KR20210085704A - Compressor and turbo chiller having the same - Google Patents

Abstract

The present invention relates to a compressor having a refrigerant leakage reducing function, and a turbo refrigerator having the same. According to the present invention, the compressor comprises: a compressor body part; a support part; a rotating part disposed in a hollow of the support part and having a compression flow path formed therein; and an airtight part installed on the inner periphery of the front end of the hollow surrounding the outer periphery of the front end of the rotating part. The outer periphery of the rear end of the rotating part forms a gap with the inner periphery of the rear end of the hollow, and the inner periphery of the airtight part and the outer periphery of the front end of the rotating part are formed to correspond to each other in a concave-convex shape, so that the pressure difference between the inner periphery of both ends of an impeller, which is the rotating part, and the support part disposed to surround the inner periphery of both ends of the impeller is reduced, thereby minimizing the leakage of a refrigerant compressed and discharged.

Description

A compressor having a refrigerant leakage reduction function, and a turbo chiller having the same

The present invention relates to a compressor having a refrigerant leakage reducing function.

In general, an air conditioner is a device that cools or heats an indoor space.

The air conditioner includes a compressor compressing the refrigerant, a condenser condensing the refrigerant discharged from the compressor, an expander in which the refrigerant passing through the condenser expands, and an evaporator in which the refrigerant expanded in the expander is evaporated.

The turbo refrigerator includes a compressor that sucks in a low-pressure refrigerant and compresses it into a high-pressure refrigerant, a condenser, an expansion valve, and an evaporator, so that a refrigeration cycle can be driven.

The turbo refrigerator is provided with a centrifugal turbo compressor.

The turbocompressor converts kinetic energy generated from the driving motor into static pressure while discharging gas in a high-pressure state, and one or more impellers that rotate by the driving force of the driving motor to compress the refrigerant and the impeller are accommodated It may include a housing and the like.

A conventional turbocompressor includes a casing having a refrigerant inlet and a refrigerant outlet, a motor provided in the casing, a rotating shaft installed inside the casing and capable of being rotated by the driving force of the motor, and the motor and the rotating shaft by connecting the and a power transmission member for transmitting the driving force of the motor to the rotation shaft.

The compressor includes an impeller positioned inside the casing and rotatably provided by the rotation shaft.

The impeller includes a hub coupled to the rotation shaft 30 and a plurality of blades disposed on an outer circumferential surface of the hub to compress the refrigerant.

An impeller cover is disposed inside the casing to surround the impeller.

The refrigerant introduced through the refrigerant inlet flows into a space (or suction space) between the blade of the impeller and the impeller cover.

The impeller rotates together with the rotation shaft. While the impeller is rotating, the refrigerant is sucked into the suction space of the impeller and compressed, and the compressed refrigerant is discharged through the refrigerant outlet.

Referring to FIG. 10A , the center of the impeller 400 is connected to the rotation shaft. The impeller 400 is rotated by the rotation of the rotating shaft.

The outer diameter of the impeller 400 is formed to extend along the rear end from the front end. The refrigerant forms a flow path from the front end to the rear end of the impeller 400 .

A first support structure is disposed at the front end of the impeller 400 . The first support structure may be a diffuser. The diffuser guides the refrigerant to the blades of the impeller 400 .

A second support structure is disposed at the rear end of the impeller 400 . The second support structure may be part of another diffuser or compressor body.

The impeller 400 is disposed between the first and second support structures. Between the first and second support structures, a discharge passage through which the refrigerant compressed through the rotation of the impeller 400 is discharged is formed.

The first and second support structures each have a step that surrounds the outer periphery of the rear end of the impeller 400 .

Each of the steps is spaced apart from the outer periphery of the impeller 400 by a predetermined distance. That is, each of the steps prevents friction with the rotating impeller 400 .

Meanwhile, the outer periphery of the front end of the impeller 400 is spaced apart from the inner periphery of the hole formed in the first support structure.

A seal 500 is disposed between the outer periphery of the front end of the impeller 400 and the inner periphery of the hole. The inner periphery of the seal 500 is spaced apart from the outer periphery of the front end of the impeller 400 by a predetermined distance.

According to the structure, the refrigerant is introduced through the front end of the rotating impeller 400 and discharged along the discharge passage through the rear end. Here, the pressure of the refrigerant is formed higher than the front end at the rear end of the discharged impeller 400 .

