KR102131637B1 - A turbo compressor and a turbo chiller including the same - Google Patents

Abstract

Turbo compressor according to an embodiment of the present invention, a casing forming an inner space; A stator installed in the inner space of the casing; A rotor installed to rotate inside the stator; A rotating shaft coupled to the rotor and rotating; It is coupled to the rotating shaft is rotated, the impeller for compressing the refrigerant; A sleeve coupled to the outer side of the rotating shaft to surround the outer circumferential surface of the rotor; And at least one fixing pin inserted through the sleeve and the rotating shaft.

Description

A turbo compressor and a turbo chiller including the same}

The present invention relates to a turbo compressor and a turbo refrigerator comprising the same.

In general, an air conditioner is a device that cools or heats an indoor space. The air conditioner includes a compressor for compressing the refrigerant, a condenser for condensing the refrigerant discharged from the compressor, an expander for expanding the refrigerant passing through the condenser, and an evaporator for evaporating the refrigerant expanded in the expander.

The turbo freezer includes a compressor that sucks a low-pressure refrigerant and compresses it with a high-pressure refrigerant, and a refrigeration cycle can be driven by including a condenser, an expansion valve, and an evaporator.

The turbo refrigerator is provided with a centrifugal turbo compressor (hereinafter, a turbo compressor). The turbo compressor acts to discharge the gas in a high pressure state while converting the kinetic energy generated by the driving motor into a positive pressure, and one or more impellers, diffusers and the impellers that rotate to compress refrigerant by driving power of the driving motor Housing to be accommodated may be included.

Prior Art Japanese Patent Application Publication No. 2016-208724 (published date: December 8, 2016) discloses a technology related to a turbo compressor.

The turbo compressor disclosed in the prior art is a drive motor including a rotor including a rotating shaft and a cylindrical magnet installed on an outer peripheral surface of the rotating shaft, a sleeve installed to cover the outer peripheral surface of the cylindrical magnet, and a stator disposed on a circumferential side of the rotor. It includes. Accordingly, even if the driving motor rotates at a high speed, the magnet installed around the rotating shaft by the sleeve is prevented from being broken or damaged by centrifugal force.

However, the turbo compressor disclosed in the prior literature has the following problems.

First, in the conventional turbo compressor motor, a cylindrical magnet is installed on an outer circumferential surface of a rotating shaft, and a cylindrical magnet is fixed by heat-pressing a sleeve made of a thermosetting resin material on the outer circumferential surface of a cylindrical magnet. In this case, in order to securely fix the cylindrical magnet, the axial length of the sleeve was formed to be long, so there was a problem in that the axial length of the motor was increased.

That is, when the axial length of the rotating shaft is increased, the axial stiffness is deteriorated and vibration and noise due to rotation are increased, thereby causing difficulty in controlling the frequency of the motor.

Second, when the motor is operated at high speed, the coupling force between the rotating shaft or the cylindrical magnet and the sleeve (heat press-in) is weakened due to the heat generated by the rotor due to the vortex loss due to the non-magnetic material's sleeve intervention, so the sleeve is displaced from the inside of the cylindrical magnet or empty. There was a problem that the phenomenon of turning.

Japanese Patent Publication No. 2016-208724 (Publication Date: December 8, 2016)

The present invention has been proposed to improve the above problems, and an object of the present invention is to provide a turbo compressor including a turbo compressor and a turbo compressor capable of significantly reducing the axial length of a sleeve installed on a rotating shaft.

Another object of the present invention is to provide a turbo compressor including a turbo compressor and a turbo compressor that can prevent the rotor from being dislodged or rotated inside the rotating shaft by centrifugal force even during high-speed operation of the motor.

Another object of the present invention is to provide a turbo compressor and a turbo compressor including the same, which can effectively alleviate the heat generated by the rotor due to vortex loss when the motor rotates.

Another object of the present invention is to provide a turbo compressor and a turbo compressor including the same, which can maintain the performance of the motor as compared to the prior art even if the outer diameter of the rotating shaft is short.

Turbo compressor according to an embodiment of the present invention for achieving the above object, includes a casing, a stator, a rotor, a rotating shaft and an impeller.

At this time, to surround the outer circumferential surface of the rotor, it may include a sleeve coupled to the outside of the rotating shaft, and at least one fixing pin inserted through the sleeve and the rotating shaft. Therefore, the coupling force between the rotor and the rotating shaft is improved, and the axial length of the sleeve is minimized, thereby greatly reducing the overall length of the rotating shaft.

In addition, both ends of the fixing pin inserted through the sleeve and the rotating shaft may protrude outside the sleeve. At this time, a gap of a predetermined distance (L) is formed between the inner circumferential surface of the stator and the outer circumferential surface of the sleeve, and both ends of the fixing pin are located inside the void, so that the outside of the motor is formed with high pressure, and the motor Since a low pressure is formed in the inside, that is, the air gap, a fluid flow in which the fluid outside the motor flows into the air gap may be formed.

The rotating shaft may include a first shaft portion and a second shaft portion spaced apart from the first shaft portion in an axial direction, and the rotor may be disposed between the first shaft portion and the second shaft portion.

Further, the front surface of the rotor may contact the rear surface of the first shaft portion, and the rear surface of the rotor may contact the front surface of the second shaft portion. In addition, the center axis of the first shaft portion, the rotor, and the second shaft portion coincide with each other, so that an outer diameter length of the rotation shaft may be reduced.

