FIG. 4, the sliding bearing 36 is provided in an annular shape on the outer circumferential surfaces of the upper support shaft 31 and the lower support shaft 33, and has a plurality of oil grooves 361 and a plurality of tapered grooves on the surface thereof. 362). The oil groove 361 and the tapered groove 362 are disposed to be inclined with respect to the axial direction (vertical direction). Each tapered groove 362 is formed such that the portion in contact with the oil groove 361 is deep and small in the direction away from it.

The sliding bearing 36 is surrounded by the upper rotating body 121 and the rotating shaft 21, and forms an oil film between the upper rotating body 121 and the rotating shaft 21 during driving. To this end, the oil groove 361 supplies a lubricating fluid (oil) to the sliding bearing 36, and the tapered groove 362 pressurizes the oil supplied to the oil groove 361 to form an oil film.

Therefore, when the rotating body rotates at a high speed, a wedge effect is caused in the rotational direction, and some oil forms a high pressure in the sliding bearing 36 by the centrifugal force. As a result, the rotating body is detached from the sliding bearing 36 to enable high speed rotation. In this way, the sliding bearing 36 supports the load during the high speed operation of the rotating body.

The sliding bearing 36 is formed on the outer circumferential surface of the fixed body, that is, the upper support shaft 31 and the lower support shaft 33, not the rotating body. If it is assumed that the oil groove 361 and the tapered groove 362 are formed on the inner wall of the rotating body, the dynamic equilibrium may be affected according to the oil supply state. Therefore, the sliding bearing 36 is formed on the outer circumferential surfaces of the upper support shaft 31 and the lower support shaft 33, which are fixed bodies, without forming the sliding bearing 36 on the rotating body.

In the above-described sliding bearing 36 structure, the lubricating fluid receives centrifugal force inside the rotating body to uniformly form a constant lubrication film (oil film), and the lubrication film (oil film) is a sliding bearing together with the oil pressure produced in the tapered groove 362. (36) To increase load bearing capacity during operation.

2 and 3, the self-setting gap of the sliding bearing 36 is set larger than the self-setting gap of the ball bearing 35 so that the load supporting action is automatically changed according to the operating area (rotational speed). Here, the setting gap of the sliding bearing 36 means a difference between the inner diameter of the upper rotating body 121 or the rotating shaft 21 on which the sliding bearing 36 is installed and the outer diameter of the sliding bearing 36. The set gap of the ball bearing 35 means a value obtained by subtracting the diameter of the ball 351 from the difference between the inner diameter of the outer ring 353 and the outer diameter of the inner ring 352. For example, when the setting gap of the sliding bearing 36 is 0.1 mm, the setting gap of the ball bearing 35 may be 0.05 mm.

Since the ball bearing 35 supports the load during the start operation and the stop operation as described above, power consumption can be reduced by lowering the starting friction load and the driving friction load, and the wear and damage of the sliding bearing 36 can be prevented. And since the high bearing is supported using the sliding bearing 36, it is possible to suppress the occurrence of vibration due to unbalance during rotation. In addition, the ball bearing 35 acts as a safety guide during high speed operation to increase driving stability.

Referring to FIG. 1, in the vertical turbo blower 100, an axial load that the rotor rotates upward due to the pressure difference between the impeller inlet and the impeller outlet during driving is generated, and the load due to the weight of the rotor also moves in the axial direction. Occurs. However, since the load by the weight of the rotating body is in the opposite direction to the axial load generated during the driving, the axial load generated during the driving is partially offset. In addition, the vertical turbo blower 100 includes a structure that presses the rotating body in the downward direction to actively cancel the axial load generated during driving.

FIG. 5 is a view illustrating a circulation path of compressed air in the vertical turbo blower shown in FIG. 1.

Referring to FIG. 5, the pressing disk 16 is fixed to the outer circumferential surface of the upper rotating body 121 to rotate together with the upper rotating body 121. The upper support 17 is located above the pressing disk 16 at a distance from the pressing disk 16. The upper support 17 surrounds a part of the upper support shaft 31, and supports the upper support shaft 31 so that the upper support shaft 31 can slide in the vertical direction. The upper supporter 17 has an air inlet 171 for injecting compressed air toward the pressurizing disk 16, and a guide member 172 extending toward the pressurizing disk 16 to prevent shaking of the pressurizing disk 16. Is formed.

Two air outlets 252 for discharging the compressed air leaking from the impeller 22 are formed in the lower support 25 under the impeller 22. And the pressure piston 37 is formed on the lower outer peripheral surface of the lower support shaft (33). The pressure piston 37 is accommodated in the recess 253 formed in the lower support 25, the lower support 25 is the lower support shaft so that the lower support shaft 33 and the pressure piston 37 can slide in the vertical direction. Support 33. An air passage 331 is provided inside the lower support shaft 33 to receive compressed air and to deliver the compressed air to the upper portion of the pressure piston 37.

