KR102239814B1 - Turbo Compressor - Google Patents

Abstract

An embodiment of the present invention relates to a turbo compressor. According to one aspect, the turbo compressor comprises: a case; a driving motor disposed in the case and having a driving shaft; an impeller mounted in the driving shaft to be rotated; a shroud disposed on an outer circumferential surface of the impeller and storing the impeller; and a diffuser disposed on a back surface of the impeller to convert kinetic energy of fluid discharged by rotation of the impeller into pressure energy.

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 is a device that sucks low-pressure fluid and compresses it into high-pressure fluid, and converts the kinetic energy of the fluid discharged by the rotation of the impeller and the impeller that rotates by the driving force of the driving motor into pressure energy. Includes a diffuser (Diffuser).

The diffuser is a device that most efficiently converts the velocity energy of air generated by the rotation of the impeller into pressure energy, and a vane is installed to guide the fluid that has passed through the impeller to the compression chamber. The vane is formed integrally with the diffuser on one side of the diffuser, and the vane angle is set according to the load of the compressor.

The most important design factor of the diffuser is the vane angle, and the design of the vane angle is determined by the shape of the compression chamber and the structural factor of the compressor.

Korean Patent Application Publication No. 10-2011-0109090 (published on Oct. 06, 2011)

The present invention is to provide a turbocompressor capable of improving the efficiency and performance of the compressor by allowing the vane angle of the diffuser to be adjusted according to the fluctuation of the load of the compressor.

In this embodiment, the turbo compressor includes: a case; A drive motor disposed in the case and including a drive shaft; An impeller mounted on the drive shaft and rotated; A shroud disposed on an outer circumferential surface of the impeller and accommodating the impeller; And a diffuser disposed on the rear surface of the impeller to convert kinetic energy of the fluid discharged by rotation of the impeller into pressure energy.

According to the present embodiment, there is an advantage in that the pressure of the gas can be increased while passing through the inlet flow path, and reverse flow in the direction opposite to the flow direction can be prevented.

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 plan view of a diffuser according to an embodiment of the present invention.
4 is a partial plan view showing a vane angle of a diffuser according to a load of a compressor according to an embodiment of the present invention.
Figure 5 is a partial cross-sectional view showing a vane angle adjustment unit according to an embodiment of the present invention.
6 is a partial plan view showing a vane angle adjustment unit according to an embodiment of the present invention.
7 is a partial perspective view of an impeller blade according to an embodiment of the present invention.
8 is a cross-sectional view showing a gap blocking member according to an embodiment of the present invention.
FIG. 9 is an enlarged view of A in FIG. 1;
10 is an enlarged view of B in FIG. 1;
11 is a cross-sectional view showing the operation of the sealing module according to the 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 exemplary embodiment of the present invention, and FIG. 2 is an enlarged view of a part of FIG. 1.

The turbo compressor according to the illustrated embodiment includes a case 10, a driving motor 20 installed inside the case 10, and an impeller 30 mounted on and rotated on a drive shaft 22 of the driving motor 20. Wow, the shroud 40 disposed on the outer circumferential surface of the impeller 30 to accommodate the impeller 30, and the kinetic energy of the fluid discharged by the rotation of the impeller 30 and installed at the rear of the impeller 30 It includes a diffuser (Diffuser) 50 that converts into energy.

One side of the case 10 is provided with a discharge port 12 through which the compressed fluid is discharged to the outside, and the shroud 40 is provided with a suction port 14 through which the external gas is sucked.

The impeller 30 is disposed with a certain gap on one surface of the diffuser 50, a hub 32 to which the drive shaft 22 is fixed, and a shroud formed at equal intervals in the circumferential direction of the hub 32. 40) It includes a rotating blade 34 that is disposed with a gap between the inner surface and generates a blowing force.