In addition, the rotation shaft, the first shaft portion and the second shaft portion further includes a seating portion recessed radially inward at the outer circumferential surfaces, and the sleeve is inserted into the seating portion to cover the outer circumferential surface of the rotor. At this time, the sleeve is fixed to the inner surface of the seating portion by a heat-pressing method, so that the rotor may be prevented from being dislodged or rotated from the inside of the rotating shaft.

The fixing pin includes a plurality of fixing pins spaced apart from each other, and the rotor may be positioned between the plurality of fixing pins. At this time, the fixing pin may be formed of at least one of stainless steel or aluminum material.

In addition, the fixing pin may include a screw thread spirally wound along the outer circumferential surface, thereby further improving the coupling force between the rotating shaft and the sleeve.

The outer diameter D1 of the rotor may be formed smaller than the outer diameter D2 of the rotating shaft, and the outer diameter D1 of the rotor may be smaller than the outer diameter of the sleeve.

In addition, the axial length (L1) of the rotor is formed smaller than the axial length (L2) of the sleeve, the total length (L3) of the fixing pin may be formed larger than the outer diameter (D1) of the rotor. In addition, the entire length L3 of the fixing pin may be formed larger than the outer diameter D2 of the rotating shaft.

Further, according to the present invention, it is possible to provide a turbo refrigerator including the turbo compressor.

According to the turbo compressor according to the embodiment of the present invention constituting the above configuration and the turbo refrigerator including the same, there are the following effects.

First, by providing at least one fixing pin inserted through the rotating shaft and the sleeve of the motor, the coupling force between the rotating shaft and the sleeve is improved. Accordingly, since the axial length of the sleeve can be reduced, the axial length of the rotating shaft can be reduced as a whole. When the axial length of the rotating shaft is shortened, the axial stiffness is improved and vibration and noise are minimized, so that motor frequency control is easy.

Second, since both ends of the fixing pin inserted through the sleeve and the rotating shaft are exposed to the air gap formed between the inner circumferential surface of the stator and the outer circumferential surface of the sleeve, a high pressure is formed in the outer space of the motor and inside the motor, that is, the air gap Low pressure may be formed. Therefore, since air flow can easily occur from the outer space of the motor to the air gap, there is an advantage of effectively alleviating heat generated by rotation of the rotor.

Third, the rotor is interposed between the first shaft portion and the second shaft portion constituting the rotating shaft, and the seating portions on the outer peripheral surfaces of the first shaft portion and the second shaft portion are recessed, so that the rotor can be stably fixed and There is an advantage that the outer diameter length can be shortened.

Fourth, the sleeve is fixed to each seating portion of the first shaft portion and the second shaft portion by a heat-pressing method, so that the rotor may be prevented from being dislodged from the inside of the rotating shaft or swept.

Fifth, the fixing pin has a merit in that a coupling force between the rotating shaft and the sleeve is maximized by including a screw thread spirally wrapped along the outer circumferential surface.

1 is a cycle diagram showing the configuration of a turbo freezer according to an embodiment of the present invention.
2 is a view showing a partial configuration of a turbo freezer according to an embodiment of the present invention.
Figure 3 is a cross-sectional view showing the internal configuration of a turbo compressor according to an embodiment of the present invention.
4 is a sectional view showing a motor of a turbo compressor according to an embodiment of the present invention.
5 is a perspective view showing a fixing pin according to an embodiment of the present invention.
Figure 6 is an exploded view showing the order in which the rotating shaft and the rotor and the sleeve according to an embodiment of the present invention are assembled.
7 is a cross-sectional view showing a method in which the fixing pin is fastened to the rotating shaft according to the embodiment of the present invention.

Hereinafter, some embodiments of the present invention will be described in detail through exemplary drawings. It should be noted that, when adding reference numerals to the components of the drawings, the same components have the same reference numerals as possible even though they are displayed on different drawings. In addition, in describing embodiments of the present invention, when it is determined that detailed descriptions of related well-known configurations or functions interfere with understanding of the embodiments of the present invention, detailed descriptions thereof will be omitted.

In addition, in describing the components of the embodiments of the present invention, terms such as first, second, A, B, (a), and (b) may be used. These terms are only for distinguishing the component from other components, and the nature, order, or order of the component is not limited by the term. When a component is described as being "connected", "coupled" or "connected" to another component, the component may be directly connected to or connected to the other component, but another component between each component It should be understood that may be "connected", "coupled" or "connected".

Hereinafter, a turbo compressor according to an embodiment of the present invention and a turbo refrigerator including the same will be described in detail with reference to the drawings.

1 is a cycle diagram showing the configuration of a turbo freezer according to an embodiment of the present invention, and FIG. 2 is a view showing a partial configuration of a turbo freezer according to an embodiment of the present invention.

1 and 2, the turbo refrigerator 10 according to an embodiment of the present invention includes a compressor 100 for compressing a refrigerant and a condenser 20 for condensing the refrigerant compressed in the compressor 100 ), the first expansion valve 30 for primary decompression of the refrigerant condensed in the condenser 20, and an economizer for separating the liquid refrigerant and the gaseous refrigerant among the refrigerant decompressed in the first expansion valve 30 40, a second expansion device 50 for secondarily decompressing the liquid refrigerant separated from the economizer 40, and an evaporator 60 for evaporating the reduced pressure refrigerant in the second expansion device 50 Is included.

The gaseous refrigerant separated from the economizer 40 flows into the compressor 100 through the injection pipe 45. The injection pipe 45 extends from the economizer 40 to one side of the compressor 100, and the refrigerant of the injection pipe 45 is to be mixed with the refrigerant compressed in the first stage in the compressor 100. Can.

