• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention relates to a two-stage centrifugal compressor, and the conventional two-stage centrifugal compressors all compress the gas refrigerant in the internal space of the compressor (C) or the first compression part (C 1 ), and then the external refrigerant line (L 2 ). Refrigerant line other than the refrigerant line (L 1 ), which is an essential fluid passage of the centrifugal compressor, that is, a fluid passage for suction, compression, and discharge, because it is a fluid passage sucked into the second compression part (C 2 ) and compressed through the second compression portion (C 2 ). (L 3~ L 5) is added, and this reason there has been a problem that the pressure loss resulting from the complex, the overall refrigerant lines (L 1 ~L 5) of the compressor (C) and interrupting the flow of the refrigerant. The present invention is to solve this problem, the first and second compression parts of the two-stage centrifugal compressor to the outer body 13 to be made while going from one end of the outer body 13 to the other end continuously through the inner space thereof. A plurality of inner fluid passages 14 are formed at both ends of the upper and lower bearing housings 21a and 21b fixed to both ends of the outer body 13 to correspond to the inner fluid passages 14, respectively. A refrigerant fluid passage 213 is formed in circulation with the first and second compression chambers 31 and 32, and the second compression portion accommodates the inlet portion of the diffuser 27 in the compression casing 34. A second compression chamber 32 is formed surrounding the outer portion and having a coolant outlet 361, and a compressed chamber fluid circulated in correspondence with the coolant fluid passage 213 of the upper and lower bearing housings 21a and 21b. Two-stage centrifugal compressor characterized in that the inner cover 36 is formed with a passage (362) Provided.
    公开号:KR20000060408A
    申请号:KR1019990008664
    申请日:1999-03-15
    公开日:2000-10-16
    发明作者:서운종
    申请人:김평길；주식회사 삼진；
    IPC主号:
    专利说明:

    Two-stage centrifugal compressor
    The present invention relates to a two-stage centrifugal compressor suitable for a refrigeration cycle, and more particularly, to simplify the refrigerant fluid passage of the two-stage centrifugal compressor to cool the electric motor part by the refrigerant of the basic refrigeration cycle without any other cooler. The present invention relates to a two-stage centrifugal compressor capable of improving performance and efficiency.
    In general, a two-stage centrifugal compressor is mainly applied to a large cooling system, and as industrial technology develops, efforts are being made to miniaturize, simplify, and lightweight it.
    The two-stage centrifugal compressor related to this technique has Korean Patent Application No. 97-70572 (Application No. 96-45731) filed and filed by the applicant of the present application, and a number of preliminary applications are disclosed in Patent Applications No. 97-70882 to 70884. And 98-42812 to 98-42813.
    The core point of the prior art and the prior application is provided with an electric motor consisting of a rotor (Rotor) and a stator in the center portion of the outer body and having an impeller having a plurality of wings at both ends of the rotating shaft forming the rotor ( Impeller is fixed, and the impeller has first and second compression parts at both ends of the outer body.
    The two-stage centrifugal compressor is provided with a cooling fluid passage for cooling the refrigerant circulated along the main refrigerant line of the cooling cycle in the first and second compression parts and cooling the heat generated in the electric motor part to an optimum temperature.
    In the two-stage centrifugal compressor, the refrigerant is sucked from the evaporator of the cooling cycle, and the sucked refrigerant is first compressed in the first compression part and then secondly compressed in the second compression part, thereby becoming high temperature and high pressure. The gas refrigerant at high temperature and high pressure is supplied to the condenser of the cooling cycle.
    As described above, in order to circulate the cooling cycle by converting the refrigerant into a high pressure gas refrigerant, the electric motor needs to rotate at a high speed, thereby generating a lot of heat in the electric motor and its bearing part. At this time, the heat generated from the electric motor and its bearing portion not only degrades the performance of the centrifugal compressor but also affects reliability.
    Therefore, the technology for effectively cooling the electric motor and its bearing portion has emerged as an important problem, and to solve this problem, researches and developments of the cooling system and the refrigerant fluid passage of the electric motor have been conducted at various angles.
    An example of cooling the electric motor and its bearing portion in the conventional two-stage centrifugal compressor being developed as described above will be described with reference to the accompanying drawings.
