Turbo compressor

Abstract

A turbo compressor comprises a rotary shaft including a rotor; a first impeller coupled to one side of the rotary shaft, a thrust bearing runner coupled between the first impeller and the rotary shaft, an impeller sleeve compressed and coupled between the first impeller and the thrust bearing runner, a second impeller coupled to the other side of the rotary shaft, and a tie rod passing through the first impeller and a thrust bearing and fastened to the rotary shaft.

Claims

1. A turbo compressor, comprising: a rotary shaft comprising a rotor and a groove formed at a first side of the rotary shaft; a first impeller provided at the first side of the rotary shaft such that a base of the first impeller faces the groove; a thrust bearing runner provided between the first impeller and the rotary shaft; a second impeller provided at a second side of the rotary shaft opposite to the first side, the second impeller having a smaller maximum diameter than a maximum diameter of the first impeller; and a tie rod having an outer diameter that is smaller than an inner diameter of the groove, wherein a first end of the tie rod is coupled through the groove to face an inner end of the groove in an axial direction of the rotary shaft and a second end of the tie rod is coupled to a fastening nut, and wherein when the fastening nut is tightened while the thrust bearing runner and the first impeller are inserted between the first side of the rotary shaft and the fastening nut, the tie rod is tensioned, and the first impeller and the thrust bearing runner are compressed and coupled.

2. The turbo compressor of claim 1, further comprising a coupling sleeve provided between the first impeller and the thrust bearing runner.

3. The turbo compressor of claim 2, wherein the first impeller and the thrust bearing runner comprise coupling shafts configured to be inserted into the coupling sleeve so as to couple the first impeller and the thrust bearing runner.

4. The turbo compressor of claim 3, wherein outer diameters of the coupling shafts are equal to or greater than an inner diameter of the coupling sleeve such that the coupling shafts are coupled to the coupling sleeve by press fitting.

5. The turbo compressor of claim 4, wherein a sum of lengths of the coupling shafts inserted into the coupling sleeve is smaller than a length of the coupling sleeve such that the coupling shafts do not contact each other before thea preload is applied.

6. The turbo compressor of claim 1, wherein: an end of the rotary shaft at the second side comprises a first section, a second section having an outer diameter greater than an outer diameter of the first section, and a stepped surface between the first and second sections; the second impeller includes a base plate; and the first and second sections are provided inside of and coupled to the second impeller such that the stepped surface contacts the base plate.

7. The turbo compressor of claim 6, wherein a preload is applied to the first and second sections of the rotary shaft by coupling a fastening bolt to the first section of the rotary shaft at a side of the second impeller that is opposite to a side having the base plate.

8. The turbo compressor of claim 1, wherein the rotor is provided at a center of the rotary shaft and protrudes radially outward.

9. The turbo compressor of claim 1, wherein the tie rod is made of a stainless steel material and has a deformation in a range of 7 to 25 μm.

10. The turbo compressor of claim 2, wherein the coupling sleeve has a concavo-convex shape.

11. The turbo compressor of claim 10, wherein the coupling sleeve is made of a labyrinth seal.

12. The turbo compressor of claim 3, wherein the rotary shaft further includes a coupling groove provided at an end of the groove, and wherein an inner diameter of the coupling groove is larger than an inner diameter of the groove.

13. The turbo compressor of claim 12, wherein the thrust bearing runner further includes a shaft that extends opposite to the coupling shaft of the thrust bearing runner, and wherein the shaft is coupled to the coupling groove.

14. The turbo compressor of claim 13, wherein an outer diameter of the shaft of the thrust bearing runner is equal to or larger than the inner diameter of the coupling groove, and wherein the shaft of the thrust bearing runner is inserted into the coupling groove to couple the shaft of thrust bearing runner to the coupling groove of the rotary shaft by press fitting.

15. The turbo compressor of claim 14, wherein a length of the shaft of the thrust bearing runner inserted into the coupling groove is smaller than a depth of the coupling groove such that a compressive force is applied between the thrust bearing runner and the first side of the rotary shaft by a preload applied to the tie rod.