The compressor 100 may include a centrifugal turbo compressor. On the inlet side of the compressor 100, a suction pipe 115 is provided to guide the suction of the refrigerant evaporated from the evaporator 60. And, on the outlet side of the compressor 100, a discharge pipe 116 extending to the condenser 20 is provided.

Cooling water (W1) is introduced and discharged from the condenser 20, and the cooling water is heated by heat exchange with a refrigerant in the process of passing through the condenser 20. Then, cold water (W2) is introduced and discharged into the evaporator 60, and the cold water is cooled by heat exchange with a refrigerant in the process of passing through the evaporator 60.

The first expansion device 30 or the second expansion device 50 may include an electronic expansion valve (EEV) capable of adjusting the opening degree.

The compressor 100 includes a motor 120 that generates a driving force and a rotation shaft 125 that transmits the driving force of the motor 120 to the first and second impellers 131 and 141. The rotating shaft 125 connects the first and second impellers 131 and 141 with the motor 120. Therefore, the first impeller 131 and the second impeller 141 may be rotated together by the rotation of the rotation shaft 125.

The compressor 100 further includes a refrigerant suction part (not shown) communicating with the suction pipe 115 and a suction guide vane 106 provided on one side of the refrigerant suction part to guide the flow of the suction refrigerant.

The refrigerant that has passed through the suction guide vane 106 is first compressed while passing through the first impeller 131. The compressor 100 further includes a return channel 180 that guides the primary compressed refrigerant passing through the first impeller 131 toward the second impeller 141.

Therefore, the refrigerant compressed in the first impeller 131 may flow into the second impeller 141 via the return channel 180. In addition, the refrigerant compressed in the second impeller 141 may be introduced into the condenser 20 through the discharge pipe 116.

The turbo refrigerator 10 further includes a droplet supply pipe 70 for supplying the refrigerant condensed in the condenser 20 to the compressor 100. The refrigerant supplied through the droplet supply pipe 70 is in a condensed state, and may have a liquid. Further, the pressure P1 of the droplet refrigerant supplied through the droplet supply pipe 70 may be greater than the pressure P2 of the primary compressed refrigerant flowing through the return channel 180.

Therefore, by the pressure difference between P1 and P2, the refrigerant in the droplet supply pipe 70 can be easily supplied to the return channel 180.

The droplet supply pipe 70 may extend from the lower portion 22 of the condenser 20 to the housing 190 of the compressor 100. The housing 190 forms the appearance of the refrigerant suction side of the compressor 100. In the housing 190, a coupling portion 190a to which the droplet supply pipe 70 is coupled is formed.

The high pressure gaseous refrigerant compressed in the compressor 100 is phase-changed to a liquid phase in the process of being condensed in the condenser 20, and the liquid refrigerant is collected in the lower portion 22 of the condenser 20.

Then, the liquid refrigerant flows through the droplet supply pipe 70 and may be supplied to the compressor 100 through the housing 190. In this way, since the droplet supply pipe 70 extends from the lower portion 22 of the condenser 20, liquid refrigerant can be easily introduced into the droplet supply pipe 70.

3 is a cross-sectional view showing the internal configuration of a turbo compressor according to an embodiment of the present invention.

Referring to FIG. 3, the turbo compressor 100 according to the present embodiment includes a casing 110 forming an inner space, a motor 120 installed in the inner space of the casing 110, and the casing 110 ) May include a first compression unit 130 and a second compression unit 140 installed outside. The first and second compression units 130 and 140 and the motor 120 may be connected by a rotating shaft 125 to be described later.

In detail, the casing 110, the shell 111 is formed in a cylindrical shape with both ends open, coupled to each of both open ends of the shell 111, the front to shield the inner space of the casing 110 It may include a frame 112 and the rear frame 113.

The inner circumferential surface of the shell 111 is fixedly coupled to the stator 121 of the motor 120, which will be described later, and a shaft hole so that a rotation shaft 125, which will be described later, penetrates through the center of the front frame 112 and the rear frame 113. (112a, 113a) are formed respectively.

In the shaft hole 112a of the front frame 112 and the shaft hole 113a of the rear frame 113, radial bearings 151 and 152 for radially supporting the rotation shaft 125 may be respectively installed.

In addition, a first thrust bearing 153 may be coupled to the inner surface of the front frame 112, and a second thrust bearing 154 may be coupled to the inner surface of the rear frame 113.

Although not shown, the rotation shaft 125 has a first axial support plate (not shown) and a second axial support plate (not shown) to face the first thrust bearing 153 and the second thrust bearing 154, respectively. Each of these can be fixedly coupled.

Meanwhile, the motor 120 serves to generate power for compressing the refrigerant. The motor 120 may include a stator 121 generating magnetic force by the applied power, and a rotor 122 generating an induced electromotive force through interaction with the stator 121.

The stator 121 may be fixed by being pressed into the inner circumferential surface of the casing 110 or welded to the casing 110. The outer circumferential surface of the stator 121 is formed to be decut in a D-shape, and a passage through which the fluid can move may be formed between the inner circumferential surface of the casing 110.

The rotor 122 is located inside the stator 121 and is spaced apart from the stator 121. The rotor 122 is coupled to the rotating shaft 125 and can be rotated together with the rotating shaft 125. The rotor 122 may include an electromagnet or a permanent magnet.