    FIG. 1A illustrates the external refrigerant line L 2 after the gas refrigerant sucked along the refrigerant line L 1 from the evaporator of the cooling cycle is first compressed in the first compression part C 1 of the centrifugal compressor C. It is sucked into the second compression part (C 2 ) through the second compression and then discharged to the condenser of the cooling cycle, and the refrigerant jacket (L) by a separate cooling unit (CU) in the fixed jacket (M J ) of the electric motor part. There is one cycle through which refrigerant is circulated along 3 ).
    Figure 1b is compressed in two stages in the first and second compression portion (C 1 , C 2 ) through the refrigerant line (L 1 ) as shown in Figure 1a and the gas refrigerant sent to the condenser condensed and thus the liquid refrigerant While part of is sucked through the fixed jacket (M J ) of the electric motor (M) is evaporated while flowing through the internal space of the compressor and connected to the external refrigerant line (L 4 ) as one to the second compression portion (C 2 ) After being sucked in, it is compressed at a high pressure in the second compression part C 2 .
    Figure 1c is a gas refrigerant sucked along the refrigerant line (L 1 ) from the evaporator through the internal space of the compressor (C) to cool the electric motor (M) and then through the external refrigerant line (L 2 ) centrifugal compressor ( The first compression portion (C 1 ) of the C) is sucked into the first compression, and then again sucked into the second compression portion (C 2 ) through the external refrigerant line (L 2 ) and the second compression and then of the cooling cycle It is discharged to the condenser.
    FIG. 1D illustrates that the gas refrigerant sucked along the refrigerant line L 1 from the evaporator is compressed in the first compression part C 1 and then sucked into the second compression part C 2 through the external refrigerant line L 2 . After the second compression is discharged to the condenser of the cooling cycle, a separate refrigerant line (L 5 ) flowing the gas refrigerant separated from the gas-liquid separator of the cooling cycle is connected to the refrigerant line (L 2 ) through the internal space of the compressor A separate refrigerant line (L 4 ) through which the liquid refrigerant condensed in the condenser is connected to the cooling line (L 2 ) through the fixing jacket (M J ) of the electric motor.
    Figure 1e is a gas refrigerant sucked along the refrigerant line (L 1 ) from the evaporator is sucked into the first compression portion (C 1 ) of the centrifugal compressor (C 1 ) and then first compressed through the external refrigerant line (L 2 ) The electric motor is cooled while passing through the internal space of the compressor (C), and then the gas refrigerant separated from the gas-liquid separator of the cooling cycle is sucked into the second compression part (C 2 ) through the external refrigerant line (L 2 ). It is sucked into the second compression part C 2 through the refrigerant line L 5 and is compressed secondly and then discharged to the condenser of the cooling cycle.
    FIG. 1F illustrates a gas refrigerant sucked along the refrigerant line L 1 from the evaporator after being compressed in the first compression part C 1 , and then through the internal space and the external refrigerant line L 2 of the compressor C. The gas refrigerant separated from the gas-liquid separator of the cooling cycle while being sucked into the compression part (C 2 ) is sucked into the second compression part (C 2 ) through the refrigerant line (L 5 ), and is second compressed, and then discharged to the condenser of the cooling cycle. Will be.
    However, the conventional two-stage centrifugal compressors are all compressed again through the external refrigerant line L 2 after the gas refrigerant is compressed in the internal space of the compressor C or the first compression part C 1 . Refrigerant lines L 3 to L 5 other than the refrigerant line L 1 , which is an essential fluid passage of the centrifugal compressor, that is, a fluid passage for suction, compression, and discharge, because it is a fluid passage sucked into the portion C 2 and compressed. ) Was added.
    Therefore, the entire refrigerant line (L 1 ~ L 5 ) of the centrifugal compressor is complicated and the pressure loss is generated by disturbing the flow of the refrigerant, as a result, the performance of the compressor, as well as the assembly workability and productivity was deteriorated. .
    In addition, there is a problem that the manufacturing cost is increased by cooling with a cooling unit (CU) having a separate cycle from the cooling cycle for cooling the mechanical friction portion of the centrifugal compressor and the electric motor therein.
    An object of the present invention has been researched and developed in order to solve all the closed and problems of the prior art as described above, the gas refrigerant compressed in the first stage compression chamber of the first compression portion after passing through the inner space of the outer body By compressing in the second stage compression chamber at the end, the refrigerant fluid passage of the second stage centrifugal compressor is simplified, and the electric and gas bearing parts are cooled by the refrigerant of the basic refrigeration cycle without any other external cooler, and thus the power consumption of the two stage centrifugal compressor It is to provide a two-stage centrifugal compressor that can reduce the performance and improve the performance and efficiency of the entire system.