That is, a pressure difference is generated between the front end and the rear end of the impeller 400 .

Accordingly, a predetermined amount of the refrigerant discharged along the discharge passage is leaked toward the front end of the impeller 400 through a gap formed between the step of the first and second support structures and the outer periphery of the rear end of the impeller 400 . Conventionally, there is a problem in that the cooling capacity is reduced according to the leakage of the refrigerant.

An object of the present invention is to reduce the pressure difference between the inner periphery of both ends of the impeller and the support arranged to surround the inner periphery of both ends of the impeller to minimize the leakage of the compressed and discharged refrigerant A compressor having a refrigerant leakage reduction function and having the same To provide a turbo chiller.

The object of the present invention is not limited to the above-mentioned object, and other objects and advantages of the present invention not mentioned can be understood by the following description, and will be more clearly understood by the examples of the present invention. Moreover, it will be readily apparent that the objects and advantages of the present invention may be realized by the means and combinations thereof indicated in the claims.

A compressor having a refrigerant leakage reduction function and a turbo refrigerator having the same according to the present invention include a compressor body having a refrigerant inlet at one end and a refrigerant outlet at the other end, and a driving unit having a drive shaft installed in the compressor body; A support portion disposed along the drive shaft, a hollow is formed and an inlet passage connected to the coolant inlet, and an outlet passage connected to the coolant outlet, a support portion is formed, connected to the drive shaft, and disposed in the hollow, the inlet passage And a rotary part having a compression flow path connected to the outlet flow path is formed, and an airtight part installed on the inner periphery of the front end of the hollow surrounding the outer periphery of the front end of the rotating part, wherein the outer periphery of the rear end of the rotating part forms a gap with the inner periphery of the rear end of the hollow And, the inner periphery of the airtight part and the outer periphery of the front end of the rotating part are formed to correspond to each other in a concave-convex shape, thereby reducing the pressure difference between the support parts arranged to surround the inner periphery of both ends of the impeller which is the rotating part and the inner periphery of both ends of the impeller, It is possible to minimize the leakage of the discharged refrigerant.

By the above solution, the present invention reduces the pressure difference between the inner periphery of both ends of the impeller, which is a rotating part, and the support portion disposed to surround the inner periphery of both ends of the impeller, thereby minimizing leakage of the compressed and discharged refrigerant.

Through this, the present invention can effectively prevent a decrease in the refrigeration capacity of the refrigerator by increasing the compression efficiency.

In addition to the above-described effects, the specific effects of the present invention will be described together while describing specific details for carrying out the invention below.

1 is a perspective view showing a refrigerator according to the present invention.
2 is a perspective view showing a compressor according to the present invention.
3 is a cross-sectional view showing a cross-section of a compressor according to the present invention.
4 is an enlarged cross-sectional view showing A of FIG. 3 .
5 is an enlarged cross-sectional view showing B of FIG. 3 .
6 is an enlarged cross-sectional view showing C of FIG. 3 .
7 is a cross-sectional view showing a coupling configuration of the airtight part and the rotating part according to the present invention.
FIG. 8 is an enlarged cross-sectional view showing D of FIG. 8 .
9 is a configuration diagram showing an arrangement relationship between first and second concavo-convex protrusions according to the present invention.
10A is a view showing a refrigerant flow between a conventional rotating part and a support part.
Figure 10b is a view showing the refrigerant flow between the rotating part and the support according to the present invention.
Figure 11a is a schematic view showing a conventional coupling relationship of the rotating part and the airtight part.
Figure 11b is a schematic view showing the coupling relationship of the rotating part and the airtight part according to the present invention.
12 is a graph showing a result of measuring a flow rate coefficient of a refrigerant through the configuration of FIGS. 11A and 11B.

The above-described objects, features and advantages will be described below in detail with reference to the accompanying drawings, and accordingly, those of ordinary skill in the art to which the present invention pertains will be able to easily implement the technical idea of the present invention. In describing the present invention, if it is determined that a detailed description of a known technology related to the present invention may unnecessarily obscure the gist of the present invention, the detailed description will be omitted. Hereinafter, preferred embodiments according to the present invention will be described in detail with reference to the accompanying drawings. In the drawings, the same reference numerals are used to refer to the same or similar components.

