KR102239812B1 - Turbo Compressor - Google Patents

Abstract

An embodiment of the present invention relates to a turbo compressor which has a simple structure. According to one aspect, the turbo compressor comprises: a driving motor including a rotary shaft; a motor casing which supports the driving motor; an impeller which rotates by the rotary shaft; a shroud which accommodates the impeller, and is spaced apart from the impeller; a gas suction part which is connected to the shroud, and guides refrigerant gas to the impeller; a diffuser which compresses the refrigerant gas discharged from the impeller and includes at least one first sealing part protruding in a circumferential direction from the inner circumferential surface opposite to the outer circumferential surface of the impeller; a gas outlet which discharges the refrigerant gas compressed by the impeller and the diffuser; and a sealing member which is provided close to the diffuser, and includes at least one second sealing part protruding in a circumferential direction from the inner circumferential surface formed therethrough to accommodate the rotary shaft.

Description

Turbo Compressor {Turbo Compressor}

This embodiment relates to a turbo compressor.

In general, compressors can be largely divided into positive displacement compressors and turbo compressors. The positive displacement compressor uses a piston or vane, such as a reciprocating type or a rotary type, in which fluid is sucked, compressed, and then discharged. On the other hand, a turbo-type compressor uses a rotating element to inhale, compress, and then discharge fluid.

The positive displacement compressor determines the compression ratio by appropriately adjusting the ratio of the suction volume and the discharge volume to obtain the desired discharge pressure. Therefore, the positive displacement compressor is limited in miniaturizing the overall size relative to its capacity.

The turbo-type compressor is similar to a turbo blower, but has a higher discharge pressure and a lower flow rate than a turbo blower. These turbo-type compressors increase pressure in a fluid that continuously flows, and are classified into an axial flow type when the fluid flows in the axial direction, and a centrifugal type when the fluid flows in a radial direction.

In general, a turbocompressor includes a driving motor, an impeller rotating by the driving force of the driving motor, and a diffuser that converts the kinetic energy of the refrigerant gas discharged by the rotation of the impeller into pressure energy. Gas can be compressed. In addition, since the impeller of the turbocompressor rotates relative to the diffuser, a gap is generated between the impeller and the diffuser, and refrigerant gas may leak through the gap.

An example of such a conventional turbocompressor is disclosed in the diffuse storage structure of the turbocompressor of Korean Patent Application No. 10-2001-49571. Such a conventional turbocompressor has an impeller coupled to a rotating shaft, a diffuser fixing member equipped with a diffuser, a plurality of grooves provided to perform a sealing role on the inner circumferential surface of a through hole formed so that the rotating shaft penetrates at the center of the diffuser fixing member, and an impeller. And a sealing groove formed in the diffuser fixing member in the axial direction of the rotation shaft, a sealing member inserted into the sealing groove, and a cover member for compressing the impeller so that the impeller compresses the sealing member.

Accordingly, the conventional turbo compressor can suppress leakage of refrigerant gas between the impeller and the diffuser fixing member.

However, such a conventional turbocompressor can double suppress the leakage of refrigerant gas between the impeller and the diffuser through a plurality of grooves provided on the inner circumferential surface of the sealing member and the through hole, but a separate sealing member must be provided. There is a problem in that the structure is complicated, such as having to process the sealing groove for mounting of.

The present invention is to provide a turbocompressor that has a simple structure and can easily block leakage of refrigerant gas between an impeller and a diffuser.

The turbo compressor according to the present embodiment includes: a drive motor including a rotating shaft; A motor casing supporting the driving motor; An impeller rotated by the rotation shaft; A shroud accommodating the impeller and spaced apart from the impeller; A gas suction unit connected to the shroud to guide the refrigerant gas to the impeller; A diffuser that compresses the refrigerant gas discharged from the impeller and has at least one first sealing portion protruding in a circumferential direction on an inner peripheral surface opposite to the outer peripheral surface of the impeller; A gas discharge port for discharging the refrigerant gas compressed by the impeller and the diffuser; And a sealing member provided close to the diffuser and having at least one second sealing portion protruding in a circumferential direction on an inner circumferential surface penetrated to receive the rotation shaft.