    1a to 1f are schematic diagrams schematically showing a two-stage centrifugal compressor according to the prior art,
    2 is a cross-sectional view showing a two-stage centrifugal compressor according to the present invention;
    Figure 3 is a perspective view showing only the fixed jacket in the two-stage centrifugal compressor of the present invention,
    Figure 4 is an exploded perspective view showing the upper and lower radial gas bearing portion in the present invention,
    Figure 5a is an exploded perspective view showing the lower body and the lower bearing housing in the present invention,
    5B is a bottom view of the parts assembled in FIG. 5A;
    5C is an exploded perspective view of a state in which the sealing housing and the diffuser portion are excluded from the second compression portion of the present invention;
    6 is an exploded perspective view showing the flow bearing portion of the present invention.
    * Description of the symbols for the main parts of the drawings *
    10: Electric motor 11: Rotor 12: Stator
    13: Outer body 14: Inner fluid passage 21a: Upper bearing housing
    21b: Lower bearing housing 22: Radial gas bearing 23: Thrust gas bearing
    23a: Space ring 23b: Fixed ring 23c: Upper gas bearing
    23d: Lower gas bearing 23e, 25a to 25c: Bolt 24: Outer ring
    24a, 238: Hinge hole 24b, 24d, 212: Set screw 24c, 211, 237: Screw tightening hole
    26: sealing housing 27: diffuser 31: first compression chamber
    32: second compression chamber 33, 34: compression casing 35: impeller
    36: inner cover 111: rotating shaft 112: rotor core
    113: color 121: coil 122: fixed jacket
    123: outer fluid passage 124: stator core 213: refrigerant fluid passage
    221: arc shaped piece 222: hemispherical groove 231: shaft through hole
    232: linear groove 233: fan groove 235: step
    236: through hole 331: refrigerant inlet 341: refrigerant outlet
    342: flash pipe 361: refrigerant outlet 362: compression chamber refrigerant passage
    The present invention is a stator fixed to the inner surface of the middle portion of the outer body to achieve the above object and the stator arranged a constant coil in the inner surface portion of the fixing jacket; A rotor core is formed on a rotation shaft opposite to the stator, and a motor supported by an upper / lower gas bearing is provided to enable high speed rotation of the upper and lower portions of the rotating shaft. In a two-stage centrifugal compressor having first and second compression parts including impellers respectively at upper and lower ends of the outer body to be wrapped, the first and second compression parts are disposed at one end of the outer body through the inner space and the other. A plurality of inner fluid passages are formed at both ends of the outer body so as to go to the end, and the upper and lower bearing housings fixed to both ends of the outer body have compression chamber fluid passages circulated with the first and second compression chambers in correspondence with the refrigerant fluid passages. It is characterized in that the two-stage centrifugal compressor.
    The second compression portion is formed in the compression casing to accommodate the inlet portion of the diffuser (Diffuser) to surround the outer portion of the compression chamber having a refrigerant outlet and the outer surface portion corresponding to the fluid passage of the upper and lower bearing housing It is a two-stage centrifugal compressor characterized in that the inner cover is formed with a circulation chamber fluid passage in circulation.
    Hereinafter, the specific features of the present invention will be more readily understood by explaining the present invention in detail with reference to the accompanying drawings.
    2 to 6 are diagrams for explaining the two-stage centrifugal compressor according to the present invention.
    Here, the electric motor 10 is installed in the middle of the outer body 13 to generate a rotational force, and the rotor 11 of the electric motor 10 can be rotated at a high speed at the upper and lower ends of the outer body 13. The upper and lower bearing parts supported by the dynamic gas bearings and the upper and lower ends of the outer body 13 of the electric motor 10 are respectively compressed to the first stage at the bottom and to the second stage at the top. It is largely composed of the first and second compression parts.
    The electric motor 10 has a rotor 11 to which the impellers 35 of the first and second compression parts are coupled to the upper and lower ends of the rotating shaft 111, and a stator for rotating the rotor 11 by an electromagnetic action. 12).