Although the first, second, etc. are used to describe various elements, these elements are not limited by these terms, of course. These terms are only used to distinguish one component from other components, and unless otherwise stated, the first component may be the second component, of course.

In the following, that an arbitrary component is disposed on the "upper (or lower)" of a component or "upper (or below)" of a component means that any component is disposed in contact with the upper surface (or lower surface) of the component. Furthermore, it may mean that other components may be interposed between the component and any component disposed on (or under) the component.

Also, when it is described that a component is "connected", "coupled" or "connected" to another component, the components may be directly connected or connected to each other, but other components are "interposed" between each component. It is to be understood that “or, each component may be “connected,” “coupled,” or “connected” through another component.

Throughout the specification, unless otherwise stated, each element may be singular or plural.

As used herein, the singular expression includes the plural expression unless the context clearly dictates otherwise. In the present application, terms such as "consisting of" or "comprising" should not be construed as necessarily including all of the various components or various steps described in the specification, some of which components or some steps are It should be construed that it may not include, or may further include additional components or steps.

Hereinafter, a compressor having a refrigerant leakage reducing function and a turbo refrigerator having the same according to some embodiments of the present invention will be described.

Here, the compressor according to the present invention is included in the refrigerator. The description of the compressor will be included in the description of the refrigerator.

1 is a perspective view showing a refrigerator according to the present invention.

Referring to FIG. 1 , the refrigerator of the present invention includes a compressor 1 , a condenser 2 , an economizer 4 , and an evaporator 5 . The refrigerator of the present invention achieves multi-stage compression.

The compressor 1 is composed of first and second compressors 1a and 1b. The first and second compressors 1a and 1b are respectively connected through a pipe 1c.

The rear end of the second compressor (1b) is connected to the condenser (2). The front end of the first compressor (1a) is connected to the evaporator (5). The condenser (2) is connected to the economizer (4). The economizer 4 is connected to a pipe connecting the first and second compressors 1a and 1b. Also, the economizer 4 is connected to the evaporator 5 .

The economizer 4 separates a gaseous refrigerant and a liquid refrigerant from the condensed refrigerant. The gaseous refrigerant is supplied to a pipe connecting the first and second compressors 1a and 1b. The liquid refrigerant is supplied to the evaporator (5).

Since the condenser 2, the economizer 4, and the evaporator 2 may be the same as described above, descriptions thereof will be omitted.

Accordingly, the first and second compressors 1a and 1b according to the present invention are connected in series. The configuration of the first and second compressors 1a and 1b is the same. Hereinafter, the first and second compressors 1a and 1b will be described as the compressor 1 with a unified name.

2 is a perspective view showing a compressor according to the present invention.

Referring to FIG. 2 , the compressor 1 according to the present invention has a compressor body 100 . A refrigerant inlet 101 is formed at the front end of the compressor body 100 . A refrigerant outlet 102 is formed in the central portion of the compressor body 100 . The evaporated refrigerant flows into the compressor 100 through the refrigerant inlet 101 . The refrigerant compressed to a predetermined pressure by the compressor 100 is supplied to the condenser 2 through the refrigerant outlet 102 .

The compressor 100 according to the present invention achieves multi-stage compression. Accordingly, the compressor 100 has three rotating parts 400 .

3 is a cross-sectional view showing a cross-section of a compressor according to the present invention.

2 and 3 , the compressor 1 according to the present invention has the above-described compressor body 100 . A first space a1 and a second space a2 are formed inside the compressor body 100 .

The driving unit 200 is disposed in the first space a1. The support part 300 and the rotating part 400 are disposed in the second space a1 .

The compressor 1 has the driving unit 200 . The driving unit 200 includes a driving motor 210 and a driving shaft 220 . The driving motor 210 is disposed at the rear end of the compressor body 100 . The driving shaft 220 is axially connected to the driving motor 210 . The driving shaft 220 is extended to be disposed in the second space (a2).

The support part 300 includes a first support part 301 , a second support part 302 , and a third support part 303 . The first, second, and third support parts 301 , 302 , and 303 are sequentially disposed along the driving shaft 220 .

The driving shaft 220 passes through the center of the first, second, and third support parts 301 , 302 , 303 . The first, second, and third support parts 301 , 302 , and 303 may have a structure having the same function as each other.