One side of the shroud 40 is connected to an inlet 14 through which gas is sucked, and an impeller 30 is disposed on the inner surface thereof with a predetermined gap, and the other side is disposed to face the diffuser 50, and the diffuser 50 ) To form a compression chamber 42 between them.

3 is a plan view of a diffuser according to an exemplary embodiment of the present invention, and FIG. 4 is a partial plan view showing a vane angle of the diffuser according to a load of a compressor according to an exemplary embodiment of the present invention.

The diffuser 50 is generally formed in a disk shape, and a diffuser body 52 having a through hole 56 through which the drive shaft 22 passes is formed in the center thereof, and one side of the diffuser body 52, that is, a shroud. It includes a vane 54 that is rotatably installed on a surface facing the 40 and guides the fluid, and a vane angle adjustment unit 60 that is installed on the diffuser body 52 and adjusts the angle of the vane according to the fluctuation of the compression load. do.

In addition, the case 10 is provided with a partition member 16 that divides the area where the driving motor 20 is installed and the area where the impeller 30 and the diffuser 50 are installed, and the partition member 16 A seating groove 18 is formed on one side so that the vane angle adjustment unit 60 is disposed.

The vane 54 allows the angle to be adjusted according to the fluctuation of the compression load. That is, the vane 54 is arranged to rotate within a set range on one surface of the diffuser body 52, and the vane angle adjustment unit 60 is provided on the diffuser body 52 to adjust the vane angle according to the change in compression load. do.

As an example, as shown in FIG. 4, when the compressor is under 100% load, the vane 52 is placed in the position A, which is the state that is maximally widened outward from the center. At this time, the vane angle θ1 becomes the maximum state.

In addition, when the compressor is partially loaded, the vane 52 is placed at the position B, which is the closest position to the center. At this time, the vane angle θ2 becomes the minimum state.

In this way, while the vane 52 rotates between the A position and the B position, the angle is adjusted in response to the load fluctuation.

5 is a partial cross-sectional view showing a vane angle adjusting unit according to an embodiment of the present invention, and FIG. 6 is a partial plan view showing a vane angle adjusting unit according to an embodiment of the present invention.

The vane 54 has a rotation shaft 62 fixed at one end thereof, and the rotation shaft 62 is rotatably supported in a hinge hole 64 formed of the diffuser body 52. That is, a hinge hole 64 formed through the diffuser body 52 is formed, and the rotation shaft 62 is rotatably supported in the hinge hole 64, and the other end of the rotation shaft 62 is fixed. It is fixed with a nut 66 or the like. In addition, a bushing 68 is installed between the inner circumferential surface of the hinge hole 64 and the outer circumferential surface of the rotation shaft 62 so that the rotation shaft 62 can be easily rotated.

The vane angle adjustment unit 60 is disposed on the other side of the diffuser body 52 and has one end of the rotating member 70 fixed to the rotating shaft 62, and the rotating member 70 and the rotating member 70 disposed at a predetermined interval. The third is installed between the stopper 72 integrally formed or fixed on the other side of the diffuser body 52 and the rotating member 70 and the stopper 72 to impart elasticity to the rotating member 70. It includes an elastic member 74.

The rotating member 70 and the vane 54 are connected by a rotating shaft 62 so that the rotating member 70 and the vane 54 rotate together.

Here, the third elastic member 74 is composed of a tension coil spring, and an elastic force is generated in the direction in which the rotating member 70 is opened. In addition, the elastic force of the third elastic member 74 is applied to the load of the compressor so that the rotating member 70 can be opened to the maximum when 100% load, and the rotating member 70 rotates within a set range when a partial load is applied. Depends on

Looking at the operation of the vane angle adjustment unit 60, when the load of the compressor is the minimum, that is, when the compression force is minimum, the rotating member 70 is disposed at the Q position. Then the vane angle is minimized.

And, when the load of the compressor is 100%, the rotating member 70 overcomes the elastic force of the third elastic member 74 by the force pushing the vane and moves to the R position, and accordingly, the vane angle is maximized. . In addition, while the rotating member 70 rotates within a predetermined range, it responds appropriately to the partial load of the compressor.

