JP2013083168A - Turbo compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a turbo compressor capable of withstanding high loads.SOLUTION: The turbocharger includes a bull gear shaft 52 which is provided along the reference plane B, and driven and rotated by a drive motor, and a bearing 60 having a split face 100 to be split along an oil supply groove 61b while the oil supply groove 61b is formed in a journal face 61a opposing a circumferential surface of the bull gear shaft 52 along the axial direction of the bull gear shaft 52. The split face 100 is arranged at the position different from the direction of the load applied to the journal face 61a from the bull gear shaft 52 which is driven and rotated.

Description

  The present invention relates to a turbo compressor.

  The following Patent Document 1 discloses a rotating structure that employs a direct lubrication journal bearing that supports a rotor. This bearing has a split-type bearing housing fixedly supported by a bearing base having a semicircular recess with respect to a reference plane. A plurality of tilting pads are arranged inside the bearing housing.

  This split bearing housing has a horizontal split surface that can be divided into an upper bearing housing and a lower bearing housing each having a semi-ring shape, and the lower bearing housing fits into the recess of the bearing base. Fixed. The upper bearing housing is coupled to the lower bearing housing by positioning pins and coupling bolts.

JP 2010-116958 A

  By the way, in a turbo compressor that compresses a predetermined gas by rotating a rotor by a driving machine, the above-mentioned split-type structure is adopted for a bearing having a journal surface (sliding surface) facing the circumferential surface of the rotor. There is. In the split-type bearing, an oil supply groove extending in the axial direction along the horizontal dividing surface may be formed for ease of processing.

  However, the load applied to the journal surface from the rotor is caused not only by the load in the gravity direction due to the weight of the rotor, but also by the load in the thrust direction due to the meshing of the helical gear, the collision with the fluid during compression, etc. Loads in a direction different from the gravity direction are included. For this reason, the load direction applied from the rotor to the journal surface may be in the vicinity of the oil groove on the horizontal dividing surface, and the load cannot be firmly received by the surface. There is a problem that can not be.

  The present invention has been made in view of the above-described problems, and an object thereof is to provide a turbo compressor that can cope with a high load.

In order to solve the above-described problems, the present invention provides a rotor that is provided along a reference plane and that is rotationally driven by a driving machine, and a journal surface that faces the circumferential surface of the rotor, along the axial direction of the rotor. And a bearing having a dividing surface that can be divided along the oiling groove, wherein the dividing surface is from the rotor that is rotationally driven to the journal surface. The structure of being arrange | positioned in the position different from the direction of the load added to is adopted.
By adopting this configuration, in the present invention, since the oil supply groove is not arranged in the load direction applied to the journal surface during driving of the rotor, it is possible to cope with a higher load than before.

Further, in the present invention, the bearing is mounted in a posture in which the dividing surface is inclined with respect to the reference plane based on a load including a horizontal component applied to the journal surface from the rotor that is rotationally driven. A configuration is adopted in which a fixing portion for fixing is provided.
By adopting this configuration, in the present invention, the split surface is inclined from the reference plane by changing and fixing the bearing posture based on the load in the direction including the horizontal component applied from the rotor to the journal surface. As a result, the load can be firmly received by the journal surface while preventing the oil supply groove from being arranged in the load direction including the horizontal component, so that it is possible to cope with a higher load than before.

Moreover, in this invention, the structure that the said division surface inclines with respect to a horizontal surface is employ | adopted.
By adopting this configuration, in the present invention, when the load direction applied from the rotor to the journal surface is horizontal by tilting the dividing surface with respect to the horizontal plane, the oil supply groove is not arranged in the load direction. The load can be firmly received on the journal surface.

In the present invention, the rotor has a gear that rotationally drives the second rotor and the third rotor, and the bearing is provided on the drive machine side with the gear interposed therebetween. A first bearing for fixing the first bearing in a first posture; and a second bearing provided on a side opposite to the drive unit across the gear. The structure which has a part and the 2nd fixing | fixed part which fixes the said 2nd bearing with the said 1st attitude | position is employ | adopted.
By adopting this configuration, in the present invention, the first bearing provided on the drive machine side with the gear interposed therebetween is fixed in the first posture, and the first bearing provided on the opposite side of the drive machine with the gear interposed therebetween. By fixing the two bearings in the same first posture as the first bearing and matching the dividing surfaces of the two bearings, the assembly work of the respective bearings with respect to the rotor can be performed collectively.