The air inlet 252 of any one of the two air outlets 252 formed in the lower support 25 passes through the air cooler 42 through the first air pipe 41 and the air inlet 171 of the upper support 17. Connected with. The other air outlet 252 is connected to the air passage 331 of the lower support shaft 33 through the second air pipe 43. Therefore, in the process of compressing and discharging air by rotating the impeller 22, the pressurizing disk 16 and the pressurizing piston 37 are strongly pressed down by the compressed air leaked from the impeller 22, so that the rotating body tries to ascend upward. It can actively offset the axial load.

As such, the vertical turbo blower 100 simplifies the overall configuration by providing compressed air to the pressurizing disk 16 and the pressurizing piston 37 without a separate air tank, and effectively cancels the axial load generated during driving. The overall driving stability can be improved.

The vertical turbo blower 100 provides cooled lubricating fluid (oil mist) towards the upper composite bearing 32. To this end, the upper support shaft 31 is formed with an oil passage 311 (see FIG. 2) and one or more spray nozzles 312 (see FIG. 2) for providing lubricating fluid toward the upper composite bearing 32. The lubricating fluid lubricates the upper composite bearing 32 and then moves along the first hollow 15 and the second hollow 27 to cool the inside of the high speed motor 10, and lubricates the lower composite bearing 34. Is then discharged to the outside.

FIG. 6 is a view showing a circulating path of lubricating fluid in the vertical turbo blower shown in FIG. 1.

Referring to FIG. 6, the cooling lubrication unit 50 includes an oil tank 51 and an oil pump 52, an oil vapor cooler 53 and an oil cooler 54 connected to the oil tank 51. The oil pump 52 is connected to the oil passage 311 of the upper support shaft 31 through the first oil pipe 55 to transfer the oil stored in the oil tank 51 to the upper support shaft 31. The oil mist is then injected into the upper composite bearing 32 through the spray nozzle 312 (see FIG. 2). The injected oil mist is supplied to the lower composite bearing 34 through the first hollow 15 and the second hollow 27 to lubricate it.

In addition, an oil vapor outlet 254 is formed at a portion of the lower supporter 25 that faces the rotating shaft 21, and the oil vapor outlet 254 is connected to the oil vapor cooler 53 through the second oil pipe 56. In addition, an oil outlet 255 for discharging oil is formed at a lower end of the lower support 25, and the oil outlet 255 is connected to the oil cooler 54 through the third oil pipe 57. The oil vapor cooler 53 and the oil cooler 54 cool the used lubricating fluid and transfer it to the oil tank 51. Through this circulation action, the lubricating fluid can be reused.

In the vertical turbo blower 100 of the first embodiment, the cooled lubricating fluid not only functions to lubricate the upper and lower composite bearings 32 and 34, but also flows through the first hollow 15 and the second hollow 27, and thus the high speed motor. Also includes the function of cooling (10). Therefore, it is possible to prevent overheating of the high speed motor 10 to increase the efficiency of the high speed motor 10 and to enable safe operation in the long term. Reference numeral 58 in FIG. 6 denotes a sensor for measuring the pressure and temperature of the lubricating fluid.

7 is a sectional view of a vertical turbo blower according to a second embodiment of the present invention.

Referring to FIG. 7, the vertical turbo blower 200 according to the second embodiment of the present invention includes the first support shaft 38 between the upper support shaft 31 and the lower support shaft 33. It has the same configuration as the vertical turbo blower of the embodiment. The same reference numerals are used for the same members as those in the first embodiment. The central support shaft 38 is positioned over the first hollow 15 and the second hollow 27 at a predetermined distance from the inner wall of the rotor 12 and the inner wall of the rotating shaft 21, and has an inner center of the rotor. It functions as an inner diameter support shaft for supporting

Next, the high speed motor 10 used for the vertical turbo blowers 100 and 200 is demonstrated. 8 is a perspective view illustrating a stator and a motor housing of the high speed motor illustrated in FIG. 1.

1 and 8, the motor housing 13 surrounds the stator 11 with the gas passage 14 therebetween at the outside of the stator 11. That is, the outer circumferential surface of the stator 11 and the motor housing 13 are not in close contact with each other. Instead, the entire outer circumferential surface of the stator 11 faces the inner wall of the motor housing 13 with the gas passage 14 communicating with the outside air therebetween. Therefore, heat generated in the stator 11 is directly transferred to the outside air flowing through the gas passage 14 to increase the heat radiation efficiency of the high speed motor 10.