16. A turbo compressor, comprising: a rotary shaft comprising a rotor; a first impeller and a second impeller coupled to opposite sides of the rotary shaft and having rear surfaces facing each other so as to have a back-to-back configuration, the first impeller having a larger maximum diameter than a maximum diameter of the second impeller; a thrust bearing runner coupled to the rear surface of the first impeller; and a tie rod configured to be coupled to the rotary shaft when a preload is applied to the first impeller and the thrust bearing runner, wherein a first end of the tie rod is coupled through a groove formed at a first side of the rotary shaft such that the first end of the tie rod faces an inner end of the groove in an axial direction of the rotary shaft and a second end of the tie rod is coupled to a fastening nut, and wherein when the fastening nut is tightened while the thrust bearing runner and the first impeller are inserted between an end of the first side of the rotary shaft and the fastening nut, the tie rod is tensioned, and the first impeller and the thrust bearing runner are compressed and coupled.

Description

DESCRIPTION OF DRAWINGS

(1) FIG. 1 shows a cross section of a turbo compressor according to related art.

(2) FIG. 2 shows a rotary shaft of a turbo compressor according to related art.

(3) FIG. 3 shows a cross section of a turbo compressor the related art.

(4) FIG. 4 shows a cooling ring of a turbo compressor the related art.

(5) FIG. 5 shows a rotary shaft of a turbo compressor according to a first embodiment of the present disclosure.

(6) FIG. 6 is an enlarged view showing a coupling portion between a rotary shaft of a turbo compressor and a thrust bearing runner according to a first embodiment of the present disclosure.

(7) FIG. 7 is an enlarged view showing a coupling portion of a rotary shaft of a turbo compressor and a second impeller according to a first embodiment of the present disclosure.

(8) FIG. 8 is a graph showing deformation of stainless steel (SUS 304) material with respect to stress.

(9) FIG. 9 is a graph showing relation between deformation and a coupling force of a tie bolt.

(10) FIG. 10 is a configuration diagram showing a turbo compressor according to a second embodiment of the present disclosure.

(11) FIG. 11 is a configuration diagram showing a turbo compressor according to a third embodiment of the present disclosure.

(12) FIG. 12 is a configuration diagram showing a turbo compressor according to a fourth embodiment of the present disclosure.

(13) FIG. 13 is a configuration diagram showing a turbo compressor according to a fifth embodiment of the present disclosure.

(14) FIG. 14 is a configuration diagram showing a turbo compressor according to a sixth embodiment of the present disclosure.

(15) FIG. 15 is a configuration diagram showing a turbo compressor according to a seventh embodiment of the present disclosure.

BEST MODE

(16) Hereinafter, example embodiments of the present disclosure will be described in detail with reference to the accompanying drawings. Reference now should be made to the drawings, in which the same reference numerals are used throughout the different drawings to designate the same or similar components. A detailed description of a well-known configuration or function relating to the present disclosure may be omitted if it unnecessarily obscures the gist of the present disclosure.

(17) In some examples, terms such as first, second, A, B, (a), (b) and the like may be used herein when describing elements of the present disclosure. These terms are intended to distinguish one element from other elements, and the essence, order, or sequence of corresponding elements are not limited by these terms. It should be noted that if it is described in the present disclosure that one component is “connected,” “coupled” or “joined” to another component, the former may be directly “connected,” “coupled” or “joined” to the latter or “connected,” “coupled” or “joined” to the latter via another component.

(18) A turbo compressor is an example of a centrifugal compressor and compresses gas based on a centrifugal force generated by rotating an impeller in a casing.

(19) The turbo compressor suctions gas in an axial direction using a rotational force of the impeller and then discharges the gas in a centrifugal direction to perform a compression operation. A two-stage compression turbo compressor has been used as an example of the turbo compressor.

(20) A number of stages of the turbo compressor may be determined based on a number of impellers, and the turbo compressor may be classified into a back-to-back type turbo compressor or a face-to-face type turbo compressor according to an arrangement of impellers.

(21) In the back-to-back type turbo compressor, rear or base surfaces of the impellers face each other. In the face-to-face type turbo compressor, suction ends of the impellers face each other.

(22) The turbo compressor according to an embodiment of the present disclosure described below is a two-stage, back-to-back type turbo compressor including two impellers having rear surfaces facing each other.

(23) FIG. 5 shows a rotary shaft of a turbo compressor according to a first embodiment of the present disclosure.

(24) FIG. 6 is an enlarged view showing a coupling portion between a rotary shaft of a turbo compressor and a thrust bearing runner according to a first embodiment of the present disclosure.

(25) An important factor for miniaturizing the turbo compressor is a first bending mode of the rotary shaft. The rotary shaft rotates at a high speed and is operated under high-pressure conditions, and if the rotary shaft is in the first bending mode within a range of operating speed, reliability of operation may not be obtained.