A balance weight (not shown) for canceling the eccentric load generated by the first impeller 131 and the second impeller 141, which will be described later, may be coupled to both ends of the rotor 122 in the axial direction. However, the balance weight may not be installed on the rotor 122 and may be coupled to the rotating shaft 125.

In addition, the motor 120 may further include a rotating shaft 125 for transmitting the rotational force of the rotor 122 to the first impeller 131 and the second impeller 141 to be described later.

The rotating shaft 125 may be coupled to and fixed to both ends of the rotor 122. Therefore, the rotation shaft 125 receives the rotational force generated by the interaction between the stator 121 and the rotor 122, rotates together with the rotor 122, and this rotational force is with the first impeller 131. It is delivered to the second impeller 141 to suck and compress the refrigerant to discharge it.

However, unlike this, the rotating shaft 125 may be press-fit through the center of the rotor 122. In this case, the rotor 122 may be fixed to the outer peripheral surface of the rotating shaft 125.

On the other hand, the compression unit may be formed of a single compression unit to proceed with a single compression, but may be formed of a plurality of compression units to perform multi-stage compression as in this embodiment.

In addition, in the case of multi-stage compression, a plurality of compression units 130 and 140 may be installed on both sides of the casing 110 based on the motor 120, but the plurality of compression units 130 and 140 are the same as in this embodiment. It may be formed on both sides of the motor 120 as a reference.

Hereinafter, when a plurality of compression units are provided to compress a refrigerant in multiple stages, each of the first and second compression units will be described according to the order of compressing the refrigerant.

The first compression unit 130 and the second compression unit 140 are sequentially installed along an axial direction at one side of the casing 110. The first compression unit 130 includes a first impeller 131 and a first impeller housing 132, and the second compression unit 140 includes a second impeller 141 and a second impeller housing 142. It includes.

The first compression unit 130 and the second compression unit 140 may be coupled to each of the impellers 131 and 141 by being accommodated in each of the impeller housings 132 and 142. That is, the first compression unit 130 is the first impeller 131 is accommodated in the first impeller housing 132 is coupled to the rotating shaft 125, the second compression unit 140 is the first 2 impeller 141 is accommodated in the second impeller housing 142 may be coupled to the rotating shaft 125.

However, in some cases, the first impeller 131 and the second impeller 141 may be continuously arranged in one impeller housing and coupled to the rotating shaft.

A first impeller accommodation space 132a in which the first impeller 131 is accommodated is formed inside the first impeller housing 132. The suction pipe 115 is connected to one end of the first impeller housing 132 to form a first inlet 132b through which refrigerant is sucked from the evaporator 60, and the other end of the first impeller housing 132 is provided. A first outlet 132c for guiding the first stage compressed refrigerant to the second impeller housing 142 is formed.

The first impeller receiving space 132a may be formed in a closed shape except for the first inlet 132b and the first outlet 132c so as to fully accommodate the first impeller 131.

However, the present invention is not limited thereto, and may be formed in a semi-sealed shape in which the rear side of the first impeller 131 is opened and the opened side is sealed to the front side of the second impeller housing 142.

Between the first inlet 132b and the first outlet 132c, a first diffuser (133) is formed by being spaced apart by a predetermined distance from the outer circumferential surface of the wing portion (131b) of the first impeller (131), A first volute 134 is formed on the downstream side of the first diffuser 133.

In addition, the first inlet 132b may be formed at the center of one end in the axial direction of the first diffuser 133, and the first outlet 132c may be formed at the downstream side of the first volute 134. .

The first impeller 131 is composed of a first disk portion 131a coupled to the rotating shaft 125 and a plurality of first wing portions 131b formed in front of the first disk portion 131a. . The first disk portion 131a, a plurality of first wing portions 131b are formed in a conical shape on its front surface, but the rear surface may be formed in a flat shape to receive back pressure.

Here, a first backing plate (not shown) coupled to the rotating shaft 125 is provided at a predetermined distance behind the first disk portion 131a, and the first backing plate has an annular first sealing member. (Not shown) may be provided. Thus, a first back pressure space (not shown) in which a predetermined refrigerant is filled may be formed between the front surface of the second impeller housing 142 and the first back pressure plate at the rear of the first disk portion.

Meanwhile, a second impeller accommodation space 142a in which the second impeller 141 is accommodated is formed inside the second impeller housing 142. A second inlet 142b is formed at one end of the second impeller housing 142 to be connected to the first outlet 132c of the first impeller housing 132 to suck the compressed refrigerant of the first stage, and the second A second outlet 142c is formed at the other end of the impeller housing 142 to connect the two-stage compressed refrigerant to the condenser 20 by connecting the discharge pipe 116.

Between the second inlet 142b and the second outlet 142c, the second diffuser 143 is formed by being spaced apart by a predetermined distance from the outer circumferential surface of the wing 141b of the second impeller 141. 2 A second volute 144 is formed on the downstream side of the diffuser 143. And, the second inlet 142b is formed at the center of one end in the axial direction of the second diffuser 143, and the second outlet 142c can be formed at the downstream side of the second volute 144. have.

The second impeller 141 is composed of a second disc portion 141a coupled to the rotating shaft 125 and a plurality of second wing portions 141b formed in front of the second disc portion 141a. . The second disk portion 141a has a plurality of second wing portions 141b formed in a conical shape on its front surface, but the rear surface thereof may be formed in a flat shape to receive back pressure.