In this embodiment, the turbocompressor includes a diffuser having at least one first sealing portion protruding in the circumferential direction on an inner circumferential surface opposite to the outer circumferential surface of the impeller, and at least one second protruding circumferentially on the inner circumferential surface penetrating to receive the rotation shaft. The structure is simple, including a sealing member having a sealing part and a sealing pad, and it is possible to easily block leakage of refrigerant gas between the impeller and the diffuser.

1 is a cross-sectional view of a turbo compressor according to an embodiment of the present invention.
FIG. 2 is an enlarged view of a part of FIG. 1;
3 is a perspective view of an impeller and a diffuser according to an embodiment of the present invention.
Figure 4 is a cross-sectional view showing a state of use of the impeller according to an embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

However, the technical idea of the present invention is not limited to some embodiments to be described, but may be implemented in various different forms, and within the scope of the technical idea of the present invention, one or more of the constituent elements may be selectively selected between the embodiments. It can be combined with and substituted for use.

In addition, terms (including technical and scientific terms) used in the embodiments of the present invention are generally understood by those of ordinary skill in the art, unless explicitly defined and described. It can be interpreted as a meaning, and terms generally used, such as terms defined in a dictionary, may be interpreted in consideration of the meaning in the context of the related technology.

In addition, terms used in the embodiments of the present invention are for describing the embodiments and are not intended to limit the present invention. In the present specification, the singular form may include the plural form unless specifically stated in the phrase, and when described as “at least one (or more than one) of A and (and) B and C”, it is combined with A, B, and C. It may contain one or more of all possible combinations.

In addition, terms such as first, second, A, B, (a), and (b) may be used in describing the constituent elements of the embodiment of the present invention.

These terms are only for distinguishing the constituent element from other constituent elements, and are not limited to the nature, order, or order of the constituent element by the term.

And, when a component is described as being'connected','coupled' or'connected' to another component, the component is not only directly connected, coupled or connected to the other component, but also the component It may also include a case of being'connected','coupled', or'connected' due to another component between the and the other component.

In addition, when it is described as being formed or disposed on the "top (top) or bottom (bottom)" of each component, the top (top) or bottom (bottom) is not only when the two components are in direct contact with each other, but also It also includes the case where one or more other components are formed or disposed between the two components. In addition, when expressed as "upper (upper) or lower (lower)", the meaning of not only an upward direction but also a downward direction based on one component may be included.

1 is a cross-sectional view of a turbo compressor according to an embodiment of the present invention, FIG. 2 is an enlarged view of a part of FIG. 1, and FIG. 3 is a perspective view of an impeller and a diffuser according to an embodiment of the present invention.

1 to 3, the turbocompressor 1 according to the present invention includes a driving motor 20, an impeller 40 provided to rotate by a rotation shaft 5 of the driving motor 20, and an impeller. It includes a diffuser 30 provided to compress the refrigerant gas discharged from the 40, and a sealing member 50 provided close to the diffuser 30 and formed therethrough to accommodate the rotating shaft 5. The turbocompressor (1) is a motor casing (10) that supports the driving motor (20), a shroud (47) that accommodates the impeller (40) and is spaced apart from the impeller, and is connected to the shroud (47) and is connected to the impeller ( 40), a gas inlet 45 for guiding the refrigerant gas, a gas outlet 49 for discharging the refrigerant gas compressed by the impeller 40 and the diffuser 30, and the refrigerant gas compressed in one stage 2 It further includes a gas connection part 48 for conveying to be compressed to the stage.

The motor casing 10 forms a predetermined accommodation space to accommodate the driving motor 20 and the rotating shaft 5, and a cooling gas inlet 11 provided at one side to suck cooling gas for cooling the driving motor 20 And, it has a cooling gas discharge port 13 provided to discharge the cooling gas sucked from the suction port 11 on the other side after cooling the drive motor (20). In addition, both sides of the motor casing 10 are coupled to the rotation shaft 5 to support the rotation shaft 5.

The rotating shaft 5 is coupled with a pair of impellers 40 on both sides thereof, and the central region thereof is integrally coupled with the rotor 25 of the driving motor 20 to be described later to rotate. And, since the rotation shaft 5 usually rotates at high speed, a thrust bearing 17 that supports the rotation shaft 5 in the axial direction, and a radial bearing that supports the rotation shaft 5 in the radial direction. ) Can be combined with (15).

The driving motor 20 includes a stator 21 integrally coupled to the motor casing 10, and a rotor 25 that is rotatably inserted at a predetermined distance apart from the inside of the stator 21. Includes.