(26) In order for the rotary shaft to be suitable for high-speed operation, the rotary shaft may have a relatively short length and a relatively larger diameter to facilitate rigidity. However, there is a limitation in that there is difficulty in increasing a diameter of the shaft because a Diameter Nominal (DN) number, which is a design limit of the bearing, has to be considered with respect to the diameter of the shaft.

(27) The present disclosure provides a structure of the turbo compressor to obtain a force that couples two impellers and the thrust bearing runner to the rotary shaft.

(28) Referring to FIGS. 5 and 6, the turbo compressor according to a first embodiment of the present disclosure includes a rotary shaft 100 having a rotor 105, a thrust bearing runner 120 provided at one side of the rotary shaft 100, a first impeller 140 provided outside the thrust bearing runner 120, a tie rod 160 to couple the first impeller 140 and the thrust bearing runner 120 to the rotary shaft 100 by applying a preload to the tie rod 160, and a second impeller 180 coupled to the other side of the rotary shaft 100.

(29) The second impeller 180 may have an outer diameter that is relatively smaller than that of the first impeller 140.

(30) In other words, the thrust bearing runner 120 may be close to the impeller having the relatively large diameter (i.e., the first impeller 140).

(31) As the diameter of the first impeller 140 increases, axial load applied to the rear surface of the first impeller 140 increases. The thrust bearing runner 120 is provided at the rear or base surface of the first impeller 140 having the relatively large diameter to effectively support the rotation of the first impeller 140.

(32) The rear surface of the first impeller 140 may mean a right surface in FIG. 5, or a surface at an end of the first impeller 140 having a base plate or a surface at an end of the first impeller 140 having a diameter greater than a remaining portion of the first impeller 140. As embodiments disclosed herein provide a back-to-back turbo compressor in which rear surfaces of impellers face each other, the rear surface of the second impeller 180 may mean a left surface in FIG. 5, or a surface facing the rear surface of the first impeller 140. If a front-rear direction of the turbo compressor is defined as a direction from the first impeller 140 to the second impeller 180, the “rear surface” of the second impeller 180 may be in front of a surface of the second impeller 180 opposite to the rear surface.

(33) In addition, the rotor 105 may protrude from other portions of the rotary shaft 110.

(34) The rotor 105 includes a permanent magnet and easily performs a high-speed rotation as a size of the permanent magnet is increased.

(35) Therefore, an outer diameter of the rotor 105 is increased to obtain a rotational force of a drive motor.

(36) As described above, when the diameter of the rotary shaft 100 is increased, the rotary shaft 100 has a disadvantage in terms of DN number, which is a limitation of a journal bearing supporting the rotary shaft 100.

(37) The DN number is calculated as a product of a diameter of the rotary shaft 100 and a number of rotations thereof. As the diameter of the rotary shaft 100 is increased, the DN number is increased.

(38) Accordingly, according to the present disclosure, both side portions of the rotary shaft 100 have diameters that are each smaller than the diameter of the rotor 105, thereby improving stability in high-speed rotation.

(39) According to the present disclosure, the turbo compressor couples the thrust bearing runner 120 and the first impeller 140 using the tie rod 160 in a state in which pre load is applied, thereby obtaining the coupling force between the thrust bearing runner 120 and the first impeller 140.

(40) When the turbo compressor rotates, the first impeller 140 receives a load in a leftward or forward direction in FIG. 5 based on a pressure difference generated by the rotation.

(41) To compensate for the load, the preload is applied to the tie rod 160 to couple the first impeller 140 and the thrust bearing runner 120 to the rotary shaft 100.

(42) The rotary shaft 100 includes a hollow groove 102 for coupling the tie rod 160 to the rotary shaft 100 by applying the pre load to the tie rod 160, and the hollow groove 102 has an inner diameter that is larger than an outer diameter of the tie rod 160.

(43) The tie rod 160 has one end coupled through the hollow groove 102 and the other end coupled to a fastening nut 162.

(44) In other words, when the fastening nut 162 is tightened while the thrust bearing runner 120 and the impeller 140 are inserted between a left end of the rotary shaft 100 and the fastening nut 162, the tie rod 160 is tensioned, and the impeller 140 and the thrust bearing runner 120 are compressed and coupled.

(45) A magnitude of the preload applied to the tie rod 160 may be set by adjusting a degree of tightening of the fastening nut 162.

(46) The hollow groove 102 is defined to allow the tie rod 160 to be in the tensioned state when the tie rod 160 is coupled and has an inner diameter that is larger than an outer diameter of the tie rod 160.