Representatively, the configuration of the first support part 301 will be described.

The first support part 301 has a support part body 310 in which a hollow 311 is formed. The inner diameter of the hollow 311 is formed to gradually expand from the front end to the rear end of the support body 310 .

An inflow passage 312 connected to the hollow 311 is formed at the front end of the support body 310 . An outlet flow path 313 connected to the hollow 311 is formed at the other end of the support body 310 . The hollow is integrally connected to the inflow passage and the outflow passage.

The inflow flow path 312 forms a flow path along a straight line. The outlet flow path 313 forms a flow path in a direction perpendicular to the driving shaft 220 .

Meanwhile, the hollow 311 includes a first surface 311a along a direction perpendicular to the driving shaft 220 at one end of the support body 310 and the driving shaft 220 at the other end of the support body 310 . It has a second surface 311b that is horizontal as a reference, and an inclined third surface 311c connecting the first surface 311a and the second surface 311b.

The third surface 311c forms an inclination extending along the other end from one end of the hollow.

Accordingly, the hollow 311 forms a space in the center of the support body 310 .

The support part 300 configured as described above includes a rotating part 400 . The rotating part 400 is an impeller having a plurality of blades formed on its outer periphery.

The rotating part 400 is disposed in the hollow of the support part 300 . The diameter of the rotating part 400 is gradually expanded from the front end to the rear end of the rotating part 400 .

The outer periphery of the rotating part 400 forms an inwardly concave inclination along the rear end from the front end of the rotating part 400 .

An empty space b of a certain volume is formed between the outer periphery of the rotating part 400 and the hollow inner wall.

And the front end of the rotating part 400 is arranged to rotate at the front end of the hollow (311). The outer periphery of the front end of the rotating part 400 and the inner periphery of the hollow front end of the support body 310 are spaced apart from each other. The front end of the rotating part 400 is formed in a shape along the same line as the first surface 311a.

The rear end of the rotating part 400 is disposed to rotate at the rear end of the hollow 311 . The rear end of the rotating part 400 is disposed along the same line as the second surface 311b.

The upper surface of the rear end of the rotating part 400 and the second surface 311b are spaced apart to form a predetermined gap (G).

The rotating part 400 has a compression flow path 410 . The compression flow path 410 connects the front end and the other end of the rotating part 400 . The compression passage 410 compresses the refrigerant flowing in according to the rotation of the rotating part 400 and discharges it to the outlet passage 313 . The compression flow path 410 follows 'a'.

The inlet of the compression passage 410 is connected to the inlet passage 312 . The outlet of the compression passage 410 is connected to the outlet passage 313 .

The airtight part 500 according to the present invention is installed on the inner periphery of the front end of the hollow 311 surrounding the outer periphery of the front end of the rotation unit 400 .

The inner periphery of the airtight part 500 is spaced apart from the outer periphery of the front end of the rotating part 400 .

4 is an enlarged cross-sectional view showing A of FIG. 3 . 5 is an enlarged cross-sectional view showing B of FIG. 3 . 6 is an enlarged cross-sectional view showing C of FIG. 3 .

It is an enlarged cross-sectional view showing the installation state of the airtight part 500 according to the present invention.

Referring to FIGS. 4 to 6 , the airtight part 500 according to the present invention has an airtight body 501 and first concavo-convex protrusions 510 protruding from the inner periphery of the airtight body 501 . The first concave-convex protrusions 510 are formed at intervals along the width of the airtight body 501 . The first concave-convex protrusions 510 are formed to protrude along the radial direction of the support body 310 .

The airtight body 501 is fitted and coupled to the hollow inner periphery of the support body 310 .

First grooves 511 are formed between the first concavo-convex protrusions 510 . The first concave-convex protrusions 510 are formed in a rectangular shape. The first grooves 511 are formed in a rectangular shape.

The first concave-convex protrusions 510 form a first interval s1 and a first protrusion length l1. The first grooves 511 form a first depth d1.

Meanwhile, the front end of the rotating part 400 is disposed in the hollow of the airtight part 500 .

The outer periphery of the front end of the rotating part 400 is spaced apart from the hollow inner periphery of the airtight member (500).

Second concave-convex protrusions 420 are formed on the outer periphery of the front end of the rotating part 400 . Second grooves 421 are formed between the second concave-convex protrusions 420 . The second concave-convex protrusions 420 are formed in a rectangular shape. The second grooves 421 are formed in a rectangular shape.