In this way, since the vane angle is appropriately adjusted according to the change in the load of the compressor, the performance and efficiency of the compressor can be maximized.

7 is a partial perspective view of an impeller blade according to an embodiment of the present invention, and FIG. 8 is a cross-sectional view showing a gap blocking member according to an embodiment of the present invention

The impeller blade 34 is formed to protrude in a curved shape from the surface of the impeller hub 32, and at one side of the impeller blade 34, a gap blocking member that blocks a gap between the impeller 30 and the shroud 40 660 is installed so as to be able to move up and down.

The impeller blade 34 is formed with a receiving groove 662 in which the gap blocking member 660 is accommodated along the longitudinal direction of the impeller blade 34, and the receiving groove 662 is opened on the upper side of the gap blocking member ( 660) protrudes to the outside.

The gap blocking member 660 according to an embodiment is formed of a plate having the same curved shape as the curved shape of the receiving groove 662 so that when the impeller 30 is rotated, it floats by centrifugal force and contacts the inner surface of the shroud 40 do. Then, the gap between the impeller 30 and the shroud 40 is blocked, thereby minimizing the leakage flow of the fluid.

The height of the gap blocking member 660 is equal to the depth of the receiving groove 662 or is formed larger than the depth of the receiving groove 662 so that it can protrude to the outside of the receiving groove 662.

Since the gap blocking member 660 rubs against the inner surface of the shroud 40, a material having excellent wear resistance is used. For example, it is formed of a Teflon material. In general, Teflon has an advantage of excellent wear resistance because it is strong against heat and has an extremely low coefficient of friction.

Meanwhile, an inclined surface 661 may be formed on one side of the gap blocking member 660. The inclined surface 661 may be disposed on one side of the gap blocking member 660 protruding outward from the receiving groove 662. When defining both protruding sides of the gap blocking member 660 as a front end and a rear end based on the rotation direction of the impeller 30, the inclined surface 661 may be disposed at the front end of the gap blocking member 660 . The inclined surface 661 may have a shape in which a linear distance to the other side surface becomes closer as the distance from the receiving groove 662 increases. Accordingly, frictional force with the shroud 40 may be reduced.

Looking at the action of the gap blocking member according to an embodiment of the present invention configured as described above, when the impeller 30 is rotated, a centrifugal force according to the rotation of the impeller 30 is generated, and by this centrifugal force, the gap blocking member 660 ) Rises from the receiving groove 662 to the outside and contacts the inner surface of the shroud 40.

Then, the gap blocking member 660 blocks the gap between the impeller 30 and the shroud 40, thereby minimizing the occurrence of leakage flow through the gap between the impeller 30 and the shroud 40 You can do it.

The rotational speed of the impeller 30 may be adjusted according to the load of the compressor. For example, the impeller 30 may have a first rotational speed and a second rotational speed that is faster than the first rotational speed. As an example, the second rotation speed may be a speed at which the impeller 30 rotates when the load of the compressor is 100%, and the first rotation speed may be a speed at which the impeller 30 rotates when the load of the compressor is minimum.

In this case, the gap blocking member 660 may protrude from the receiving groove 662 only at the second rotational speed. To this end, in the receiving groove 662, a first elastic member 665 having one end coupled to the bottom surface of the receiving groove 662 and the other end coupled to the lower end of the gap blocking member 660 may be disposed. The first elastic member 665 may be a compression spring having an elastic force to be compressed. By adjusting the elastic modulus of the first elastic member 665, the gap blocking member 660 may partially protrude from the receiving groove 662 or the upper end of the impeller blade 34 according to the rotation speed of the impeller 30. It may have a state that does not protrude forming the same plane as the upper surface.

In summary, when the load of the compressor is 100%, the vane 52 is in a state that is widest outward from the center, and the gap blocking member 660 is at least partially protruded to the outside of the receiving groove 662 so that the shroud It can block the gap formed with (40).