(47) When a frictional force occurs between the tie rod 160 and the hollow groove 102, a portion of the preload applied to the tie rod 160 is canceled or countered by the frictional force between the tie rod 160 and an inner wall of the hollow groove 102. In this case, the preload applied to the tie rod 160 may not act as a fastening force.

(48) An impeller sleeve 150 may be provided between the first impeller 140 and the thrust bearing runner 120 to achieve sealing performance of the first impeller 140.

(49) The impeller sleeve 150 may have a concavo-convex shape to prevent fluid leakage between the first impeller 140 and the impeller housing. For example, the impeller sleeve 150 may be made of a labyrinth seal.

(50) According to the present disclosure, the impeller sleeve 150 is provided between the first impeller 140 and the thrust bearing runner 120 to provide a coupling force for coupling the first impeller 140 and the thrust bearing runner 120.

(51) As shown, the ends of the thrust bearing runner 120 and the first impeller 140 are inserted into the inner diameter of the impeller sleeve 150, and the impeller sleeve 150 surrounds an outer circumference of a connecting portion between the first impeller 140 and the thrust bearing runner 120 and couples the first impeller 140 and the thrust bearing runner 120.

(52) For this coupling, a coupling shaft portion or shaft 142 is provided at a rear or right side of the first impeller 140, and a coupling shaft portion or shaft 124 is provided at a front or left side of the thrust bearing runner 120. The coupling shaft portion 142 and the coupling shaft portion 124 are inserted into the impeller sleeve 150.

(53) In this case, an outer diameter of each of the coupling shafts 142, 124 is larger than the inner diameter of the impeller sleeve 150. When the coupling shaft portions 142, 124 are forcibly coupled to or fitted into the impeller sleeve 150, the impeller sleeve 150 may provide the coupling force to couple the first impeller 140 and the thrust bearing runner 120.

(54) In this case, a sum of lengths of the coupling shaft portions 142 and 124 is smaller than a length of the impeller sleeve 150 such that there may be a gap or such that the coupling shaft portions 142 and 125 do not contact each other, and the pre load is applied to the first impeller 140 and the thrust bearing runner 120 by tightening the fastening nut 162 coupled to the tie rod 160, and thus, the impeller sleeve 150 is compressed and coupled between the first impeller 140 and the thrust bearing runner 120.

(55) When the sum of the lengths of the coupling shaft portions 142 and 124 is equal to or larger than that of the impeller sleeve 150, the coupling shaft portions 142 and 124 contact each other to prevent the compression of the first impeller 140 and the thrust bearing runner 120 by the impeller sleeve 150.

(56) In addition, the thrust bearing runner 120 coupled between the first impeller 140 and the rotary shaft 100 may also be coupled to the rotary shaft 100 by stationary fitting.

(57) As shown, the rotary shaft 100 includes a coupling groove 104 at an end of the hollow groove 102, the coupling groove 104 has an inner diameter that is larger than the inner diameter of the hollow groove 102, and the thrust bearing runner 120 includes a coupling shaft 122. The coupling shaft 122 may be coupled to the coupling groove 104 by stationary fitting.

(58) An outer diameter of the coupling shaft 122 is larger than the inner diameter of the coupling groove 104 to forcibly couple the coupling shaft 122 of the thrust bearing runner 120 to the coupling groove 104.

(59) Therefore, a contact area between the rotary shaft 100 and the thrust bearing runner 120 provided between the first impeller 140 and the rotary shaft 100 may be obtained to provide a coupling force between the thrust bearing runner 120 and the rotary shaft 100.

(60) The thrust bearing runner 120 inserted into the coupling groove 104 is shorter than a depth of the coupling groove 104 such that a compressive force is applied between the thrust bearing runner 120 and the left end of the rotary shaft 100 by the preload applied to the tie rod 160.

(61) FIG. 7 is an enlarged view showing a coupling portion between a rotary shaft and a second impeller of a turbo compressor according to a first embodiment of the present disclosure.

(62) Referring to FIG. 7, the second impeller 180 has a diameter that is relatively smaller than that of the first impeller 140 and is coupled to the rotary shaft 100 with multiple stages for providing a coupling force to couple the second impeller 180 and the rotary shaft 100.

(63) The second impeller 180 may be directly coupled to the rotary shaft 100 using a fastening bolt 164.

(64) The end of the rotary shaft 100 coupled to the second impeller 180 has a multi-stage structure in which a diameter is reduced with two stages.