The second concave-convex protrusions 420 form a second interval s2 and a second protrusion length l2. The second grooves 421 form a second depth d2.

The first concave-convex protrusions 510 are disposed to face each of the second grooves 421 between the second concave-convex protrusions 420 .

The second concave-convex protrusions 420 are disposed to face each of the first grooves 511 between the first concave-convex protrusions 510 .

Accordingly, a zigzag flow path is formed between the outer periphery of the front end of the rotating part 400 and the inner periphery of the airtight body 501 .

On the other hand, the upper surface of the other end of the rotating part 400 according to the present invention is spaced apart from the inner periphery of the hollow 311 forming the above-described outlet flow path 313 by a predetermined distance. Accordingly, the other end of the compression flow path 410 formed in the rotating part 400 forms a flow path connected to the outlet flow path 313 . Here, the flow path is exposed to the space b between the inner wall of the hollow 311 of the rotating part 400 and the support body 310 through the gap (G).

The configuration of the support part 300 and the rotation part 400 described above may be the configuration of the first support part 301 and the first rotation part 401 disposed at the front end of the compressor body part 100 .

The second support part 302 and the second rotation part 402 according to the present invention may have the same configuration as the above-described first support part 301 and the first rotation part 401 . In addition, the third support part 303 and the third rotation part 403 may have the same configuration as the above-described first support part 301 and the first rotation part 401 . However, the first, second, and third support parts 301 , 302 , 303 are sequentially disposed along the driving shaft 220 direction, including the first, second, and third rotation parts 401 , 402 and 403 , respectively. In addition, the first, second, and third support parts (301, 302, 303) are non-rotatable, and the first, second, and third rotating parts (401, 402, 403) are configured to be rotated by being centrally connected to the driving shaft (220). . Accordingly, a description of the configuration of the second and third supporting parts 302 and 303 and the second and third rotating parts 402 and 403 will be omitted.

7 is a cross-sectional view showing a coupling configuration of the airtight part and the rotating part according to the present invention. FIG. 8 is an enlarged cross-sectional view showing D of FIG. 7 .

Referring to FIGS. 7 and 8 , the inner periphery of the airtight part 500 according to the present invention has first concavo-convex protrusions 510 forming a plurality of first grooves 511 .

The outer periphery of the front end of the rotating part 400 has second concave-convex protrusions 420 protruding to be located inside the plurality of first grooves 511 .

A plurality of second grooves 421 in which the first concave-convex protrusions 510 are positioned are formed between the second concave-convex protrusions 420 .

The first concave-convex protrusions 510 and the second concave-convex protrusions 420 are formed in a rectangular shape.

The inner periphery of the airtight part 500 has a first stepped surface 530 .

The inner diameter of the first stepped surface 530 forms a step that sequentially decreases along the front end from the rear end of the airtight body 501 .

The outer periphery of the front end of the rotating part 400 forms a second stepped surface 430 corresponding to the first stepped surface 530 . Accordingly, the inner diameter of the second stepped surface 430 forms a step that sequentially decreases from the rear end to the front end of the rotating part 400 .

The first and second step surfaces 530 and 430 form a predetermined gap.

Accordingly, the first concave-convex protrusions 510 according to the present invention are formed on the first stepped surface 530 . The first concave-convex protrusions 510 are formed at equal intervals along the width direction of the airtight body 501 . Of course, the interval between the first concave-convex protrusions 510 may be gradually densely formed along the front end from the rear end of the airtight body 501 .

The second concave-convex protrusions 420 according to the present invention are formed on the second stepped surface 430 . The second concave-convex protrusions 420 are formed at equal intervals along the width direction of the rotating part 400 . Of course, the interval between the second concave-convex protrusions 420 may be formed to be gradually denser along the front end from the rear end of the rotating part 400 .

On the other hand, the upper surface of the other end of the rotating part 400 according to the present invention is arranged to form a predetermined gap (G) with the inner wall of the hollow 311 of the support body 310 near the rear end of the hollow 311, that is, the outlet flow path 313. . Here, the upper surface of the other end of the rotating part 400 is parallel to the second surface 311b of the hollow 311 .

9 is a configuration diagram showing an arrangement relationship between first and second concavo-convex protrusions according to the present invention.