The impeller 40 is provided in a pair and has an impeller body 41 coupled to the rotating shaft 5, and a plurality of blades 43 formed on the impeller body 41 with a gap between the shroud 47 and a spaced gap.

The impeller body 41 has a circular cross-sectional shape, and its outer circumferential surface includes the first sealing part 35 of the diffuser 30 to be described later to suppress leakage of the refrigerant gas between the impeller body 41 and the diffuser 30. Come into contact.

The plurality of blades 43 are provided in the impeller body 41 at equal intervals by sucking refrigerant gas from the gas intake unit 45.

The diffuser 30 is provided in a pair corresponding to each impeller 40 to form a space capable of compressing the refrigerant gas discharged from the impeller 40. The diffuser 30 includes a diffuser part 31 for compressing the refrigerant gas discharged from the impeller 40, and at least one first sealing part 35 protruding in the circumferential direction on the inner circumferential surface opposite to the outer circumferential surface of the impeller 40. ). The diffuser 30 penetrates to accommodate the impeller 40 and may be provided outside the impeller 40 in the radial direction. The diffuser 30 is a vane diffuser in which a blade (not shown) for guiding the refrigerant gas discharged from the impeller 40 to the diffuser part 31 is provided, or a diffuser in which a blade (not shown) is not provided in the diffuser part 31 I can.

The first sealing portion 35 is provided to be in contact with the outer circumferential surface of the impeller body 41. As shown in FIG. 1, the first sealing parts 35 are provided in a plurality of spaced apart from each other so as to contact the outer circumferential surface of the impeller body 41. The first sealing portion 35 is formed in a direction perpendicular to the longitudinal direction of the rotation shaft 5 to prevent leakage of the refrigerant gas between the impeller body 41 and the impeller body 41. The first sealing part 35 may be provided in a serrated shape. That is, when the end of the first sealing part 35 in contact with the outer circumferential surface of the impeller body 41 is sharply formed in a serrated shape, it can be easily in close contact with the outer circumferential surface of the impeller body 41. The first sealing portion 35 may be formed of an elastic material such as rubber so as to elastically adhere to the outer circumferential surface of the impeller body 41 that rotates relative to each other.

Accordingly, it is possible to block the refrigerant gas leaking between the diffuser 30 and the impeller 40 by the first sealing part 35. The sealing member 50 includes at least one second sealing portion 51 protruding in the circumferential direction on an inner circumferential surface penetrated to receive the rotation shaft 5. The sealing member 50 is provided to prevent the refrigerant gas passing through the first sealing portion 35 from leaking into the motor casing 10.

The sealing member 50 is integrally coupled with the diffuser 30 as an example of the present invention. However, the sealing member 50 may be provided close to the diffuser 30.

The second sealing portion 51 is provided to be in close contact with the outer circumferential surface of the rotation shaft 5. As shown in FIG. 1, the second sealing portions 51 are spaced apart from each other so as to contact the outer circumferential surface of the rotation shaft 5 and are provided in plural. The second sealing part 51 is formed in a direction perpendicular to the longitudinal direction of the rotation shaft 5 to prevent the refrigerant gas passing through the first sealing part 35 from leaking between the sealing member 50 and the rotation shaft 5. do. The second sealing part 51 is provided in a serrated shape like the first sealing part 35. The second sealing part 51 may be formed of an elastic material such as rubber so as to elastically adhere to the outer circumferential surface of the rotating shaft 5 that rotates relative to each other.

Accordingly, it is possible to block the refrigerant gas leaking between the sealing member 50 and the rotation shaft 5 by the second sealing part 51. With this configuration, an operation process of the first sealing unit 35 and the second sealing unit 51 provided in the turbocompressor 1 according to the present invention will be described as follows.

First, power is applied to the drive motor 20 so that the drive motor 20 rotates the rotation shaft 5. Then, a pair of impellers 40 rotate integrally with the rotating shaft 5, and the refrigerant gas from the gas intake part 45 is transferred to the diffuser 30 through the impeller 40 by the rotation of the impeller 40. It is inhaled and compressed. At this time, since the impeller 40 rotates relative to the diffuser 30, a gap may occur between the impeller 40 and the diffuser 30, and refrigerant gas may leak through the gap. Accordingly, the refrigerant gas leaking between the diffuser 30 and the impeller 40 can be blocked by the first sealing portion 35 provided in the diffuser 30. And, even if the refrigerant gas leaks through the first sealing part 35, the second sealing part 51 provided in the sealing member 50 prevents the double refrigerant gas from leaking into the motor casing 10. can do. In addition, the structure is simple because the first sealing portion 35 and the second sealing portion 51 may be formed to protrude from the inner circumferential surface of the diffuser 30 and the inner circumferential surface of the sealing member 50, respectively.