(65) Hereinafter, a portion with a largest diameter of the rotary shaft 100 is referred to as a large-diameter or first portion 100-1, a portion with a smallest diameter of the rotary shaft 100 is referred to as a small-diameter or third portion 100-3, and a portion with a diameter that is smaller than the diameter of the large diameter portion 100-1 and larger than the diameter of the small-diameter portion 100-3 is referred to as a middle-diameter or second portion 100-2. The large-diameter, middle-diameter, and small-diameter portions 100-1, 100-2, and 100-3 may alternatively be referred to as first, second, and third sections.

(66) The second impeller 180 is coupled to the middle-diameter portion 100-2 and the small-diameter portion 100-3.

(67) The second impeller 180 includes a base plate 182 and an impeller blade 184 provided on the base plate 182.

(68) A rotary shaft fastening hole of the second impeller 180 has a first inner diameter corresponding to the middle-diameter portion 100-2 on the base plate 182 and has a second inner diameter corresponding to the small-diameter portion 100-3 on the impeller blade 184.

(69) This structure has an effect of increasing an effective area of the impeller blade 184 by reducing the inner diameter of the impeller blade 184.

(70) In addition, a stronger coupling force to couple the rotary shaft 100 and the second impeller 180 may be set.

(71) When the second impeller 180 is coupled to the rotary shaft 100 in multiple stages, a radial and/or circumferential surface of the rotary shaft 100 contacts the second impeller 180, and the contact area thereof is enlarged.

(72) Accordingly, the coupling force to couple the second impeller 180 and the rotary shaft 100 may be increased.

(73) An inner surface of the second impeller 180 is supported by a first stepped surface 103 between the large-diameter portion 100-1 and the middle-diameter portion 100-2 of the rotary shaft 100, and a stepped surface inside the base plate 182 of the second impeller 180 is supported by a second stepped surface 106 between the middle-diameter portion 100-2 and the small-diameter portion 100-3 of the rotary shaft 100.

(74) This structure allows the coupling contact on which the frictional force acts to be expanded when the second impeller 180 is coupled to the rotary shaft 100 by stationary fitting or shrink-fitting.

(75) In addition, when the fastening bolt 164 is coupled, the second impeller 180 is compressed between the first stepped surface 103 of the rotary shaft 100 and the fastening bolt 164, and the middle diameter portion 100-2 and the small diameter portion 100-3 of the rotary shaft 100 are tensioned.

(76) The preload applied to the second impeller 180 at the middle diameter portion 100-2 and the small diameter portion 100-3 of the rotary shaft 100 may be adjusted by controlling the fastening force of the fastening bolt 164.

(77) In this structure, the first impeller 140 and the second impeller 180 receiving the greatest force are symmetrical to each other in a forward and rearward direction (or leftward-rightward direction) and are equally deformed in the forward and rearward direction.

(78) If the deformation is biased to one side, the reliability of the turbo compressor may be deteriorated due to the deformation during high-speed operation.

(79) The tie rod 160 may be coupled to the rotary shaft 100 in a state in which the tension load is applied to the tie rod 160 based on the tightening force of the fastening nut 162.

(80) In other words, the tie rod 160 may be coupled in the state in which the pre load is applied to the tie rod 160. Therefore, even if deformation occurs in the tie rod 160 due to a thermal expansion and the tensile force is reduced, the pre load applied to the tie rod 160 absorbs the deformation due to the thermal expansion, thereby enabling reliable coupling of the tie rod 160.

(81) In order to reduce the size of the turbo compressor and perform the high-speed rotation, the first impeller 140 and the thrust bearing runner 120 are coupled using the tie rod 160 in the state in which the preload is applied and the second impeller 180 is coupled to the rotary shaft 100 by applying the pre load to the small diameter portion of the multistage rotary shaft 100. Therefore, the present disclosure has an effect of obtaining the coupling force between the rotating components of the turbo compressor rotating at the high speed.

(82) A result of an experiment of rotating the rotary shaft having a length of 177 mm and an outer diameter of 125 mm at 200,000 rpm is as follows.

(83) First bending frequency was 2,250.5 Hz and the DN Number was 2,500,000 mm×rpm. It was found that the first bending frequency was within a range of the operating speed, and thus, the turbo compressor shown in FIG. 2 was not suitable for high-speed operation.

(84) A result of an experiment in which the rotary shaft shown in FIG. 5 having a length of 135.5 mm and an outer diameter of 14.5 mm of the turbo compressor of FIG. 5 according to the first embodiment of the present disclosure is rotated at 200,000 rpm is as follows.

(85) First bending frequency was 5,1362.2 Hz and a DN Number was 2,900,000 mm×rpm. It was found that the first bending frequency was outside of an operating speed range, and thus, the rotary shaft 100 is suitable for the high-speed operation.