In addition, when the load of the compressor is a relatively low partial load or a minimum, the vane 52 is moved to a position close to the center, and a gap with the shroud 40 may be formed.

According to the structure as described above, by adjusting the inclination angles of the gap blocking member 660 and the vane 52 in consideration of the load of the compressor, it is possible to maximize the performance and efficiency of the compressor.

9 is an enlarged view of A in FIG. 1.

Meanwhile, a plurality of protrusions 47 may be disposed in the inlet passage 46 of the compression chamber 42. The protrusion 47 may protrude inward from the inner circumferential surface of the lead passage 46. A hole through which gas passes may be formed inside the protrusion 47.

The protrusion 47 includes a first protrusion 47a, a second protrusion 47b disposed inside the first protrusion 47a, and the second protrusion 47b based on the distance from the compression chamber 42. A third protrusion 47c disposed inside and a fourth protrusion 47d disposed inside the third protrusion 47c may be included.

The length protruding from the inner surface of the lead passage 46 is that the second protrusion 47b is formed longer than the first protrusion 47a, the third protrusion 47c is formed longer than the second protrusion 47b, and the second protrusion 47b is formed longer than the second protrusion 47b. The fourth protrusion 47d may be formed longer than the third protrusion 47c. Accordingly, the plurality of holes formed inside the plurality of protrusions 47 may be disposed to have a smaller diameter as they are closer to the compression chamber 42.

Accordingly, since the holes formed on the inner side of the protrusion 47 in the inlet flow path 46 are sequentially reduced in diameter, the pressure of the gas flowing into the compression chamber 42 may also be sequentially increased.

According to the structure as described above, there is an advantage in that the pressure of the gas can be increased while passing through the inlet flow path 46, and it can be prevented from flowing backward in the direction opposite to the flow direction.

10 is an enlarged view of B of FIG. 1, and FIG. 11 is a cross-sectional view showing the operation of the sealing module according to an embodiment of the present invention.

10 and 11, the turbo compressor may include a sealing module 100.

The sealing module 100 is inserted into a diffuser 50 to which the drive shaft 22 is inserted and fixed to the case 10, and is inserted in a free state on both outer inner circumferential surfaces of the diffuser 50 when the drive shaft 22 swings in the radial direction. A sealing member 120 that moves together while maintaining an allowable tolerance, and the sealing member 120 is inserted into the inner surface of the sealing member 120 opposite to the outer surface of the diffuser 50, and the gap with the diffuser 50 And a second elastic member 140 interposed between the tip seal member 130 and the diffuser 50 so that the tip seal member 130 maintains a certain air gap from the diffuser 50 Consists of

The diffuser 50 is formed in an annular shape, and its outer circumferential surface is fastened and fixed to the inner surface of the case 10, respectively, and among the outer surfaces opposite to the rear surface of each impeller 30, a sealing member ( A sealing member insertion groove 111 into which 120 is inserted so as to be swingable is formed.

The sealing member 120 is also formed in an annular shape, and a tip seal member insertion groove 121 into which the tip seal member 130 is slidably inserted is formed on an inner surface opposite to the outer surface of the diffuser 50, and the tip seal member A back pressure hole 122 in which a part of the compressed gas leaking from the compression chamber 42 from the inner peripheral surface of the insertion groove 121 to the rear surface of the impeller 30 pushes the tip chamber member 130 toward the opposite surface of the diffuser 50 A second elastic member mounting groove 123 is formed in the inside of the tip seal member insertion groove 122 (ie, in the center of the inner surface of the sealing member).

Here, it is preferable that a labyrinth seal 124 for reducing the pressure of the leakage gas is formed on an outer surface or an inner circumferential surface of the sealing member 120 serving as a flow path for the leakage gas.