Here, a second back pressure plate 145 coupled to the rotating shaft 125 is provided at a predetermined distance behind the second disk portion 141a, and the second back pressure plate 145 has an annular shape 2 The sealing groove 145a is formed so that the second sealing member 146 may be inserted into the second sealing groove 145a.

As a result, a second back pressure space 147 in which a predetermined refrigerant is filled is formed between the second back pressure plate 145 and the front surface of the casing 110 at the rear of the second disk portion 141a. Then, as the portion of the refrigerant flowing into the second back pressure space 147 flows into the second sealing groove 145a and pushes up the second sealing member 146, the second sealing member 146 Is in close contact with the front of the front frame 112 to seal the second back pressure space 147.

In addition, the second back pressure space 147 is connected to a back pressure flow passage 171 to be described later, and the pressure of the second back pressure space 147 is connected to the back pressure flow passage 171 at the operating speed (ie, compression ratio) of the compressor. Accordingly, a back pressure regulating valve 173 may be installed to selectively open and close the back pressure flow path 171 so as to vary the pressure in the second back pressure space 147.

For example, the back pressure passage 171 may be formed through the interior of the second impeller housing 142 and the casing 110. That is, the first back pressure flow path 171a is formed inside the housing constituting the wall of the second impeller housing 142, and the first back pressure flow path inside the front frame 112 of the casing 110 ( A second back pressure flow path 171b communicating with 171a) may be formed.

However, in some cases, the back pressure passage 171 may be formed by assembling a separate valve frame provided with the back pressure passage 171 in front of the casing 110.

On the other hand, a valve space 172 having a predetermined depth in a radial direction is formed in the front frame 112 of the casing 110, and the valve space 172 slides in the valve space 172 and is described below. A back pressure regulating valve 173 for selectively opening and closing the 1 back pressure hole 172a and the second back pressure hole 172b is inserted, and the back pressure regulating valve is between the valve space 172 and the back pressure regulating valve 173. A valve spring 174 that elastically supports 173 may be installed.

The valve space 172 is formed to be recessed by a predetermined depth from the outer circumferential surface of the front frame 112 of the casing 110 to the inner circumferential surface, and the valve space 172 is disposed in the middle of the valve space 172. A first back pressure hole 172a communicating with the back pressure space 147 is formed. The first back pressure hole 172a may be formed to be smaller than or equal to the inner diameter of the valve space 172.

In addition, a second back pressure hole 172b may be formed on one side of the first back pressure hole 172a to communicate the valve space 172 with the inner space of the casing 110.

When the second back pressure hole 172b is inside the first back pressure hole 172a, that is, when the back pressure regulating valve 173 is opened by pressure, it receives a higher pressure than the first back pressure hole 172a. It may be formed to be located in the center more than the first back pressure hole (172a) to be opened.

However, in some cases, the second back pressure hole 172b is at the same position as the first back pressure hole 172a, that is, the first back pressure hole 172a and the second back pressure hole 172b are opened and closed at the same time. It may be formed, or may be formed outside the first back pressure hole (172a).

The back pressure regulating valve 173 may be formed of a ball valve or a piston valve. The back pressure regulating valve 173 may have three positions according to a difference between a force due to the pressure of the refrigerant flowing through the back pressure passage 171 and a force due to the elastic force of the elastic member.

That is, the back pressure regulating valve 173 has a first position in which both the first back pressure hole 172a and the second back pressure hole 172b are closed, the first back pressure hole 172a is opened, and the second back pressure hole 172b is It may be formed to have a closed second position and a third position in which both the first back pressure hole 172a and the second back pressure hole 172b are opened.

To this end, the valve spring 174 is made of a compression coil spring and may be installed between the inner surface of the back pressure regulating valve 173 and the valve space 172, and in some cases, the valve spring 174 It may be formed of a tension coil spring and may be installed between the outside of the back pressure regulating valve 173 and the valve space 172.

The turbo compressor 100 according to the present embodiment as described above may be operated as follows.

First, when power is applied to the motor 120, rotational force is generated by an induced current between the stator 121 and the rotor 122, and the rotational shaft 125 is the rotor 122 by the rotational force. Rotate with. Rotational force is transmitted to the first impeller 131 and the second impeller 141 by the rotating shaft 125, and the first impeller 131 and the second impeller 141 each have an impeller receiving space 132a, At 142a), it rotates simultaneously.

Then, the refrigerant that has passed through the evaporator 60 flows into the first impeller accommodation space 132a through the suction pipe 115 and the first inlet 132b, and this refrigerant is the first impeller 131. As it moves along the wing portion 131b, the static pressure rises and at the same time has a centrifugal force to pass through the first diffuser 133.

Then, the refrigerant that has passed through the first diffuser 133 is converted into kinetic energy by pressure energy by centrifugal force in the first diffuser 133, and the high-temperature and high-pressure refrigerant compressed by centrifugation is the first volute 134. Collected in and discharged through the first outlet (132c).

Then, the refrigerant discharged from the first outlet 132c is transferred to the second impeller 141 through the second inlet 142b of the second impeller housing 142, and the refrigerant is discharged from the second impeller 141. The static pressure rises again from the inside and at the same time passes through the second diffuser 143 with centrifugal force.

Then, the refrigerant that has passed through the second diffuser 143 is compressed to a desired pressure by centrifugal force, and the two-stage compressed high-temperature and high-pressure refrigerant is collected in the second volute 144 and the second outlet 142c. And a series of processes discharged to the condenser 20 through the discharge pipe 116 is repeated.