(86) FIG. 8 is a graph showing deformation with respect to stress of a stainless steel (SUS 304) material. FIG. 9 is a graph showing relation between deformation and a coupling force of a tie rod.

(87) Referring to FIGS. 8 and 9, the tie rod (e.g., tie rod 160 of FIG. 5) is made of, for example, a stainless steel (SUS 304) material. According to the graph showing the deformation of the SUS 304 material with respect to the stress, it can found that, if a safety factor is 3, the deformation may be less than 25 μm.

(88) In addition, if the deformation of the tie rod is set in a range from 7 to 25 μm, preload of the rotary shaft 100 may be set to 500 to 1800 N.

(89) FIG. 10 is a configuration diagram showing a structure of a turbo compressor according to a second embodiment of the present disclosure.

(90) Referring to FIG. 10, a turbo compressor 201 according to a second embodiment of the present disclosure includes a drive motor 210 including a rotary shaft 212, an impeller 230 coupled to the rotary shaft 212, a thrust bearing runner 250 to support load in an axial direction of the rotary shaft 212, and casings 220, 240, and 260 to accommodate or receive the drive motor 210, the impeller 230, and the thrust bearing runner 250.

(91) The casings 220, 240, 260 may include a motor casing 220 to accommodate or receive the drive motor 210, an impeller casing 240 to accommodate or receive the impeller 230, and a bearing casing 260 to accommodate or receive the thrust bearing runner 250.

(92) A stator of the drive motor 210 is provided inside the motor casing 220.

(93) The impeller casing 240 constitutes a compressor together with the impeller 230. An inlet flow path 310 to guide inflow of compressing fluid and a discharge flow path 320 to guide the fluid discharged after being compressed by the compressor are each connected to the compressor.

(94) In addition, the turbo compressor 201 may include a cooling flow path 350 branched from the discharge flow path 320 and connected to the bearing casing 260.

(95) A portion of the fluid discharged through the discharge flow path 320 of the turbo compressor 201 is supplied to an inside of the bearing casing 260 to accommodating the thrust bearing runner 250 to cool heat generated at the thrust bearing runner 250.

(96) The turbo compressor 201 includes a drive motor 210, a motor casing 220, an impeller 230 coupled to the rotary shaft 212, an impeller casing 240, a thrust bearing runner 250 coupled to the rotary shaft 212, a bearing casing 260 to accommodate the thrust bearing runner 250, an inflow flow path 310 to guide fluid to an inlet of the impeller casing 240, a discharge flow path 320 to guide the fluid discharged from a discharge outlet of the impeller casing 240, and a cooling flow path 350 to connect the discharge glow path 320 and the bearing casing 260 to supply the fluid to the inside of the bearing casing 260.

(97) This structure may cool the turbo compressor 201 using the compressing fluid without using additional refrigerant or a separate coolant or cooling fluid to cool the turbo compressor 201, thereby removing or not requiring the cooling ring of the related art structure or the inlet and the discharge outlet of the refrigerant connected to the cooling ring. The cooling ring which surrounds an outer circumferential surface of the drive motor may be removed to reduce a size of the turbo compressor.

(98) In addition, the portion of the fluid discharged through the discharge flow path 320 is supplied to the inside of the bearing casing 260 to cool the thrust bearing runner 250.

(99) In this case, a flow rate control means or controller may be provided at the cooling flow path 350 to adjust a flow rate of the fluid supplied into the bearing casing 260 through the cooling flow path 350.

(100) The flow rate control of the fluid supplied through the cooling flow path 350 may be performed by adjusting a cross-sectional area of the cooling flow path 350. In other words, the flow rate of the fluid flowing through the cooling flow path 350 may be adjusted by providing an orifice or a capillary tube in a portion of the cooling flow path 350.

(101) The turbo compressor 201 supplies the portion of the fluid discharged through the discharge flow path 320 into the bearing casing 260.

(102) If an excessive amount of the flow rate of the fluid is supplied through the cooling flow path 350 of the turbo compressor 201, the performance of the compressor is deteriorated.

(103) For this reason, the flow rate of the fluid supplied to the bearing casing 260 through the cooling flow path 350 may be appropriately adjusted.

(104) In addition, the turbo compressor may include a check valve provided in the cooling flow path 350 to prevent backflow of fluid.

(105) FIG. 11 is a configuration diagram showing a structure of a turbo compressor according to a third embodiment of the present disclosure.