To this end, the motor housing 13 has a pair of inner housings 131 which are in close contact with both ends of the stator 11 to support the stator 11, and have an inner diameter larger than the outer diameter of the stator 11 to provide a gas passage ( The outer housing 132 which surrounds the stator 11 with 14 between them and the outer wall of the inner housing 131 and the inner wall of the outer housing 132 integrally connect with each other while allowing the gas passage 14 to communicate with the outside air. It includes a plurality of supports (133).

The inner housing 131 is formed in an annular shape surrounding the coil 18 of the stator 11 and is formed to have an outer diameter equal to or smaller than the outer diameter of the stator 11 so as not to block the gas passage 14. The plurality of supports 133 extend radially from the inner housing 131 and are disposed at equal intervals along the circumferential direction of the stator 11.

FIG. 9 is a cross-sectional view illustrating a detached state of a motor housing among the high speed motors illustrated in FIG. 8.

Referring to FIGS. 8 and 9, the motor housing 13 is manufactured separately from the first housing 13A surrounding the upper part of the stator 11 and the second housing 13B surrounding the lower part of the stator 11. And then assembled together. Each of the first housing 13A and the second housing 13B is made of an integral structure using castings. An assembling step 134 is formed on the engaging surface of the first housing 13A and the second housing 13B to match the assembling position.

The long bolt 19 is coupled to the two supports while passing through the support 133 of the first housing 13A and the support 133 of the second housing 13B. The long bolt 19 forms a bolt head 191 at either end and a thread 192 at the opposite end. Accordingly, the long bolt 19 is sequentially fitted to the support 133 of the second housing 13B and the support 133 of the first housing 13A, and then the nut (outside the support 133 of the first housing 13A). 193 and secured to the first and second housings 13A, 13B.

In addition, the stator 11 may maximize the heat dissipation efficiency by forming a heat dissipation protrusion on the entire outer circumferential surface. FIG. 10 is a perspective view illustrating an iron core of the stator illustrated in FIG. 8.

Referring to FIGS. 8 and 10, the stator 11 has an iron core 113 forming a hollow 111 and a plurality of slots 112 therein, and a coil wound around the slot 112 of the iron core 113. (18). Iron core 113 is composed of a combination of a plurality of silicon steel sheets of the same shape laminated and fixed. The iron core 113 is formed in a cylindrical or similar shape, and forms a plurality of slots 112 connected to the hollow 111 along an inner circumference thereof.

The iron core 113 forms a plurality of heat dissipation protrusions 114 on the entire outer circumferential surface. The heat dissipation protrusion 114 extends long along the axial direction of the iron core 113, and the width, height, and spacing of the heat dissipation protrusion 114 may be the same. If the heat radiation protrusions 114 are formed in such a shape, all steel sheets can be manufactured in the same shape during steel sheet production, thereby increasing manufacturing efficiency, and implementing a uniform heat dissipation effect on the entire outer circumferential surface of the stator 11. On the other hand, the long bolt 19 is located in the concave portion between the heat dissipation projections 114 of the outer peripheral surface of the iron core 113 can stably support the iron core 113.

FIG. 11 is a cross-sectional view of a vertical turbo blower according to a third exemplary embodiment of the present invention, and FIG. 12 is an exploded view of the rotor, the support shaft, and the rotating shaft of the vertical turbo blower shown in FIG. 11.

11 and 12, in the vertical turbo blower 300 of the third embodiment, a first hollow 15 ′ is formed in a part of the rotor 12 ′ of the high speed motor 10 ′, and the first hollow blower 300 is formed. One support shaft 39 is positioned at the 15 'and the second hollow 27, and the upper composite bearing 32 and the lower composite bearing 34 are installed on the upper and lower portions of the support shaft 39. Except for the above, the structure is similar to that of the vertical turbo blower of the first embodiment. The same reference numerals are used for the same members as those in the first embodiment. In the following, portions different from the first and second embodiments will be mainly described.

The rotor 12 'of the high speed motor 10' does not form a first hollow penetrating the whole thereof, and has a cylindrical extension 124 having a first hollow 15 'formed therein at a lower end thereof. . The rotating shaft 21 is coupled to the extension portion 124 in an upright state, and forms a second hollow 27 that is connected to the first hollow 15 ′ along the vertical direction. The upper rotor 121 ′ and the press disk 16 ′ are fixed to the top of the rotor 12 ′ to rotate together with the rotor 12 ′.