    The stator 12 of the electric motor 10 has the stator core 124 having the coil 121 wound around the inner surface portion thereof and is fixed to the outer surface portion thereof with the fixing jacket 122 wrapped therein. Forced to
    In the fixing jacket 122 of the stator 12, a plurality of outer surface fluid passages 123 are formed at regular intervals so that gas refrigerant flows along the inner surface of the outer body 13 as shown in FIG. The outer fluid passage 123 of the fixing jacket 122 may be formed on the inner surface of the outer body 13 without being formed on the fixing jacket 122.
    The rotor 11 of the electric motor 10 has a rotor core 112 formed on a rotation shaft 111 at a central position facing the stator 12, and a thrust gas bearing 23 is disposed below the rotation shaft 111. The collar 113 supported by the fluid bearing means including a is formed integrally.
    The outer body 13 is formed in a cylindrical shape in which the first and second compression parts are open while completely enclosing the electric motor 10 as shown in FIG. 5A, and a plurality of inner fluids arranged at regular intervals on the inner surfaces of the upper and lower end portions thereof. The passage 14 is formed.
    The upper and lower bearing parts are rotatably supported by radial gas bearings 22 inside the upper and lower bearing housings 21a and 21b, wherein both ends of the rotating shaft 111 are coupled to both ends of the outer body 13. A thrust gas bearing 23 rotatably surrounding the collar 113 of the rotating shaft 111 is fixed to a plurality of bolts 23e at a position close to the lower bearing part of the bearing part. The radial gas bearing 22 and the thrust gas bearing 23 are provided to rotate in a state where there is little mechanical friction when the rotating shaft 111 rotates.
    Meanwhile, the upper and lower bearing parts supporting the upper and lower ends of the rotating shaft 111 are illustrated in detail as shown in FIG. 4.
    The upper and lower bearing housings 21a and 21b of the upper and lower bearing parts are fixed to the upper and lower ends of the outer body 13 by a plurality of bolts 25a, which are fitted into the inner body at both ends of the outer body 13. Screw fastening holes 211 are formed on the outer surface at 120 ° intervals toward the center, and the set screws 212 supporting arc-shaped pieces 221 constituting the radial gas bearing 22 are formed in the screw fastening holes 211. Is fastened.
    In addition, an arc-shaped refrigerant fluid passage 213 is formed to be circulated in correspondence with the inner fluid passage 14 of the lower end of the outer body 13 when assembled to the upper and lower ends of the outer body 13. In the upper and lower bearing housings 21a and 21b, a sealing housing 26 and a diffuser 27, which form a boundary between the first and second compression chambers 31 and 32, are fixed by a plurality of bolts 25b. .
    The radial gas bearing 22 is formed such that three arc-shaped pieces 221 divided at 120 ° intervals form a cylindrical shape, and the arc-shaped pieces 221 are centered on the outer surface of the position slightly biased to one side from the center thereof. Hemispherical grooves 222 are respectively formed in the grooves.
    The radial gas bearing 22 of this configuration has three arc-shaped pieces 221 arranged to surround the rotating shaft 111, and the hemispherical grooves 222 of the arc-shaped pieces 221 have screws of the lower bearing housing 21a. The ends of the set screws 212 which are respectively fastened through the fastening holes 211 are fitted.
    The thrust gas bearing 23 supporting the collar 113 of the rotating shaft 111 and the fluid bearing means for receiving the same are shown in detail as shown in FIG. 6.
    The fluid bearing member accommodates the thrust gas bearing 23 supporting the collar 113 of the rotating shaft 111 at a position higher than the upper end of the lower bearing housing 21b, and the thrust gas bearing 23 within a predetermined range. It consists of an outer ring (24) rotatably supported while flowing freely from.
    The thrust gas bearing 23 has a space ring 23a which is covered on the outer side of the collar 113 of the rotating shaft 111, and upper and lower gas bearings 23c and 23d which are provided on the upper and lower surfaces of the space ring 23a. ) And a fixing ring 23b for fixing the components with bolts 23e.
    The upper and lower gas bearings 23c and 23d are arranged in pairs on the upper and lower surfaces of the space ring 23a, and the center through-hole 231 is centered on the surface in contact with the collar 113. A plurality of linear grooves 232 are formed radially, and the thin grooves 233 are formed in the linear grooves 232 so as to form a gas film in the rotational direction of the rotation shaft 111.