In the present invention, the rotor has a gear that rotationally drives the second rotor and the third rotor, and the bearing is provided on the drive machine side with the gear interposed therebetween. A first bearing for fixing the first bearing in a first posture; and a second bearing provided on a side opposite to the drive unit across the gear. And a second fixing portion that fixes the second bearing in a second posture different from the first posture.
By adopting this configuration, in the present invention, the first bearing provided on the drive machine side with the gear interposed therebetween is fixed in the first posture, and the first bearing provided on the opposite side of the drive machine with the gear interposed therebetween. By fixing the second bearing in a second posture different from that of the first bearing and changing the dividing surfaces of the two bearings, it is possible to cope with a higher load as an optimum inclination of the dividing surface in each bearing. .

In the present invention, the second rotor and the third rotor each have a thrust collar that can abut against the gear in the axial direction.
By adopting this configuration, the present invention can cope with a high load when a moment load is applied from the rotor to the journal surface due to the axial loads from the second rotor and the third rotor.

In the present invention, the second rotor and the third rotor are provided along the reference plane and have a positional relationship with the rotor interposed therebetween.
By adopting this configuration, in the present invention, when the moment load along the substantially reference plane is applied from the rotor to the journal surface due to the axial load from the second rotor and the third rotor, By tilting with respect to the reference plane, the moment load can be firmly received on the journal surface while preventing the oil supply groove from being arranged in the moment load direction.

Moreover, in this invention, the said bearing has the structure of having the journal bearing part which has the said journal surface, and the thrust bearing part provided integrally with the said journal bearing part.
By adopting this configuration, in the present invention, it is possible to cope with a high load when the bearing actively receives a thrust load.

  ADVANTAGE OF THE INVENTION According to this invention, the turbo compressor which can respond to a high load is obtained.

It is sectional drawing which shows the principal part of the turbo compressor in embodiment of this invention. It is a front view which shows the fixed attitude | position with respect to the gear case of the 1st bearing in embodiment of this invention. It is a rear view which shows the structure of the 1st bearing in embodiment of this invention. It is an arrow A figure in FIG. It is a figure for demonstrating the load containing the horizontal component added to a journal surface from the bull gear shaft in embodiment of this invention. It is a graph regarding the load added to the journal surface of a 1st bearing from the bull gear shaft in embodiment of this invention. It is a graph which shows the relationship between the bearing rotation angle and the minimum oil film thickness in the 1st bearing in embodiment of this invention. It is a graph regarding the load added to the journal surface of a 2nd bearing from the bull gear shaft in embodiment of this invention. It is a graph which shows the relationship between the bearing rotation angle and the minimum oil film thickness in the 2nd bearing in embodiment of this invention.

  Embodiments of a turbo compressor according to the present invention will be described below with reference to the drawings.

FIG. 1 is a cross-sectional view showing a main part of a turbo compressor 1 according to an embodiment of the present invention.
The turbo compressor 1 includes a first stage compressor 10, a second stage compressor 20, a third stage compressor 30, a fourth stage compressor 40, a drive motor (drive machine) M, and a gear device 50. And have. Further, the turbo compressor 1 guides the gas G from the first stage compressor 10 to the second stage compressor 20, the third stage compressor 30, and the fourth stage compressor 40 in this order. It has.

  The gear device 50 includes a bull gear shaft (rotor) 52 having a bull gear 51, a low speed pinion shaft (second rotor) 54 having a first pinion gear 53, and a high speed pinion shaft (first gear) having a second pinion gear 55. 3 rotors) 56 and a gear case 57. The bull gear 51 meshes with the first pinion gear 53 and the second pinion gear 55, respectively. The bull gear 51, the first pinion gear 53, and the second pinion gear 55 are composed of helical gears that are excellent in silence and torque transmission.

  The low-speed pinion shaft 54 is arranged in parallel with the bull gear shaft 52 and is rotatably supported with respect to the gear case 57 by a journal bearing (not shown) provided in the gear case 57. An impeller 11 of the first stage compressor 10 is provided at one end of the low-speed pinion shaft 54, and an impeller 21 of the second stage compressor 20 is provided at the other end. The low-speed pinion shaft 54 has a thrust collar 58 that can abut on the bull gear 51 on both axial sides.