Referring to FIG. 9 , the first length l1 of the first concavo-convex protrusions 510 according to the present invention is formed to be a predetermined length longer than the second length l2 of the second concavo-convex protrusions 420 .

The ends of the first concave-convex protrusions 510 and the ends of the second concave-convex protrusions 420 are disposed on the same line.

A width W of each of the plurality of first grooves 511 and the plurality of second grooves 421 is formed to be the same as each other.

A width of each of the plurality of first grooves 511 is formed to be wider than a width of each of the second concavo-convex protrusions 420 .

Each of the first concavo-convex protrusions 510 is disposed at the center of each of the plurality of second grooves 421 .

Each of the second concavo-convex protrusions 420 is disposed at the center of each of the plurality of first grooves 511 .

A first depth d1 of each of the plurality of first grooves 511 forms a second depth d2 that is a predetermined depth deeper than a depth of each of the plurality of second grooves 421 .

The first and second concavo-convex protrusions 510 and 420 and the first and second grooves 511 and 421 are formed in a rectangular shape.

According to its configuration, a zigzag flow path is formed between the first concave-convex protrusions 510 and the second concave-convex protrusions 420 .

The flow path formed in the zigzag shape serves to prevent the refrigerant from flowing by increasing frictional force with the refrigerant.

The following describes the operation of the compressor having the above configuration. In the following description, reference will be made to FIGS. 1 to 9 for the configuration.

Referring to FIG. 2 , the refrigerant flowing from the evaporator 5 or the economizer 4 is introduced through the refrigerant inlet 101 .

The driving unit 200 rotates the driving shaft 220 . According to the rotation of the driving shaft 220, the first, second, and third rotation units 401, 402, 403 are rotated at a constant rotation speed. Here, the first, second, and third support parts 301 , 302 , 303 arranged to surround the first, second, and third rotating parts 401 , 402 , 403 are non-rotating.

10A is a view showing a refrigerant flow between a conventional rotating part and a support part. Figure 10b is a view showing the refrigerant flow between the rotating part and the support according to the present invention.

The refrigerant flows into the inlet of the compression passage 410 of the rotating part 400 through the inflow passage 312 of the first support part 301 . The refrigerant flowing into the compression passage 410 is compressed to a predetermined pressure by the centrifugal force of the rotating part 400 . The refrigerant flows along the compression passage 410 while being compressed. The flowing refrigerant flows out through the outlet of the compression passage 410 to the outlet passage 313 formed at the rear end of the hollow 311 of the support body 310 .

At this time, the first pressure is formed at the outlet of the compression passage 410 and the outlet passage 313 due to the outflow of the compressed refrigerant. And the pressure of the space between the outer periphery of the rotating part 400 and the inner space (b) of the hollow 311 of the support body 310 may be lower than the first pressure.

That is, a pressure difference may be generated between the inlet portion of the outlet passage 313 and the inner space b of the hollow 311 .

Accordingly, as shown in FIG. 10A , a gap formed between the upper surface of the rear end of the rotating part 400 and the second surface 311b forming the hollow 311 of the support body 310 forming the outlet flow path 313 ( A certain amount may leak into the hollow 311 inner space (b) through G).

Here, the outer periphery of the conventional rotating part 400 forms a planar shape. Accordingly, the refrigerant leaked into the hollow 311 leaks to the outside through a gap between the front end of the rotating part 400 and the airtight part 500 installed at the front end of the hollow 311 of the support part 300 .

On the other hand, as shown in Figure 10b, the outer periphery of the front end of the rotating part 400 according to the present invention and the inner periphery of the airtight body 310 through the first and second concavo-convex projections 510 and 420 to form a zigzag flow path do.

Accordingly, the refrigerant flowing into the zigzag flow path from the inner space (b) of the hollow 311 forms a frictional force greater than or equal to a certain level while passing through the first and second concavo-convex protrusions 510 and 420 . The amount of the refrigerant leaked to the outside through the zigzag flow path may be reduced by a predetermined amount.

That is, according to the present invention, the second pressure that may be similar to the above-described first pressure may be formed in the zigzag-shaped flow path.

In conclusion, as the first pressure and the second pressure are similarly formed, the difference between the first pressure and the hollow internal pressure may be reduced to a certain level or less.