    The upper gas bearing 23c is divided into two pieces of semicircular shape in consideration of assembly workability, and has a stepped portion 235 as high as the height of the fixing ring 23b except for the outer edge portion of the semicircle. It is.
    At the edges of the upper and lower gas bearings 23c and 23d and the space ring 23a, a plurality of through holes 236 are formed on the same radius to fasten the collar 113 of the rotating shaft 111 with the bolt 23e. It is formed at equal intervals, and screwing holes 237 coupled to upper and lower gas bearings 23c and 23d and through holes 236 of the space ring 23a are formed at the edges of the fixing ring 23b. Formed.
    The outer ring 24 has two hinge holes 24a formed in a straight line across the center thereof so as to be supported while being rotated by two setscrews 24b fastened to the outer body 13 and the hinge holes ( A set screw 24d fitted into the hinge hole 238 of the spacer ring 23a is rotatably fastened to the straight screw fastening hole 24c intersecting the planes by 24 ° with the 24a. It is.
    Referring to the assembling process of the thrust gas bearing 23, the space ring 23a is first placed on the lower gas bearing 23d, and the bottom surface of the collar 113 of the rotating shaft 111 is the lower gas bearing 23d. The rotary shaft 111 is penetrated through the shaft through-hole 231 at the center thereof so as to be in contact with the upper surface. In this state, the space ring 23a is inserted outside the collar 113 of the rotating shaft 111 and the semicircular upper gas bearing 23c is fixed to the space ring 23a and the upper surface of the collar 113 by the fixing ring 23b. The assembly is completed by mounting together a plurality of bolts 23e from the top of the fixing ring 23b.
    The first and second compression parts are fixed to the upper and lower bearing housings 21a and 21b at both ends of the outer body 13, and the sealing housing 26 and the diffuser to the upper and lower bearing housings 21a and 21b. It is provided on its outer side sealed with 27, and has a plurality of wings at both ends of the rotating shaft 111 of the rotor 11 through the sealing housing 26 between the sealing housing 26 and the diffuser 27 The impeller 35 is fixed.
    The upper and lower bearing housings 21a and 21b and the outside of the diffuser 27 are fixed by a plurality of bolts 25c to cover the compression casings 33 and 34 constituting the first and second compression chambers 31 and 32. In the center of the compression casing 33, a refrigerant suction port 331 is formed, which is sucked by suction force generated by the rotation of the impeller 35, and the impeller 35 of the first and second compression parts is a diffuser. The wings are provided to face the diffuser 27 so as to be sucked through the inlet of the 27.
    One side of the compression casing 34 of the second compression portion has a refrigerant outlet 341 for discharging the high-pressure gas refrigerant to a condenser (not shown) forming a cooling cycle, and a gas-liquid separator (not shown) in the center thereof. The flash pipe 342 is connected to suck the gas refrigerant separated from the negative).
    Inside the compression casing 34 is provided with an inner cover 36 having a compression space for guiding the gas refrigerant sucked from the inner space of the outer body 13 and compressing the guided gas refrigerant as shown in Figure 5c, It accommodates the inlet portion of the diffuser 27 inside the compression casing 34 and surrounds the outer portion thereof, and a second compression chamber 32 having a refrigerant outlet 361 is formed, and the upper bearing housing 21b is formed on the outer surface portion thereof. Compression chamber fluid passage 362 is formed to flow in correspondence with the refrigerant fluid passage (213) of.
    The two-stage centrifugal compressor of the present invention configured as described above, when power is applied to the coil 121 wound on the stator 12 forming the electric motor 10, the magnetic field is sequentially generated according to the arrangement of the coil 121 The rotating shaft 111 of (11) is rotated. At this time, as the rotary shaft 111 is rotated, both ends thereof are arc-shaped pieces 221 constituting the radial gas bearing 22 in the upper / lower bearing housings 21a and 21b, respectively, on one set screw 212. Since it is supported by the eccentric state, it swings with the rotating shaft 111. FIG.
    Therefore, when the arc-shaped pieces 221 are rocked, gas refrigerant flowing into the electric motor 10 is sucked between the outer surface of the rotating shaft 111 and the inner surface of the arc-shaped pieces 221 to form a gas film.