Ends of the first sealing portion 35 and the second sealing portion 51 may be formed to be round. Accordingly, it is possible to minimize friction and seal the rotation of the impeller 40 and the rotation shaft 5.

In addition, the material of the first sealing portion 35 and the second sealing portion 51 is formed of a material having a lower hardness than the material of the rotating shaft 5 and the impeller 40, the rotating shaft 5 and the impeller 40 By being worn during rotation of, a minimum gap for rotation may be formed.

Meanwhile, a sealing pad 60 may be disposed between the inner surface of the diffuser part 31 and the outer surface of the sealing member 50. At least part of the sealing pad 60 may be disposed to overlap the diffuser part 31 in the horizontal direction, and another part may be disposed to overlap the impeller body 41 in the horizontal direction. In addition, the sealing pad 60 may also be disposed to overlap the first sealing portion 35 and the second sealing portion 51 in the horizontal direction, respectively.

The sealing pad 60 has a hole in the center through which the rotation shaft 5 passes, and the diameter of the hole may be larger than the diameter of the rotation shaft 5.

With the structure as described above, the turbocompressor includes a diffuser having at least one first sealing portion protruding circumferentially on an inner circumferential surface opposite to the outer circumferential surface of the impeller, and at least one protruding circumferentially on the inner circumferential surface penetrating to receive the rotation shaft. The structure is simple, including a sealing member having a second sealing portion and a sealing pad, and it is possible to easily block leakage of refrigerant gas between the impeller and the diffuser.

On the other hand, the shroud 47 is provided to be spaced apart from the blade 43 of the impeller 40 between the gas intake portion 45 and the diffuser 31, which is a gas discharge portion. In addition, the shroud 47 is provided with a plurality of channels 70 that are obliquely disposed toward the diffuser 31 in the rotational direction of the impeller 40 to suppress a reverse flow phenomenon of a gas to be described later and a leakage flow phenomenon of a gas to be described later. do.

The reverse flow phenomenon of the gas is a factor of lowering the compression efficiency because the impeller 40 obstructs the flow of the gas discharged from the gas intake part 45 to the diffuser 31. In addition, both sides of each blade 43 provided in the impeller 40 have different speeds and frictions of the gas discharged according to the rotational direction of the impeller 40, and each blade 43 Different pressures are distributed on both sides of the. And, due to the pressure difference between the two sides of the blade 43, a leakage flow phenomenon flowing across the blade 43 from one side of the blade 43 to the other side through the gap between the shroud 47 and the blade 43 Will occur. In addition, the leakage flow phenomenon of the gas proceeds to the other blades 43 horizontally adjacent to the discharge direction C of the gas, thereby interfering with the discharge flow of the gas, thereby reducing the compression efficiency.

It is preferable that the plurality of channels 70 are provided in the gas discharge region of the shroud 47 adjacent to the diffuser 31. That is, it is preferable that the plurality of channels 70 are provided in a gas discharge region adjacent to the diffuser 31, not a gas suction region of the shroud 47 adjacent to the gas suction unit 45. This is because a gas flow phenomenon and a gas leakage flow phenomenon strongly appear in the gas discharge region of the shroud 47. However, it goes without saying that the plurality of channels 70 may be provided on the entire inner circumferential surface of the shroud 47 including the gas intake area as well as the gas discharge area of the shroud 47 adjacent to the diffuser 31.

In addition, it is preferable that each of the channels 70 that are close to each other are overlapped to be spaced apart in the gas discharge direction. That is, each channel 70 is preferably provided so as to be overlapped in order to effectively suppress a gas flow phenomenon and a gas leakage flow phenomenon in both end regions of the channel 70.

In addition, each channel 70 is preferably provided in a curved shape. Each channel 70 is preferably provided to have an arc shape in the direction in which the gas is discharged. This is to easily discharge the leakage flow of gas generated from both sides of the blades of the impeller 40 to the diffuser 31 through the plurality of channels 70.