Accordingly, the refrigerant flowing out to the outlet passage 313 through only the outlet of the compression passage 410 of the rotation unit 400 may not leak more than a certain amount into the inner space (b) of the hollow 311 through the above-described gap (G). have.

Figure 11a is a schematic view showing a conventional coupling relationship of the rotating part and the airtight part. Figure 11b is a schematic view showing the coupling relationship of the rotating part and the airtight part according to the present invention. 12 is a graph showing a result of measuring a flow rate coefficient of a refrigerant through the configuration of FIGS. 11A and 11B.

[Equation 1]

Equation 1 is an equation for calculating the flow coefficient when the pressure conditions of the inlet and outlet are the same.

where m: refrigerant leakage [kg/s], Cd: flow coefficient, A: area between impeller (rotating part) and seal (tight part), P: pressure, ρ: density, n: number of first and second concavo-convex projections .

13a shows a case in which the outer periphery of the rotating part 400 forms a flat surface, and a groove is formed on the inner periphery of the airtight body 501 .

In this case, it can be seen that 1.0 to 12.0 Cd are obtained as a result of calculation through Equation 1 as shown in FIG. 14 .

On the other hand, Figure 13b shows the above-described second concavo-convex protrusions 420 are formed on the outer periphery of the rotating part 400 and the first concave-convex protrusions 510 are formed on the inner periphery of the airtight body 501 to form a zigzag flow path show the case of formation.

In this case, it can be seen that 0.6 to 0.8 Cd is obtained as shown in FIG. 14 as a result of calculation through Equation 1 above.

Therefore, in the present invention, when the inlet and outlet pressure conditions are the same, when the Cd value is calculated based on the flow rate and pressure distribution calculated by flow analysis, the case in which the above-described zigzag flow path is formed is calculated as a lower value than when Cd is not. it can be seen that

That is, since it can be seen that the smaller the flow coefficient (Cd), the smaller the refrigerant leakage, so the example of the present invention can reduce the amount of refrigerant compressed and discharged through each rotating machine leaking through the front end of the rotating machine to a certain level or less. have.

According to the above configuration and action, the present invention reduces the pressure difference between the inner periphery of both ends of the impeller and the support portion disposed to surround the inner periphery of both ends of the impeller, thereby minimizing leakage of the compressed and discharged refrigerant.

Meanwhile, although not shown in the drawings, each of the second concavo-convex protrusions according to the present invention may be formed in pairs.

Each of the pair of second concavo-convex protrusions is disposed to correspond to one first groove.

Accordingly, the frictional force with the refrigerant that may be introduced through between the first and second concavo-convex protrusions may be increased to a certain level or more.

In addition, the pair of second concavo-convex protrusions disposed at positions corresponding to one first groove may have different heights. According to its configuration, the above-described frictional force may be further increased. This may induce the above-described first pressure and the second pressure to be similarly formed with a difference of less than a certain amount.

Also, an inclined surface may be formed on each of the second concave-convex protrusions according to the present invention.

The inclined surface is formed to be inclined along the rear end of the rotating part.

Accordingly, the refrigerant leaked into the hollow inner space by the inclined surface may physically limit the flow along the flow path formed between the first and second concavo-convex protrusions.

As described above, the present invention has been described with reference to the illustrated drawings, but the present invention is not limited by the embodiments and drawings disclosed in this specification, and various methods can be obtained by those skilled in the art within the scope of the technical spirit of the present invention. It is obvious that variations can be made. In addition, although the effects according to the configuration of the present invention are not explicitly described and described while describing the embodiments of the present invention, it is natural that the effects predictable by the configuration should also be recognized.

100: compressor body 101: refrigerant inlet
102: refrigerant outlet 200: driving unit
210: drive motor 220: drive shaft
300: support 310: support body
311: hollow 311a: first side
311b: second side 311c: third side
312: inflow flow path 313: outflow flow path
400: rotating part 410: compression flow path
420: second concavo-convex projection 421: second groove
500: airtight 501: airtight body
510: first concavo-convex projection 511: first groove
b: space
s1: first interval l1: first length
d1: first depth s2: second interval
l2: second length d2: second depth