At this time, the first impeller 131 and the second impeller 141 are subjected to thrust pushed backward by the refrigerant sucked through the first inlet 132b and the second inlet 142b of each impeller housing 132,142. do. In particular, in the case of the second impeller 141, as the refrigerant compressed in one stage by the first impeller 131 flows through the second inlet 142b, a significantly large rear thrust is received.

The rear thrust is prevented by the first thrust bearing 153 and the second thrust bearing 154 provided inside the casing 110 so that the first impeller 131 and the second impeller 141 are It is suppressed to be pushed to the rear side with the rotating shaft 125.

4 is a cross-sectional view showing a motor of a turbo compressor according to an embodiment of the present invention, and FIG. 5 is a perspective view showing a fixing pin according to an embodiment of the present invention.

4 and 5, the motor 120 according to an embodiment of the present invention generates an induced electromotive force through interaction between the stator 121 generating magnetic force by the applied power and the stator 121. The rotor 122 may be included. In addition, the motor 120 may further include a rotating shaft 125 rotated according to the rotation of the rotor 122.

In detail, the stator 121 may be formed in a cylindrical shape with an empty interior. The stator 121 may be fixed by being pressed into the inner circumferential surface of the casing 110 or welded to the casing 110.

In addition, the rotor 122 and the rotating shaft 125 may be disposed inside the stator 121. The rotor 122 may be combined with the rotating shaft 125 and rotated together with the rotating shaft 125. A coil winding part in which the coil is wound may be formed on one side of the stator 121.

The rotor 122 is located inside the stator 121 and is spaced apart from the stator 121. The rotor 122 may be coupled to the rotating shaft 125 and rotated together with the rotating shaft 125.

For example, the rotor 122 may include an electromagnet or a permanent magnet formed in a cylindrical shape. At this time, the outer diameter D1 of the rotor 122 may be formed smaller than the outer diameter of the rotating shaft D2. In addition, the central axis of the rotor 122 may coincide with the central axis C of the rotation axis 125.

The rotating shaft 125 is coupled to the rotor 122 and rotates together with the rotor 122. A central axis of the first impeller 131 and the second impeller 141 may be coupled to one side of the rotating shaft 125. Therefore, the rotation shaft 125 may transmit the rotational force transmitted by the rotor 122 to the first impeller 131 and the second impeller 141.

In particular, in this embodiment, the rotation shaft 125 may be formed of a first shaft portion 125a and a second shaft portion 125b. That is, the rotation shaft 125 may be composed of a first shaft portion 125a positioned in front of the rotor 122 and a second shaft portion 125b positioned in the rear, based on the axial direction. In addition, the rotor 122 may be disposed between the first shaft portion 125a and the second shaft portion 125b.

At this time, the front surface 122a of the rotor 122 is in contact with the rear surface (rear end) of the first shaft portion 125a, and the rear surface 122b of the rotor 122 is the second shaft portion 125b It can be in contact with the front (front end) of the. That is, the rotor 122 may connect the first shaft portion 125a and the second shaft portion 125b. In addition, the first shaft portion 125a, the second shaft portion 125b, and the rotor 122 may be fixed together by a sleeve 127 to be described later.

In the first shaft portion 125a and the second shaft portion 125b, seating grooves 126a and 126b to which the sleeve 127 to be described later is seated may be formed, respectively.

The seating grooves 126a and 126b are recessed radially inward from the outer circumferential surface of the first shaft portion 125a and the first seating groove 126a recessed radially inward from the outer peripheral surface A second seating groove 126b may be included.

Specifically, the first seating groove 126a is formed by being recessed at the edge of the rear end of the first shaft portion 125a, and the second seating groove 126b is at the edge of the front end of the second shaft portion 125b. It can be formed by depression. At this time, the first seating groove 126a and the second seating groove 126b may have symmetrical shapes. In addition, a sleeve 127 to be described later may be inserted into the first seating groove 126a and the second seating groove 126b.

The turbo compressor 100 may further include a sleeve 127 installed on an outer circumferential surface of the rotating shaft 125.

The sleeve 127 is formed in a hollow cylindrical shape and is disposed to cover the circumference of the rotating shaft 125. At this time, the sleeve 127 may surround the outer circumferential surface of the rotor 122 provided inside the rotating shaft 125. That is, the rotor 122 is positioned inside the sleeve 127.

Further, the sleeve 127 may be inserted into the first seating groove 126a and the second seating groove 126b. At this time, both ends of the sleeve 127 may be supported by the first seating groove 126a and the second seating groove 126b, respectively. In addition, while the sleeve 127 is seated in the seating groove 126, the sleeve 127 may be shrink fit on the inner surface of the seating groove 126.

Therefore, the sleeve 127, the first shaft portion 125a, and the second shaft portion 125b can be fixed. In addition, since the rotor 122 positioned inside the sleeve 127 is also fixed, the phenomenon in which the rotor 122 is detached from the inside of the rotation shaft 125 or is lost can be prevented.

The outer diameter of the sleeve 127 may be formed to be the same as the outer diameter D2 of the rotating shaft 125. That is, when the sleeve 127 is inserted into the seating groove 126, the outer circumferential surface of the sleeve 127 and the outer circumferential surface of the rotating shaft 125 may be smoothly connected without a step.

However, the present invention is not limited thereto, and the outer diameter of the sleeve 127 may be formed smaller or larger than the outer diameter D2 of the rotating shaft 125.

In addition, the turbo compressor 100 may further include a fixing pin 128 penetrating the rotating shaft 125.