(106) Referring to FIG. 11, a turbo compressor 202 according to the third embodiment of the present disclosure includes a drive motor 210, a motor casing 220, an impeller 230, an impeller casing 240, a thrust bearing runner 250, a bearing casing 260, an inlet flow path 310, a discharge flow path 320, and a cooling flow path 350 similar to the second embodiment.

(107) In addition, the turbo compressor 202 according to the third embodiment of the present disclosure further includes a recovery chamber 270 to receive fluid supplied to an inside of the bearing casing 260 through the cooling flow path 350 and a recovery flow path 280 to return the fluid received in the recovery chamber 270 to the compressor.

(108) The recovery chamber 270 functions to supply a space to temporarily store the fluid which is supplied to the inside of the bearing casing 260 through the cooling flow path 350 and stably supply the fluid to the bearing casing 260.

(109) The fluid flows based on a pressure difference. A velocity and the flow rate of the fluid passing through the bearing casing 260 may be set or predetermined based on the pressure difference between the cooling flow path 350 and the recovery chamber 270.

(110) The turbo compressor 202 recovers the fluid used to cool the thrust bearing runner 250 through the recovery chamber 270 and supplies the fluid to the inflow path 310 through the recovery flow path 280, thereby preventing fluid leakage.

(111) The fluid supplied through the discharge flow path 320 has high pressure, but the fluid pressure is decreased as the fluid passes through the inside of the bearing casing 260 and the recovery chamber 270.

(112) In this case, the fluid with the reduced pressure is recovered to the inlet flow path 310 through the recovery flow path 280, and the recovered fluid may be recompressed by the impeller 230.

(113) The turbo compressor 202 according to the present embodiment may further include a flow rate control valve at the recovery flow path 280.

(114) The flow velocity and the flow rate of the fluid supplied to the inside of the bearing casing 260 may be adjusted using the flow rate control valve provided in the recovery flow path 280.

(115) FIG. 12 is a configuration diagram showing a structure of a turbo compressor according to a fourth embodiment of the present disclosure.

(116) Referring to FIG. 12, a turbo compressor 203 according to the fourth embodiment of the present disclosure includes a drive motor 210 including a rotary shaft 212, a motor casing 220 to accommodate the drive motor 210, an impeller 230 coupled to one side of the rotary shaft 212, an impeller casing 240 to accommodate the impeller 230, a thrust bearing runner 250 coupled to the other side of the rotary shaft 212, a bearing casing 260 to accommodate the thrust bearing runner 250, an inflow flow path 310 to guide fluid to an inlet of the impeller casing 240, a discharge flow path 320 to guide fluid discharged through a discharge outlet of the impeller casing 240, a cooling flow path 350 to connect the discharge flow path 320 and the bearing casing 260 to supply the fluid to an inside of the bearing casing 260, a recovery chamber 270 to receive the fluid supplied to the bearing casing 260, a recovery flow path 280 to guide the fluid received in the recovery chamber 270 to the inlet flow path 310, and a flow rate control valve 352 included in the cooling flow path 350 to adjust flow rate of the fluid flowing through the cooling flow path 350 and to adjust the flow rate of fluid supplied to a bearing.

(117) For example, in the case of low-speed operation in which cooling of the thrust bearing runner 250 is not needed, the flow rate control valve 352 is closed to prevent degradation in compression efficiency, and in the case of high-speed operation, the flow rate control valve 352 is opened to supply the fluid into the bearing casing 260 through the cooling flow path 350.

(118) An opening rate or degree of the flow rate control valve 352 may be adjusted based on a temperature inside the bearing casing 260 or a rotation speed of the drive motor 210.

(119) FIG. 13 is a configuration diagram showing a turbo compressor according to a fifth embodiment of the present disclosure.

(120) Referring to FIG. 13, a turbo compressor 204 according to the fifth embodiment of the present disclosure includes a drive motor 210 including a rotary shaft 212, a motor casing 220 to accommodate the drive motor 210, an impeller 230 coupled to one side of the rotary shaft 212, an impeller casing 240 to accommodate the impeller 230, a thrust bearing runner 250 coupled to the other side of the rotary shaft 212, a bearing casing 260 to accommodate the thrust bearing runner 250, an inlet flow path 310 to guide fluid to an inlet of the impeller casing 240, a discharge flow path 320 to guide the fluid discharged from an outlet of the impeller casing 240, a cooling flow path 350 to connect the discharge flow path 320 and the bearing casing 260 to supply fluid into the bearing casing 260, a recovery chamber 270 to receive the fluid supplied to the bearing casing 260, a recovery flow path 280 to guide the fluid received in the recovery chamber 270 to the inlet flow path 310, a flow rate control valve 352 provided in the cooling flow path 350 to control a flow rate of the fluid flowing through the cooling flow path 350, a pressure sensor 354 provided downstream of the flow rate control valve 352 and to sense pressure of fluid passing through the flow rate control valve 352, and a controller 356 to receive information on pressure detected by the pressure sensor 354 and adjust an opening rate or degree of the flow control valve 352.