One support shaft 39 is positioned over the first hollow 15 ′ and the second hollow 27 at a distance from the inner wall of the extension portion 124 and the inner wall of the rotation shaft 21. An upper composite bearing 32 composed of a ball bearing 35 and a sliding bearing 36 is installed between the support shaft 39 and the extension part 124 at the upper portion of the support shaft 39. In the lower portion of the support shaft 39 and the rotary shaft 21 between the lower composite bearing 34 consisting of a ball bearing 35 and a sliding bearing 36 is installed.

A part of the support shaft 39 protrudes in the downward direction of the rotation shaft 21, and the lower support 25 ′ supports the part of the support shaft 39 to be slidable in the vertical direction. An extension shaft 45 may be coupled to a lower end of the support shaft 39, and the support shaft 39 and the extension shaft 45 form a third hollow 46 penetrating therein along the vertical direction.

Lubricating fluid (oil mist) provided to the third hollow 46 at the lower end of the extension shaft 45 is discharged from the upper end of the support shaft 39 to the first hollow 15 '. The lubricating fluid discharged into the first hollow 15 ′ is provided to the upper composite bearing 32 to lubricate it, flows through the space between the support shaft 39 and the rotating shaft 21, and cools the inside of the rotating shaft 21. It is provided to the composite bearing 34 and lubricated and discharged to the lower support 25 ′.

FIG. 13 is a view illustrating a circulation path between compressed air and lubricating fluid in the vertical turbo blower shown in FIG. 11.

Referring to FIG. 13, the air outlet 252 formed in the lower support 25 ′ is connected to the air inlet 171 ′ of the upper support 17 ′ through the air cooler 42 through the first air pipe 41. The configuration is the same as the first embodiment described above.

The cooling lubrication part 50 ′ is connected to the oil tank 51 and the oil pump 52, the oil mist mixer 59 connected to the oil pump 52 and the air cooler 42, and the oil tank 51. Oil cooler 54.

The oil mist mixer 59 receives oil from the oil tank 51 through the fourth oil pipe 61 and receives compressed air cooled from the air cooler 42 through the fourth air pipe 47. It generates and provides the generated oil mist to the third hollow 46 at the bottom of the extension shaft (45). The oil cooler 54 is connected to the oil outlet 255 of the lower support 25 ′ through the fifth oil pipe 62 to recover the used oil mist, and cools it to the oil tank 51.

As described above, the vertical turbo blower 300 of the third embodiment generates oil mist by mixing oil and compressed air at the outside of the turbo blower 300 unlike the first and second embodiments, and then supports the support shaft ( 39 to a third hollow 46. 11 and 12 illustrate a high speed motor 10 'having a structure in which the motor housing 13' is in close contact with the outer circumferential surface of the stator 11 ', but also in the vertical turbo blower 300 of the third embodiment. The high speed motor of the first embodiment described above can be applied.

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

10: high speed motor 11: stator
13: motor housing 13A: first housing
13B: second housing 14: gas passage
18: coil 19: sheet bolt
111: hollow 112: slot
113: iron core 114: heat dissipation projection

Claims (6)

A stator having a hollow core and a plurality of slots and a coil wound around the slot, the stator configured to receive a current to generate a magnetic force;
A rotor installed rotatably with an air gap in the hollow of the stator and rotating by the magnetic force; And
A motor housing surrounding the stator with a gas passage communicating with the outside air interposed therebetween and supporting the stator
Including,
The motor housing includes a pair of inner housings in close contact with both ends of the iron core, an outer housing surrounding the iron core with the gas passage therebetween, and the inner housing and the outer housing while allowing the gas passage to communicate with the outside air. A high speed motor for a vertical turbo blower comprising a plurality of supports connected integrally. delete The method of claim 1,
Each of the pair of inner housings is formed in an annular shape to surround the coil and the rotor, and the outer diameter of the inner housing is formed to be less than or equal to the outer diameter of the iron core. The method according to claim 1 or 3,
The iron core is composed of a laminated body in which a plurality of steel sheets are laminated and bonded, the high-speed motor for a vertical turbo blower to form a plurality of heat dissipation projections extending along the axial direction of the iron core on the entire outer peripheral surface facing the gas passage. The method of claim 4, wherein
The motor housing is separately assembled with a first housing surrounding the upper part of the stator and a second housing surrounding the lower part of the stator, and then assembled together, and the first housing and the second housing have an assembly step on the coupling surface. High speed motor for vertical turbo blowers to be formed. The method of claim 5,
A plurality of long bolts which pass through the support of the first housing and the support of the second housing, are coupled to the first housing and the second housing, are fitted between the plurality of heat dissipation protrusions, and are in close contact with the outer surface of the stator; High speed motor for a vertical turbo blower that includes.

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