In addition, it is preferable that the plurality of channels 70 are recessed in the inner circumferential surface of the shroud 47. In addition, each channel 70 is preferably formed to have a rectangular cross-section, but of course it may be provided in a semicircular shape or the like. In addition, the width of each channel 70 is preferably provided so as to suppress the gas flow phenomenon and the leakage flow phenomenon of the gas, the size of the shroud 47 and the impeller 40, and the impeller 40 Of course, it may vary depending on the rotational speed of

The plurality of channels 70 may include a first channel, a second channel, and a third channel in a direction from the gas intake part 45 toward the gas discharge part. Accordingly, the first channel may be disposed relatively close to the gas intake unit 45, and the third channel may be disposed relatively close to the gas discharge unit. In this case, the first channel may be the lowest and the third channel may be the highest as for a depth that is depressed from the inner surface of the shroud 47. In other words, the length from the inner surface of the shroud 47 to the bottom surface of each channel may be formed such that the second channel is longer than the first channel, and the third channel is longer than the second channel. Accordingly, the closer the gas discharge portion is, the longer the channel is depressed, so that the leakage flow phenomenon can be more reliably suppressed.

Further, in order to more easily guide the flow direction of the gas, the channel 70 may be formed in a trapezoidal cross-sectional shape. Accordingly, an inclined surface having a smaller cross-sectional area may be formed on the inner circumferential surface of the channel 70 excluding the bottom surface as it goes toward the bottom surface.

Accordingly, the turbocompressor may increase compression efficiency by providing a plurality of channels in the shroud inclined toward the diffuser in the rotational direction of the impeller, thereby suppressing the phenomenon of gas leakage as well as backflow of gas.

4 is a cross-sectional view showing a state of use of an impeller according to an embodiment of the present invention.

An inclined surface and a curved surface may be formed on a surface of the impeller 40 that faces the shroud 47 of the blades 43. The inner surface of the shroud 47 may include a flat portion 47a and a curved portion 47b. The curved portion 47b may be disposed between a plurality of mutually perpendicular planar portions, that is, in a region forming an inner edge of the shroud 47. The inclined surface may be disposed to face the flat portion 47a, and the curved surface may be disposed to face the curved portion 47b.

The spacing between the blades 43 and the shroud 47 may be formed to become smaller from the gas intake part 45 to the gas discharge part.

More specifically, the inclined surface of the outer surface of the wing 43 may be formed such that the distance from the gas intake part 45 to the gas discharge part becomes closer to the inner surface of the shroud 47. The curved surface may have a certain curvature, and the distance from the gas intake part 45 to the gas discharge part may become closer to the inner surface of the shroud 47.

At this time, the first gap T1 formed between one end of the inclined surface 122 and the inner surface of the shroud 47 is a second gap formed between the end of the curved surface 123 and the inner surface of the shroud 47 (T2) can be 10 times.

Accordingly, since the gap between the wing 43 and the shroud 47 is sequentially decreased by the inclined surface 122 and the curved surface 123, it is possible to prevent the gas from flowing backward.

In addition, the shroud 47 and the wing 43 are disposed to face each other with the curved surface 123 and the curved surface portion 47b facing each other, and the inclined surface 122 is disposed to face the flat portion 47a. It is possible to prevent the formation of vortex in the compressed fluid containing gas.

In the above, even if all the constituent elements constituting the embodiments of the present invention have been described as being combined into one or operating in combination, the present invention is not necessarily limited to these embodiments. That is, within the scope of the object of the present invention, all the constituent elements may be selectively combined and operated in one or more. In addition, terms such as'include','comprise', or'have' described above mean that the corresponding component can be present unless otherwise stated, so other components are excluded. It should not be construed as being able to further include other components. All terms, including technical or scientific terms, have the same meaning as commonly understood by one of ordinary skill in the art, unless otherwise defined. Terms generally used, such as terms defined in the dictionary, should be interpreted as being consistent with the meaning of the context of the related technology, and are not interpreted as ideal or excessively formal meanings unless explicitly defined in the present invention.