(121) The turbo compressor 204 includes the pressure sensor 354 on the downstream side of the flow rate control valve 352 to measure actual pressure of the fluid supplied through the cooling flow path 350 and accurately control the flow rate of the fluid supplied to the bearing casing 260.

(122) FIG. 14 is a configuration diagram showing a turbo compressor according to a sixth embodiment of the present disclosure.

(123) Referring to FIG. 14, a turbo compressor 205 according to the sixth embodiment of the present disclosure includes a drive motor 210 including a rotary shaft 212, a motor casing 220 to accommodate the drive motor 210, an impeller 230 coupled to one side of the rotary shaft 212, an impeller casing 240 to accommodate the impeller 230, a thrust bearing runner 250 coupled to the other side of the rotary shaft 212, a bearing casing 260 to accommodate the thrust bearing runner 250, an inlet flow path 310 to guide fluid to an inlet of the impeller casing 240, a discharge flow path 320 to guide fluid discharged from a discharge outlet of the impeller casing 240, a cooling flow path 350 to connect the discharge flow path 320 and the bearing casing 260 to supply fluid into the bearing casing 260, a recovery chamber 270 to receive the fluid supplied to the bearing casing 260, a recovery flow path 280 to guide the fluid received in the recovery chamber 270 to the inlet flow path 310, and a heat exchanger 360 provided along or in the cooling flow path 350 and in the inlet flow path 310.

(124) Relatively high temperature fluid supplied through the cooling flow path 350 may be heat-exchanged with relatively low temperature fluid introduced through the inlet flow path 310 through the heat exchanger 360, thereby reducing a temperature of the fluid supplied through the cooling flow path 350.

(125) The heat exchanger 360 is provided so as not to interfere with a flow of suctioned fluid.

(126) For example, in the case of a pin-tube type heat exchanger, the pin is arranged in parallel with a flow direction of the suctioned fluid.

(127) The fluid supplied through the cooling flow path 350 cools the inside of the bearing casing 260, and the cooling effect is increased as the fluid temperature decreases.

(128) If the cooling effect is improved, the desired cooling effect of the bearing may be obtained with a relatively less flow rate of fluid.

(129) The structure has an effect of eliminating a phenomenon in which cooling is not sufficiently performed when the fluid circulating through a fluid circuit has a relatively high temperature.

(130) FIG. 15 is a configuration diagram showing a turbo compressor according to a seventh embodiment of the present disclosure.

(131) Referring to FIG. 15, a turbo compressor 206 according to the seventh embodiment of the present disclosure includes a drive motor 210 including a rotary shaft 212, a motor casing 220 to accommodate the drive motor 210, an impeller 230 coupled to one side of the rotary shaft 212 and rotating together with the rotary shaft 212, an impeller casing 240 to accommodate the impeller 230 and including a diffuser to convert flow of gas accelerated by the impeller 230 into pressure energy, a thrust bearing runner 250 coupled to the other side of the rotary shaft 212 and rotating together with the rotary shaft 212, a bearing casing 260 to support the thrust bearing runner 250, an inlet flow path 310 to guide fluid introduced into the impeller casing 240, a discharge flow path 320 to guide fluid discharged from the impeller casing 240, a cooling flow path 350 connected to the diffuser of the impeller casing 240 and to guide the fluid in the diffuser to the bearing casing 260, a recovery chamber 270 to receive the fluid discharged from the bearing casing 260, and a recovery flow path 280 to guide the fluid received in the recovery chamber 270 to the inlet flow.

(132) The cooling flow path 350 of the turbo compressor 206 is connected to the impeller casing 240 and may not be connected to the discharge flow path 320.

(133) The fluid inside the impeller casing 240 has pressure that is relatively lower than that of the fluid inside the discharge flow path 320, thereby reducing compression loss of the fluid supplied to the cooling flow path 350.

(134) In addition, the configurations of the flow rate control valve 352, the pressure sensor 354, and the controller 356 of the above-described embodiments (e.g., in FIG. 13) may be used.