As illustrated in FIG. 5, the fixing pin 128 is elongated in a rod or rod shape, and is inserted through the rotating shaft 125. The fixing pin 128 may be inserted through the radial direction of the rotating shaft 125. At this time, the length of the fixing pin 128 in the extending direction, that is, the entire length D3, may be formed to be longer than the length of the outer diameter D2 of the rotating shaft 125.

In addition, the entire length L3 of the fixing pin 128 may be formed to be longer than the length of the outer diameter of the sleeve 127 coupled to the rotating shaft 125. Therefore, when the fixing pin 128 is inserted into the rotating shaft 125, both ends of the fixing pin 128 may be exposed outside the rotating shaft 125.

In particular, the fixing pin 128 penetrates the sleeve 127 disposed on the outer circumferential surface of the rotating shaft 125 together. That is, the fixing pin 128 may penetrate one side of the outer circumferential surface of the sleeve 127 and penetrate the other side of the outer circumferential surface of the sleeve 127.

However, the fixing pin 128 is penetrated by avoiding the rotor 122 located inside the rotating shaft 125. This reason is to minimize the influence on the magnetic flux density of the rotor 122 by the fixing pin 128.

The fixing pin 128 may be formed of a non-magnetic material capable of minimizing the influence on the magnetic flux density of the rotor 122. For example, the fixing pin 128 may be formed of at least one of stainless steel or aluminum.

In addition, the fixing pin 128 may be made of a plurality.

In one example, the fixing pin 128 is made of a pair, it may be coupled to the first shaft portion 125a and the second shaft portion 125b, respectively. In this case, one fixing pin 128 is inserted at a point close to the rear end of the first shaft portion 125a, and the other fixing pin 128 is a point close to the front end portion of the second shaft portion 125a. Can be inserted in.

At this time, the rotor 122 may be disposed between the pair of fixing pins 128. In addition, the pair of fixing pins 128 may be installed to correspond to the first shaft portion 125a and the second shaft portion 125b, respectively.

By the configuration of the fixing pin 128, the coupling force between the rotating shaft 125 and the sleeve 127 is improved, and accordingly, the sleeve 127 is prevented from being displaced or wandered inside the rotating shaft 125. Can be. In addition, since the sleeve 127 is thermally press-fitted inside the rotating shaft 125 to maintain a close contact, the rotor 122 may be prevented from being displaced or wandered inside the rotating shaft 125. have.

Therefore, even when the motor 120 rotates at a high speed, the rotor 122 and the sleeve 127 may be prevented from being scattered or shaken from the rotating shaft 125.

Meanwhile, the fixing pin 128 may include a cylindrical body portion 128a and a screw thread 128b formed in a spiral shape along the outer circumferential surface of the body portion 128a. That is, a screw 128b is additionally provided on the outer circumferential surface of the fixing pin 128, thereby further improving the fastening force between the rotating shaft 125 and the sleeve 128.

In addition, when the fixing pin 128 is inserted into the rotating shaft 125, both ends of the fixing pin 128 may be exposed to the outside of the rotating shaft 125.

In detail, since the entire length D3 of the fixing pin 128 is formed longer than the outer diameter D2 of the rotating shaft 125, the fixing pin 128 is provided on the rotating shaft 125 and the sleeve 127. When fastened, both ends of the fixing pin 128 may be exposed to the air gap 129 formed between the stator 121 and the rotating shaft 125.

Here, assuming that the distance between the inner circumferential surface of the stator 121 and the outer circumferential surface of the rotating shaft 125 or the sleeve 127 is "L", the fixing pin 128 exposed to the air gap 129 The end length (or distance) may be defined as "L/2". That is, the fixing pin 128 may be exposed by a distance L/2 corresponding to at least half or more with respect to the gap L of the gap 129.

According to this configuration, since the fixing pin 128 is interposed into the gap 129 between the stator 121 and the sleeve 127, the inlets on both sides of the gap 129 may be relatively narrow.

Then, when the motor 120 is rotated, a high pressure is formed in the outer space of the motor 120, and a low pressure is formed in the inner space of the motor 120, that is, the air gap 129. Air flow from the outside of the motor 120 to the inside (air gap) may occur. When air flow occurs, heat generated by rotation of the motor 120 may be effectively alleviated. Accordingly, even if the motor 120 rotates at a high speed, it can be prevented that the temperature of the rotor 122 increases rapidly.

Hereinafter, a method of assembling a rotating shaft, a rotor, and a sleeve according to an embodiment of the present invention will be described in detail with reference to the drawings.

6 is an exploded view showing a sequence in which a rotating shaft and a rotor and a sleeve are assembled according to an embodiment of the present invention, and FIG. 7 is a cross-sectional view showing a method in which a fixing pin is fastened to a rotating shaft according to an embodiment of the present invention.

Referring to FIGS. 6 and 7, a seating groove 126 formed in the first shaft portion 125a in a state where the first shaft portion 125a and the rotor 122 that form part of the rotation shaft 125 face each other. Insert the sleeve 127 in.

Specifically, after aligning and aligning the center of the rear surface of the first shaft portion 125a with the center of the front surface 122a of the rotor 122, the sleeve 127 is inserted into the seating groove 126. Then, the front surface of the second shaft portion 125b is inserted into the rear surface 122b of the rotor 122.

Then, the front end and the rear end of the rotor 122 are fixed by the first shaft portion 125a and the second shaft portion 125b, and the circumference of the rotor 122 is covered by the sleeve 127.