  On the other hand, the high-speed pinion shaft 56 is disposed parallel to the bull gear shaft 52 and on the opposite side of the bull gear shaft 52 with respect to the low-speed pinion shaft 54. On the other hand, it is pivotally supported. An impeller 31 of the third stage compressor 30 is provided at one end of the high-speed pinion shaft 56, and an impeller 41 of the fourth stage compressor 40 is provided at the other end. The high-speed pinion shaft 56 has a thrust collar 59 that can abut against the bull gear 51 on both axial sides.

  The impellers 11, 21, 31, and 41 are radial impellers, and have blades including a three-dimensional twist (not shown) that guides the gas G sucked in the axial direction in the radial direction. Diffuser flow paths are provided around the impellers 11, 21, 31, and 41, respectively, and the gas G led out in the radial direction is compressed and boosted in the flow paths, and further provided around the diffuser flow paths. It is possible to supply the compressor to the next stage through the scroll flow path.

  The bull gear shaft 52 is connected to the output shaft 2 of the drive motor M and is configured to be rotationally driven by the drive motor M. The bull gear shaft 52 is rotatably supported with respect to the gear case 57 by a bearing 60 provided on the gear case 57. The bearing 60 includes a first bearing 60A provided on the drive motor M side with the bull gear 51 interposed therebetween, and a second bearing 60B provided on the opposite side to the drive motor M side with the bull gear 51 interposed therebetween.

  According to the turbo compressor 1 having the above configuration, when the bull gear shaft 52 is rotationally driven by the drive motor M, the low speed pinion shaft 54 and the high speed pinion shaft 56 are rotationally driven in synchronization with the rotation of the bull gear shaft 52. Thereby, the gas G is introduced from the inlet 12 of the first stage compressor 10 and is compressed in the first stage, and then the gas G is supplied to the second stage compressor 20 via a gas flow path (not shown). The intake port 22, the intake port 32 of the third stage compressor 30, and the intake port 42 of the fourth stage compressor 40 are introduced in this order for multistage compression. The multistage-compressed gas G is supplied to an industrial machine (not shown) connected to the turbo compressor 1 or an air separation device.

Next, the configuration of the bearing 60 will be described in detail with reference to FIGS. In the following description, only the configuration of the first bearing 60A will be described, and the configuration of the second bearing 60B having the same configuration as that of the first bearing 60A will be omitted to avoid redundant description.
FIG. 2 is a front view showing a fixed posture of the first bearing 60A with respect to the gear case 57 in the embodiment of the present invention. FIG. 3 is a rear view showing the configuration of the first bearing 60A in the embodiment of the present invention. 4 is an arrow A view in FIG.

  As shown in FIG. 2, the first bearing 60 </ b> A is fixed in a predetermined posture with respect to a gear case 57 having a semicircular recess 57 a with respect to a reference plane B on which the bull gear shaft 52 is provided. The reference plane B of the present embodiment coincides with the combined surface of the lower gear case 57 shown in FIG. 2 and the upper gear case not shown in FIG. In addition, the reference plane B of the present embodiment matches the horizontal plane. The reference plane B and the horizontal plane are almost the same, but the reference plane B and the horizontal plane may not match depending on the installation location and specifications of the turbo compressor 1.

The first bearing 60 </ b> A includes a journal bearing portion 61 having a journal surface (slip surface) 61 a and a thrust bearing portion 62 provided integrally with the journal bearing portion 61.
The journal bearing portion 61 is a perfect circular bearing having a substantially cylindrical shape that can be fitted into the semicircular recess 57a (see FIGS. 3 and 4). The journal surface 61a is made of, for example, white metal. The journal surface 61a is formed with a pair of oil supply grooves 61b along the axial direction of the bull gear shaft 52 (see FIG. 3).

  The thrust bearing portion 62 is a substantially annular plate-shaped taper land bearing having a diameter larger than that of the journal bearing portion 61. The thrust bearing portion 62 is disposed opposite to a substantially disc-shaped thrust disk 63 (see FIG. 1) that rotates integrally with the bull gear shaft 52, and is fixed integrally with the gear case 57 together with the journal bearing portion 61. .

  As shown in FIG. 3, the first bearing 60 </ b> A configured as described above has a split structure with a split surface 100 that can be split along the oil supply groove 61 b. Hereinafter, one side divided by the dividing surface 100 is referred to as an upper half 70A, and the other side is referred to as a lower half 70B. Each of the upper half 70A and the lower half 70B has a substantially semicircular ring shape.