The tip seal member 130 is made of a Teflon material and is formed in an annular shape, and the inner surface thereof is coupled to the inner surface of the sealing member insertion groove 111 of the diffuser 50, and the outer surface thereof is at the end of the back pressure hole 122. It is opposite to be coupled to the inner surface of the tip seal member insertion groove 121 of the sealing member 120.

When power is applied to the drive motor and the drive shaft 22 rotates at high speed, the impeller 30 fixed at both ends of the drive shaft 22 rotates together with the drive shaft 22 in the compression chamber 42, and refrigerant gas Is discharged to a condenser (not shown) by centrifugal compression in stages.

At this time, as the pressure on the discharge side of the compression chamber 42 becomes higher than the internal pressure of the motor chamber 12 as described above, a part of the compressed gas discharged from each compression chamber 42 is about to leak into the motor chamber, The compressed gas that is about to leak from the compression chamber 42 to the motor chamber passes through the labyrinth chamber 124 of the sealing member 120 and decreases in pressure, so that leakage into the motor chamber 12 is suppressed.

On the other hand, when the drive shaft 22 causes an abnormal operation such as a lateral swing due to an external shock or a change in condition, the sealing member 120 that has been extrapolated with a tolerance on the outer peripheral surface of the drive shaft 22 is removed from the diffuser 50 ) Inside the drive shaft 22 as much as the lateral displacement of the drive shaft 22 to prevent collision and abrasion between the drive shaft 22 and the sealing member 120. At this time, the tip seal member in the process of moving the sealing member 120 Although there is a risk that 130 may be lifted from the diffuser 50, the high-pressure leakage gas compressed into the back pressure hole 122 of the sealing member 120 flows to push the tip seal member 130, so that the tip seal member 130 ) And the air gap between the diffuser 50 is maintained.

In order to improve the pressing force to the tip seal member 130, the back pressure hole 122 may be formed in a shape in which the cross-sectional area becomes smaller as the distance to the tip seal member 130 is closer. That is, the inner surface of the back pressure hole 122 may include an inclined surface having a smaller cross-sectional area as the distance from the tip seal member 130 is closer.

Further, a plurality of ribs 59 protruding inward are formed on the inner surface of the diffuser 50 to which the sealing module 100 is coupled, so that it may contact the outer surface of the sealing member 120. Accordingly, not only the frictional force between the sealing member 120 and the diffuser 50 is increased, but also the leakage gas can be easily guided to the back pressure hole 122.

In addition, even if the entire outer surface of the sealing member 120 is pressed by the high-pressure compressed gas leaking from the compression chambers 13 and 14, between the inner surface of the sealing member 120 and the outer surface of the diffuser 50 Since the second elastic member 140 is interposed, the sealing member 120 can move freely in the transverse direction together with the drive shaft 22.

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)