    In this state, since the rotating shaft 111 reaches a certain number of revolutions, the arc-shaped pieces 221 are maintained in a static state, so that the rotating shaft 111 is floated at the center of the arc-shaped pieces 221 forming a circle, that is, the friction is almost It will rotate without it.
    At the same time, when the thrust gas bearing 23 of the lower bearing housing 21b shown in FIG. 6 is in contact with the lower surface of the collar 113 on the upper surface of the lower gas bearing 23d, the collar 113 is rotated. The gas refrigerant flowing into the electric motor 10 is sucked into the fan-shaped groove 233 through the straight grooves 232 of the lower gas bearing 23d to form a gas film. Therefore, the collar 113 of the rotating shaft 111 is rotated in a state in which it is floated in the center between the upper and lower gas bearings 23c and 23d, that is, there is little friction.
    Therefore, the rotation shaft 111 of the rotor 11 is the pressure difference between the pressure of the gas refrigerant first compressed in the first compression chamber (31) and the gas refrigerant compressed secondarily in the second compression chamber (32) and the rotor (11) 2) due to the total weight, the vibration of the rotating shaft 111 caused by a phenomenon such as being lowered toward the lower side or the initial rotation of the rotating shaft 111 in one direction is driven. It can be prevented.
    In addition, the two-stage centrifugal compressor of the present invention does not cause mechanical obstacles on the rotary shaft 111 of the electric motor 10 due to the radial and thrust gas bearings 22 and 23 as described above, thereby ensuring operational reliability of the device. It is possible to expect a smooth operation from low speed to ultra high speed rotation (3500 to 60000 rpm).
    As the rotation shaft 111 of the rotor 11 rotates at a high speed as described above, heat is inevitably generated in the electric motor 10. The heat generated in this way is the electric motor through the refrigerant refrigerant passage 213 and the inner fluid passage 14, the gas refrigerant compressed in the first compression portion of the lower end of the outer body 13 and circulated with the first compression chamber 31 10 is introduced into the inner space of the outer body 13 provided, the gas refrigerant introduced into the inner space of the outer body 13 is the stator 12 of the electric motor 10 and the rotor core of the rotor 11 ( The heat generated from the coil 121 of the stator 12 is taken away while passing through the air gap formed between the 112 and the outer fluid passage 123 of the outer surface of the fixing jacket 122 surrounding the stator 12. Cool 12).
    At the same time, the gas refrigerant introduced into the inner space of the outer body 13 includes radial gas bearings 22 inside the upper / lower bearing housings 21a and 21b, and a part of the gas refrigerant has a collar ( 113) Since it is sucked into the straight grooves 232 and the fan-shaped grooves 233 of the upper and lower gas bearings 23c and 23d from the upper and lower surfaces, the heat generated from the upper and lower bearing parts and the thrust gas bearing 23 is taken away. .
    In this way, the gas refrigerant compressed to the first stage in the first compression chamber 31 is connected to the refrigerant fluid passage 213 of the lower bearing housing 21b and the inner surface fluid passage 14 of the lower inner surface of the outer body 13 in contact with the refrigerant. Cooling while passing through the electric motor 10 as well as the upper / lower bearing portion installed in the inner space of the outer body 13 to prevent overheating due to the operation of the electric motor 10. Therefore, since the electric motor 10 is continuously cooled while driving, the electric motor 10 is always maintained in the optimum operating state.
    As the electric motor 10 is driven as described above, the impeller 35 at both ends thereof rotates at high speed together with the rotary shaft 111 of the rotor 11, and among them, the lower side is compressed by suction force due to the rotation of the impeller 35. The gas refrigerant flowing into the refrigerant inlet 331 of the casing 33 is compressed into one stage in the compression chamber 31 of the first compression part through the lower impeller 35 and the diffuser 27 of the compression casing 33. Will be.
    The gas refrigerant compressed to the first stage in the first compression chamber 31 is the outer body 13 through the refrigerant fluid passage 213 of the lower bearing housing 21 and the inner surface fluid passage 14 of the inner surface of the outer body 13. The refrigerant gas discharged into the inner space of the outer body 13 and passed into the inner space of the outer body 13 passes through the upper / lower bearing part and the electric motor 10, and then the inner surface fluid passage 14 of the inner surface of the outer body 13. And the refrigerant fluid passage 213 of the upper bearing housing 21 and the compression chamber fluid passage 362 of the inner cover 36 are discharged to the compression casing 34 of the second compression part.