  The upper half 70A is positioned by the positioning pin 71 with respect to the lower half 70B, and is coupled to the lower half 70B by the coupling bolt 72. The positioning pin 71 and the coupling bolt 72 are provided on the journal bearing portion 61, respectively. As shown in FIG. 4, the journal bearing portion 61 is provided with pin insertion holes 73 for inserting the positioning pins 71 and bolt insertion holes 74 for inserting the coupling bolts 72 at two diagonal points.

  A bearing fixing hole (fixing portion) 75 that fixes the first bearing 60A to the gear case 57 in a predetermined posture is formed at a position corresponding to the journal bearing portion 61 of the upper half 70A. The bearing fixing hole 75 of this embodiment is formed as a hole into which a pin (not shown) is inserted. As shown in FIG. 2, the bearing fixing hole 75 is arranged at a right angle (90 °) with respect to the reference plane B when the first bearing 60 </ b> A is fixed to the gear case 57.

  A pin (not shown) is inserted into the bearing fixing hole 75 from above when the lower gear case 57 and the upper gear case (not shown) are combined. Accordingly, the rotation of the first bearing 60A relative to the gear case 57 is restricted and fixed. The bearing fixing hole 75 is provided at a predetermined angle with respect to the dividing surface 100, and is configured to incline the dividing surface 100 with respect to the reference plane B (horizontal plane) as shown in FIG. The predetermined angle (60 °) shown in FIG. 2 is defined by setting the reference plane B to 0 ° and the rotation direction of the bull gear shaft 52 (clockwise in FIG. 2) as +.

The inclination of the dividing surface 100 with respect to the reference plane B is set based on a load including a horizontal component applied from the bull gear shaft 52 to the journal surface 61a during rotational driving.
Subsequently, a load including a horizontal component applied from the bull gear shaft 52 to the journal surface 61a will be described in detail.

  FIG. 5 is a view for explaining a load including a horizontal component applied from the bull gear shaft 52 to the journal surface 61a in the embodiment of the present invention. FIG. 5A is a diagram schematically showing a load applied in the direction along the reference plane B. FIG. FIG. 5B is a diagram schematically illustrating a load applied in a direction along a plane orthogonal to the reference plane B.

  As shown in FIG. 5A, the bull gear shaft 52 is driven to rotate by receiving torque from the drive motor M. When the bull gear shaft 52 is rotationally driven, the low speed pinion shaft 54 and the high speed pinion shaft 56 that are arranged on the left and right along the reference plane B are rotationally driven via the bull gear 51. The low-speed pinion shaft 54 and the high-speed pinion shaft 56 are each supported by a journal bearing (not shown), and the axial load (thrust load) generated by the helical gear and the compressed gas is caused by the thrust collars 58 and 59 to the bull gear 51 side. Is transmitted to. The bearing 60 of the bull gear shaft 52 receives the transmitted thrust load by the thrust bearing portion 62 and receives the radial load (journal load) from the bull gear shaft 52 by the journal bearing portion 61.

  On the journal surface 61a of the journal bearing portion 61, as shown in FIG. 5B, a load due to the weight of the bull gear shaft 52 and transmission power (reaction force) to the low-speed pinion shaft 54 and the high-speed pinion shaft 56 are present. In addition, a moment load resulting from the thrust load from the low-speed pinion shaft 54 and the high-speed pinion shaft 56 is further applied (see FIG. 5A). This moment load is particularly affected by the gas / thrust force generated by the compressed gas among the thrust loads generated by the helical gears and the compressed gas. The gas / thrust force includes those from the impellers 11 and 21 provided at both ends of the low-speed pinion shaft 54 and those from the impellers 31 and 41 provided at both ends of the high-speed pinion shaft 56.

  When the gas / thrust force is evenly generated on both the low-speed pinion shaft 54 side and the high-speed pinion shaft 56 side, the bearing 60 of the bull gear shaft 52 receives a load perpendicular to the bearing surface 62a of the thrust bearing portion 62. Can do. However, when there is an imbalance in the gas and thrust forces generated on the low-speed pinion shaft 54 side and the high-speed pinion shaft 56 side (this is the case in most cases), the moment of the bearing 60 of the bull gear shaft 52 is increased. This affects the journal surface 61a. Depending on the magnitude of the gas / thrust force generated at this time, the load direction applied to the journal surface 61a of the bearing 60 may be substantially horizontal. In this way, a load including a horizontal component is applied from the bull gear shaft 52 to the journal surface 61a.