Claims (15)

a compressor body having a refrigerant inlet formed at one end and a refrigerant outlet formed at the other end;
a driving unit having a driving shaft installed in the compressor body;
a support part disposed along the driving shaft, the hollow being formed and having an inflow passage connected to the refrigerant inlet and an outlet passage connected to the refrigerant outlet;
a rotating part connected to the drive shaft, disposed in the hollow, and having a compression flow path connected to the inflow flow path and the outflow flow path; and;
an airtight part installed on the inner periphery of the front end of the hollow surrounding the outer periphery of the front end of the rotating part; including,
The outer periphery of the rear end of the rotating part forms a gap with the inner periphery of the rear end of the hollow,
The inner periphery of the airtight part and the outer periphery of the front end of the rotating part are formed to correspond to the concavo-convex shape,
compressor.
The method of claim 1,
The inner periphery of the airtight part,
It has first concavo-convex projections forming a plurality of first grooves,
The outer periphery of the front end of the rotating part,
It has second concavo-convex protrusions protruding so as to be located inside the plurality of first grooves,
Between the second concavo-convex projections,
A plurality of second grooves in which the first concave-convex projections are located are formed,
compressor.
3. The method of claim 2,
The first concave-convex protrusions and the second concave-convex protrusions are formed in a rectangular shape,
compressor.
3. The method of claim 2,
The inner periphery of the airtight portion has a first stepped surface,
The outer periphery of the front end of the rotating part forms a second step surface corresponding to the first step surface,
compressor.
3. The method of claim 2,
The length of the first concave-convex projections is,
Formed to be a certain length longer than the length of the second concave-convex projections,
compressor.
6. The method of claim 5,
The ends of the first concave-convex protrusions and the ends of the second concave-convex protrusions are disposed on the same line with each other,
compressor.
3. The method of claim 2,
The plurality of first grooves and the plurality of second grooves each have the same width as each other,
compressor.
8. The method of claim 7,
The width of each of the plurality of first grooves,
Formed wider than the width of each of the second concave-convex projections,
compressor.
9. The method of claim 8,
Each of the first concave-convex projections,
disposed in the center of each of the plurality of second grooves,
Each of the second concave-convex projections,
disposed in the center of each of the plurality of first grooves,
compressor.
10. The method of claim 9,
The depth of each of the plurality of first grooves,
Formed deeper than the depth of each of the plurality of second grooves,
compressor.
3. The method of claim 2,
Each of the second concave-convex projections,
Formed in pairs in each of the plurality of first grooves,
compressor.
12. The method of claim 11,
Each of the second concavo-convex projections formed in pairs,
formed to achieve different heights,
compressor.
3. The method of claim 2,
An inclined surface is formed on each of the second concave-convex protrusions,
The inclined surface is
formed toward the inflow passage of the rotating part,
compressor.
a compressor body having a refrigerant inlet formed at one end and a refrigerant outlet formed at the other end;
a driving unit having a driving shaft installed in the compressor body;
a support part disposed along the driving shaft, the hollow being formed and having an inflow passage connected to the refrigerant inlet and an outlet passage connected to the refrigerant outlet;
a rotating part connected to the drive shaft, disposed in the hollow, and having a compression flow path connected to the inflow flow path and the outflow flow path; and;
an airtight part installed on the inner periphery of the front end of the hollow surrounding the outer periphery of the front end of the rotating part; including,
The outer periphery of the rear end of the rotating part forms a gap with the inner periphery of the rear end of the hollow,
The inner periphery of the airtight part and the outer periphery of the front end of the rotating part are formed to correspond to each other in a concave-convex shape,
The inner periphery of the airtight portion has a first concave-convex protrusion forming a plurality of first grooves,
The outer periphery of the front end of the rotating part has second concavo-convex protrusions protruding to be located inside the plurality of first grooves,
Between the second concave-convex protrusions, a plurality of second grooves in which the first concave-convex protrusions are located are formed,
The first concave-convex protrusions and the second concave-convex protrusions are formed in a rectangular shape,
The inner periphery of the airtight portion has a first stepped surface,
The outer periphery of the front end of the rotating part forms a second stepped surface corresponding to the first stepped surface,
The length of the first concavo-convex protrusions is formed to be a certain length longer than the length of the second concavo-convex protrusions,
The ends of the first concave-convex protrusions and the ends of the second concave-convex protrusions are disposed on the same line with each other,
compressor.
comprising the compressor of claim 1 or 14,
turbo chiller.

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