    The gas refrigerant discharged into the compression casing 34 of the second compression part is compressed by the compression casing of the second compression part due to suction force generated as the impeller 35 inside the sealing housing 26 and the diffuser 27 rotates. 34) and through the inlet of the diffuser 27 and the impeller 35 in the second compression chamber 32 of the inner cover 36. The gas refrigerant compressed in two stages in the second compression chamber 32 of the inner cover 36 is discharged to the refrigerant outlet 341 of the second compression chamber 32 and the compression casing 34 of the inner cover 36. It is then supplied to a condenser (not shown) constituting a refrigeration cycle.
    As described in detail above, the two-stage centrifugal compressor of the present invention, unlike the prior art having a separate cooling line on the outside of the outer body, the gas refrigerant compressed in the first stage compression chamber of the first compression part is the inner space of the outer body. The simplification of the refrigerant fluid passage of the two-stage centrifugal compressor is continued by passing through the second stage compression chamber at the other end and the electric motor and the gas bearing part are cooled by the refrigerant of the basic refrigeration cycle without any other auxiliary cooler. Therefore, while reducing the power consumption of the two-stage centrifugal compressor there is a unique effect that can improve the performance and efficiency.
    权利要求:
    Claims (5)
    [1" claim-type="Currently amended] A stator 12 having a fixing jacket 122 fixed to an inner surface of a middle portion of the outer body 13 and having a coil 121 uniformly arranged on an inner surface portion of the fixing jacket 122; The rotor core 112 is formed on the rotary shaft 111 at the position opposite to the stator 12, and the upper and lower portions of the rotary shaft 111 can be rotated at high speed by radial and thrust gas bearings 22 and 23. An electric motor 10 is provided as a supported rotor 11, and first and second compression parts each including an impeller 35 are provided at upper and lower ends of the outer body 13 surrounding the electric motor 10. In the two stage centrifugal compressor,
    A plurality of inner fluid passages 14 are formed at both ends of the outer body 13 such that the first and second compression parts are continuously made from one end of the outer body 13 through the inner space to the other end. The upper and lower bearing housings 21a and 21b fixed to both ends of the outer body 13 are distributed with the first and second compression chambers 31 and 32 of the first and second compression parts corresponding to the inner fluid passage 14. Two-stage centrifugal compressor characterized in that the refrigerant fluid passage (213) is formed.
    [2" claim-type="Currently amended] The second compression chamber (32) according to claim 1, wherein the second compression portion (32) has an inlet portion of the diffuser (27) inside the compression casing (34) and surrounds its outer portion and has a refrigerant outlet (361). And an inner cover (36) having a compression chamber fluid passage (362) formed therein, the outer surface portion having a compression chamber fluid passage (362) corresponding to the refrigerant fluid passage (213) of the upper and lower bearing housings (21a, 21b). Centrifugal compressor.
    [3" claim-type="Currently amended] The inner cover (36) is provided with a compression casing (34) fastened with bolts (25c) at the ends of the outer body (13) to have a space between the upper end and the upper inner surface of the upper end of the compression casing (34). Two-stage centrifugal compressor characterized in that it is fixed.
    [4" claim-type="Currently amended] The two-stage centrifugal compressor according to claim 1 or 2, characterized in that the compression casing (34) of the second compression portion is provided with a gas pipe separator and a flash pipe (342) distributed in the cooling cycle.
    [5" claim-type="Currently amended] According to claim 1, wherein the outer surface of the fixing jacket 122 of the stator 12, the gas refrigerant compressed in the compression casing 33 of the first compression portion easily flows through the inner space of the outer body 13, the electric motor ( 10) a two-stage centrifugal compressor characterized in that a plurality of outer fluid passages (123) are formed to cool.
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    AU3460200A|2000-10-04|
    KR100288315B1|2001-04-16|
    WO2000055506A1|2000-09-21|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    法律状态:
    1999-03-15|Application filed by 김평길, 주식회사 삼진
    1999-03-15|Priority to KR1019990008664A
    2000-10-16|Publication of KR20000060408A
    2001-04-16|Application granted
    2001-04-16|Publication of KR100288315B1
    优先权:
    申请号 | 申请日 | 专利标题
    KR1019990008664A|KR100288315B1|1999-03-15|1999-03-15|Two-stage centrifugal compressor|
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