  FIG. 6 is a graph relating to the load applied from the bull gear shaft 52 to the journal surface 61a of the first bearing 60A in the embodiment of the present invention. FIG. 7 is a graph showing the relationship between the bearing rotation angle and the minimum oil film thickness in the first bearing 60A in the embodiment of the present invention. FIG. 8 is a graph relating to the load applied to the journal surface 61a of the second bearing 60B from the bull gear shaft 52 in the embodiment of the present invention. FIG. 9 is a graph showing the relationship between the bearing rotation angle and the minimum oil film thickness in the second bearing 60B in the embodiment of the present invention. 6 and 8 show graphs in the circumferential direction of the axial center position of the journal surface 61a when the dividing surface 100 is arranged on the reference plane B (when arranged at 0 ° and 180 °).

As shown in FIG. 6, the journal surface 61a of the first bearing 60A has an oil film pressure of the lubricating oil in the vicinity of the oil supply groove 61b disposed at 180 ° due to the influence including a horizontal component applied from the bull gear shaft 52. It can be seen that the maximum value appears and the minimum value of the oil film thickness appears. Further, it can be seen that the maximum value of the bearing temperature rise appears in the vicinity of the oil supply groove 61b arranged at 180 °.
As described above, when the split surface 100 of the first bearing 60A is arranged on the reference plane B, the load applied to the journal surface 61a from the bull gear shaft 52 is received in the vicinity of the oil supply groove 61b and can be received firmly on the surface. In this case, it can be seen that a high load cannot be handled.

On the other hand, as shown in FIG. 7, when the bearing rotation angle with respect to the reference plane B of the first bearing 60A is changed every 30 °, the minimum oil film thickness in the circumferential direction of the journal surface 61a gradually increases from 0 °. It can be seen that the maximum value is 90 °, and then gradually decreases.
Thus, the load direction including the horizontal component applied from the bull gear shaft 52 by changing the attitude of the first bearing 60A to, for example, 30 °, 60 °, and 90 ° and inclining the dividing surface 100 from the reference plane B. Therefore, the journal surface 61a can receive the load firmly while preventing the oil supply groove 61b from being disposed on the journal surface 61a. Therefore, it is possible to cope with a higher load than when the dividing surface 100 is arranged on the reference plane B.

On the other hand, as shown in FIG. 8, the journal surface 61 a of the second bearing 60 B has an effect of a load including a horizontal component applied from the bull gear shaft 52 in the vicinity of the oil supply groove 61 b arranged at 0 ° (360 °). It can be seen that the maximum value of the oil film pressure of the lubricating oil appears and the minimum value of the oil film thickness appears. Further, it can be seen that the maximum value of the bearing temperature rise appears in the vicinity of the oil supply groove 61b arranged at 0 ° (360 °). In addition, it is thought that the appearance position of the maximum value of each value is half-phase shifted from the first bearing 60A because a moment is applied to the bull gear shaft 52 around the bull gear 51 (see FIG. 5A). ).
Thus, even when the dividing surface 100 of the second bearing 60B is arranged on the reference plane B, the load applied to the journal surface 61a from the bull gear shaft 52 is received in the vicinity of the oil supply groove 61b and can be received firmly on the surface. In this case, it can be seen that a high load cannot be handled.

On the other hand, as shown in FIG. 9, when the bearing rotation angle with respect to the reference plane B of the second bearing 60B is changed every 30 °, the minimum oil film thickness in the circumferential direction of the journal surface 61a gradually increases from 0 °. It can be seen that the maximum value is 120 ° and then gradually decreases.
Thus, the load direction including the horizontal component applied from the bull gear shaft 52 by changing the attitude of the second bearing 60B to, for example, 60 °, 90 °, and 120 ° and inclining the dividing surface 100 from the reference plane B. Therefore, the journal surface 61a can receive the load firmly while preventing the oil supply groove 61b from being disposed on the journal surface 61a. Therefore, it is possible to cope with a higher load than when the dividing surface 100 is arranged on the reference plane B.