In this state, the sleeve 127 is thermally pressed into the inner surface of the seating groove 126. That is, when heat is applied while the sleeve 127 is assembled, the inside of the sleeve 127 may be thermally bonded to the first shaft portion 125a and the second shaft portion 125b.

Then, after machining the threads on each outer circumferential surface of the pair of pins 128, the pair of pins 128 are fastened through the radial direction of the rotating shaft 125.

In detail, one fixing pin 128 is fastened to penetrate the outer circumferential surface of the sleeve 127 corresponding to the first shaft portion 125a. At this time, the rotor 122 is avoided and fastened so that the fixing pin 128 does not penetrate the rotor 122.

And the other fixing pin 128 is fastened to penetrate the outer peripheral surface of the sleeve 127 corresponding to the second shaft portion (125b). In this case, the rotor 122 is avoided and fastened so that the fixing pin 128 does not penetrate the rotor 122.

When the pair of fixing pins 128 are fastened to both the sleeve 127 and the rotating shaft 125, the sleeve 127 and the rotating shaft 125 are firmly fixed by the fastening force of the fixing pin 128. Can. Then, even when the motor 120 is rotated at a high speed, the rotor 122 or the sleeve 127 may be prevented from being displaced or wandered inside the rotating shaft 125.

In addition, in the state in which the fixing pin 128 is inserted into the rotating shaft 125, both ends of the fixing pin 128 are exposed to the outside of the rotating shaft 125.

In detail, since the entire length D3 of the fixing pin 128 is formed longer than the outer diameter D2 of the rotating shaft 125, the fixing pin 128 is provided on the rotating shaft 125 and the sleeve 127. When fastened, both ends of the fixing pin 128 may be exposed to the air gap 129 formed between the stator 121 and the rotating shaft 125.

That is, both ends of the fixing pin 128 are exposed by a length corresponding to at least half of the gap between the inner circumferential surface of the stator 121 and the outer circumferential surface of the sleeve 127.

Claims (18)

A casing forming an inner space;
A stator installed in the inner space of the casing;
A rotor installed to rotate inside the stator;
A rotating shaft coupled to the rotor and rotating;
It is coupled to the rotating shaft is rotated, the impeller for compressing the refrigerant;
A sleeve coupled to the outer side of the rotating shaft to surround the outer circumferential surface of the rotor; And
And at least one fixing pin inserted through the sleeve and the rotating shaft,
Between the inner circumferential surface of the stator and the outer circumferential surface of the sleeve, a gap of a predetermined distance (L) is formed,
Both ends of the fixing pin, the turbo compressor is located inside the air gap. According to claim 1,
A turbo compressor protruding outwardly of the sleeve, both ends of the fixing pin inserted through the sleeve and the rotating shaft. delete According to claim 1,
The rotating shaft includes a first shaft portion and a second shaft portion spaced apart from the first shaft portion in an axial direction,
A turbo compressor in which the rotor is disposed between the first shaft portion and the second shaft portion. The method of claim 4,
The front surface of the rotor is in contact with the rear surface of the first shaft,
The rear of the rotor, the turbo compressor in contact with the front of the second shaft portion. The method of claim 4,
A turbo compressor according to claim 1, wherein a central axis of the rotor and the second shaft portion coincide with each other. The method of claim 6,
The rotating shaft further includes a seating portion recessed radially inward from each outer circumferential surface of the first shaft portion and the second shaft portion,
The sleeve is inserted into the seating portion, the turbo compressor surrounding the outer peripheral surface of the rotor. The method of claim 7,
The sleeve, the turbo compressor, characterized in that fixed to the inner surface of the seating portion by a heat press. According to claim 1,
The fixing pin includes a plurality of fixing pins spaced apart from each other,
Turbo compressor, characterized in that the rotor is located between the plurality of pins. According to claim 1,
The fixing pin is a turbo compressor, characterized in that formed of at least one of stainless steel or aluminum material. According to claim 1,
The fixing pin, the turbo compressor, characterized in that it comprises a thread that is spirally wrapped along the outer peripheral surface. According to claim 1,
The outer diameter (D1) of the rotor, the turbo compressor is formed smaller than the outer diameter (D2) of the rotating shaft. According to claim 1,
The outer diameter (D1) of the rotor, the turbo compressor is formed smaller than the outer diameter of the sleeve. According to claim 1,
The axial length (L1) of the rotor, the turbo compressor is formed smaller than the axial length (L2) of the sleeve. According to claim 1,
The overall length (L3) of the fixing pin, the turbo compressor is formed larger than the outer diameter (D1) of the rotor. According to claim 1,
The overall length (L3) of the fixing pin, the turbo compressor is formed larger than the outer diameter (D2) of the rotating shaft. A turbo refrigerator comprising the turbocompressor according to any one of claims 1, 2, 4 to 16. A casing forming an inner space;
A stator installed in the inner space of the casing;
A rotor installed to rotate inside the stator;
A rotating shaft coupled to the rotor and rotating;
It is coupled to the rotating shaft is rotated, the impeller for compressing the refrigerant;
A sleeve coupled to the outer side of the rotating shaft to surround the outer circumferential surface of the rotor; And
And at least one fixing pin inserted through the sleeve and the rotating shaft,
The rotating shaft includes a first shaft portion and a second shaft portion spaced apart in the axial direction from the first shaft portion,
The rotor is disposed between the first shaft portion and the second shaft portion,
The fixing pin, the turbo compressor to avoid the rotor to fasten the sleeve and the rotating shaft.

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