The above description is merely illustrative of the technical idea of the present invention, and those of ordinary skill in the art to which the present invention pertains will be able to make various modifications and variations without departing from the essential characteristics of the present invention. Accordingly, the embodiments disclosed in the present invention are not intended to limit the technical idea of the present invention, but to explain the technical idea, and the scope of the technical idea of the present invention is not limited by these embodiments. The scope of protection of the present invention should be construed by the following claims, and all technical ideas within the scope equivalent thereto should be construed as being included in the scope of the present invention.

Claims (5)

A drive motor including a rotating shaft;
A motor casing supporting the driving motor;
An impeller rotated by the rotation shaft;
A shroud accommodating the impeller and spaced apart from the impeller;
A gas suction unit connected to the shroud to guide the refrigerant gas to the impeller;
A diffuser that compresses the refrigerant gas discharged from the impeller and has at least one first sealing portion protruding in a circumferential direction on an inner peripheral surface opposite to the outer peripheral surface of the impeller;
A gas discharge port for discharging the refrigerant gas compressed by the impeller and the diffuser; And
A sealing member provided adjacent to the diffuser and having at least one second sealing portion protruding in a circumferential direction on an inner peripheral surface penetrating to receive the rotation shaft,
The impeller is provided in a pair and includes an impeller body coupled with the rotation shaft, and a plurality of blades formed on the impeller body with a gap with the shroud,
The first sealing portion is provided with a plurality of mutually spaced apart so as to contact the outer circumferential surface of the impeller body,
The material of the first sealing part is rubber,
The first sealing part protrudes in a direction perpendicular to the longitudinal direction of the rotation shaft, and has a sawtooth shape,
The second sealing portion has a serrated shape protruding in a direction perpendicular to the longitudinal direction of the rotation shaft,
The material of the second sealing part is rubber,
Ends of the first sealing part and the second sealing part are formed to be rounded,
The material of the first sealing part and the second sealing part is a material having a lower hardness than that of the rotating shaft and the impeller,
The diffuser includes a diffuser part for compressing the refrigerant gas discharged from the impeller,
A sealing pad is disposed between the inner surface of the diffuser part and the outer surface of the sealing member,
At least a portion of the sealing pad is disposed to overlap the diffuser in a horizontal direction,
The sealing pad is disposed to overlap the first sealing part and the second sealing part in a horizontal direction,
The shroud includes a plurality of channels obliquely disposed toward the diffuser in the rotation direction of the impeller,
The plurality of channels are disposed in a gas discharge region of the shroud adjacent to the diffuser,
The plurality of channels are disposed to be spaced apart from each other along the gas discharge direction,
The plurality of channels have an arc shape in a gas discharge direction,
The plurality of channels are recessed in the inner circumferential surface of the shroud,
The plurality of channels include a first channel, a second channel disposed behind the first channel, and a third channel disposed behind the second channel, based on a direction in which gas is discharged,
The length from the inner surface to the bottom surface of the shroud is that the second channel is formed longer than the first channel, and the third channel is formed longer than the second channel,
The channel has a trapezoidal cross-sectional shape, and an inclined surface having a smaller cross-sectional area toward the bottom is formed on the inner circumferential surface of the channel,
An inclined surface and a curved surface are formed on a surface of the impeller that faces the shroud,
On the inner surface of the shroud, a curved portion forming an edge and a plurality of flat portions disposed perpendicular to each other and in which the curved portion is disposed are formed on the inner surface of the shroud,
The inclined surface is disposed to face the flat portion, the curved surface is disposed to face the curved portion,
The gap between the wing and the shroud is formed to become smaller from the gas inlet to the gas outlet,
The inclined surface of the wing is formed so that the distance from the gas intake part to the gas discharge port becomes closer to the inner surface of the shroud,
The first interval formed between one end of the inclined surface and the inner surface of the shroud is 10 times the second interval formed between the end of the curved surface and the inner surface of the shroud,
The curved surface has a certain curvature, and a distance from the gas inlet to the gas discharge port is formed such that a distance from the gas inlet to the inner surface of the shroud becomes closer.
The method of claim 1,
The diffuser is penetrated to receive the impeller, and the turbocompressor is disposed radially outside the impeller.
The method of claim 1,
The sealing member is a turbo compressor coupled to the diffuser.
The method of claim 1,
A turbocompressor comprising a thrust bearing supporting the rotating shaft in an axial direction.
The method of claim 1,
A turbo compressor including a radial bearing supporting the rotation shaft in a radial direction.

Images