case;
A drive motor disposed in the case and including a drive shaft;
An impeller mounted on the drive shaft and rotated;
A shroud disposed on an outer circumferential surface of the impeller and accommodating the impeller; And
It is disposed on the rear surface of the impeller, and includes a diffuser for converting the kinetic energy of the fluid discharged by the rotation of the impeller into pressure energy,
One side of the case is provided with a discharge port through which the fluid is discharged to the outside,
The shroud is provided with a suction port through which external gas is sucked,
The impeller includes a hub to which the drive shaft is fixed, and impeller blades formed at equal intervals in the circumferential direction of the hub,
The diffuser includes a diffuser body, a vane rotatably disposed on one surface of the diffuser body, and a third elastic member installed on the diffuser body, and the vane angle by the elastic force of the third elastic member according to a load It includes a vane angle adjustment unit for adjusting the,
The impeller blade is formed to protrude in a curved shape from the surface of the hub,
It is installed to be movable on the impeller blade, and includes a gap blocking member that contacts the inner surface of the shroud when the impeller rotates,
The impeller blade has a receiving groove in which the gap blocking member is accommodated along the length direction of the impeller blade,
The receiving groove has an upper side open so that the gap blocking member protrudes to the outside,
The gap blocking member includes a curved plate to correspond to the curved shape of the receiving groove,
The height of the gap blocking member is formed larger than the height of the receiving groove,
The material of the gap blocking member includes Teflon,
An inclined surface is disposed on one side of the gap blocking member protruding outward of the receiving groove,
Based on the rotation direction of the impeller, the inclined surface is disposed at the front end of the gap blocking member,
The inclined surface has a shape in which a linear distance to the other side of the gap blocking member becomes closer as the distance from the receiving groove increases,
The impeller includes a first rotational speed that is operated when the load is minimal, and a second rotational speed that is 100% of the load and is faster than the first rotational speed,
The length of the gap blocking member protruding to the outside of the receiving groove is formed longer at the second rotation speed of the impeller than at the first rotation speed of the impeller,
When the vane is at the second rotational speed of the impeller than at the first rotational speed of the impeller, the angle spread outward from the center is increased,
And a first elastic member coupled to a bottom surface of the receiving groove and a lower end of the gap blocking member,
The first elastic member is a compression spring,
A compression chamber is formed between the shroud and the diffuser,
A protrusion protruding inward from the inner circumferential surface is disposed in the inlet flow path of the compression chamber,
The protrusion includes a first protrusion based on a distance from the compression chamber, a second protrusion disposed inside the first protrusion, a third protrusion disposed inside the second protrusion, and an inner side of the third protrusion. Including a fourth protrusion disposed in,
The length protruding from the inner surface of the inlet flow path is that the second protrusion is formed longer than the first protrusion, the third protrusion is formed longer than the second protrusion, and the fourth protrusion is longer than the third protrusion. Is formed,
The hole formed inside the protrusion is formed to have a smaller diameter as it is closer to the compression chamber,
It includes a sealing member that is inserted in a free state on both outer inner circumferential surfaces of the diffuser and moves together while maintaining an allowable tolerance when the drive shaft is radially swung,
It includes a tip seal member inserted into the inner surface of the sealing member to maintain the air gap with the diffuser,
And a second elastic member interposed between the tip seal member and the diffuser so that the tip seal member maintains a predetermined air gap from the diffuser,
A sealing member insertion groove into which the sealing member is pivotably inserted is formed on an inner circumferential surface of the diffuser facing the drive shaft,
A tip seal member insertion groove into which the tip seal member is inserted is disposed on the inner side of the sealing member,
A back pressure hole is formed from the inner circumferential surface of the tip seal member insertion groove to the rear side of the impeller so that the compressed gas pushes the tip seal member toward the opposite surface of the diffuser,
A second elastic member mounting groove is disposed in a region of the inner surface of the sealing member that is spaced apart from the tip seal member insertion groove,
The tip seal member has an inner surface coupled to the inner surface of the sealing member insertion groove, and an outer surface of the tip seal member facing the end of the back pressure hole and coupled to the tip seal member insertion groove,
The back pressure hole is formed in a shape in which the cross-sectional area decreases as the distance to the tip seal member increases,
The inner surface of the back pressure hole is arranged with an inclined surface having a smaller cross-sectional area as the distance from the tip seal member is closer,
Includes a plurality of ribs protruding inward on the inner surface of the diffuser and contacting the outer surface of the sealing member,
The turbocompressor in which a direction in which the plurality of ribs protrude from an inner surface of the diffuser is perpendicular to a direction of providing an elastic force of the second elastic member.
The method of claim 1,
A turbo compressor provided with a labyrinth seal for reducing the pressure of the compressed gas on the inner circumferential surface of the sealing member.
The method of claim 1,
The first elastic member is a turbo compressor composed of a coil spring.
The method of claim 1,
The case is a turbocompressor including a partition member partitioning a region in which the driving motor is installed and a region in which the impeller and the diffuser are installed.
The method of claim 1,
The tip seal member is a turbo compressor made of Teflon.

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