  Returning to FIG. 2, the bearing fixing hole 75 of the first bearing 60 </ b> A of the present embodiment is provided at 30 ° with respect to the dividing surface 100, and the dividing surface 100 is inclined by 60 ° with respect to the reference plane B. It is configured. By the way, as shown in FIG. 7, it is most preferable that the bearing rotation angle of the first bearing 60A is 90 °. However, when the bearing rotation angle of the first bearing 60A is 90 °, the formation of the bearing fixing hole 75 is formed. The position coincides with the dividing surface 100 and interferes with the positioning pins 71 and the like. Therefore, in the present embodiment, the first bearing 60A is fixed to the gear case 57 in a posture (first posture) in which the bearing rotation angle is 60 °, and the dividing surface 100 is inclined by 60 ° with respect to the reference plane B. It is configured to allow

  As shown in FIG. 1, the second bearing 60B of the present embodiment has the same first attitude as that of the first bearing 60A so that the divided surface 100 and the divided surface 100 of the first bearing 60A coincide with each other. And fixed to the gear case 57. In this way, by associating the two divided surfaces 100, the assembly work of the respective bearings 60 with respect to the bull gear shaft 52 can be performed collectively. Specifically, the bull gear shafts 52 are placed on the respective lower halves 70B supported by the recesses 57a, and the respective upper halves 70A are assembled thereto using the positioning pins 71 and the connecting bolts 72. Thereafter, both the first bearing 60A and the second bearing 60B assembled to the bull gear shaft 52 are rotated by 60 °, and in both positions, the bearing fixing hole 75 (first fixing portion) of the first bearing 60A and the first bearing Pins (not shown) can be respectively inserted into the bearing fixing holes 75 (second fixing portions) of the second bearing 60 </ b> B so as to be fixed to the gear case 57 at a time.

By the way, the reason why the second bearing 60B is fixed in the same first posture as the first bearing 60A is that the first bearing 60A has a horizontal component applied from the bull gear shaft 52 more than the second bearing 60B. This is because the load to be included is large. That is, as shown in FIGS. 6 and 8, the first bearing 60 </ b> A provided on the drive motor M side has an oil film pressure higher than that of the second bearing 60 </ b> B provided on the opposite side to the drive motor M. Since the maximum value is large, the bearing rotation angle of both the bearings 60B is set to 120 ° in accordance with the attitude of the second bearing 60B (second attitude), and is adjusted to the attitude of the first bearing 60A (first attitude). Therefore, it is possible to cope with a higher load when both bearing rotation angles are set to 60 °.
Although the assembly work takes time, the first bearing 60A is fixed in the first posture (60 °), and the second bearing 60B is in a second posture (120 °) different from the first bearing 60A. It is also possible to cope with a higher load by fixing the two and making the two dividing surfaces 100 different from each other so that the optimum inclination of the dividing surface 100 is obtained in each bearing 60.

Therefore, according to the above-described embodiment, the bull gear shaft 52 provided along the reference plane B and rotated by the drive motor M and the journal surface 61a facing the circumferential surface of the bull gear shaft 52 are connected to the bull gear shaft 52. A turbo compressor 1 having an oil supply groove 61b formed along the axial direction and a bearing 60 having a divided surface 100 that can be divided along the oil supply groove 61b. It is arranged at a position different from the direction of the load applied to the journal surface 61a from the driven bull gear shaft 52, and is applied to the load in the direction including the horizontal component applied to the journal surface 61a from the bull gear shaft 52 that is rotationally driven. On the basis of this, by adopting a configuration having a bearing fixing hole 75 for fixing the bearing 60 in a posture in which the dividing surface 100 is inclined with respect to the reference plane B. By changing the posture of the bearing 60 and fixing it based on the load in the direction including the horizontal component applied from the bull gear shaft 52 to the journal surface 61a, the split surface 100 is inclined from the reference plane B, and the load including the horizontal component The load can be firmly received by the journal surface 61a while preventing the oil supply groove 61b from being disposed in the direction.
For this reason, according to this embodiment, the turbo compressor 1 which can respond to a high load is obtained.

  As mentioned above, although preferred embodiment of this invention was described referring drawings, this invention is not limited to the said embodiment. Various shapes, combinations, and the like of the constituent members shown in the above-described embodiments are examples, and various modifications can be made based on design requirements and the like without departing from the gist of the present invention.

  For example, in the above embodiment, the drive motor M is employed as the drive machine, but a gas turbine or the like may be used, for example.

  DESCRIPTION OF SYMBOLS 1 ... Turbo compressor, B ... Reference plane, M ... Drive motor (drive machine), 51 ... Bull gear (gear), 52 ... Bull gear shaft (rotor), 54 ... Low-speed pinion shaft (second rotor), 56 ... High speed Pinion shaft (third rotor), 58, 59 ... thrust collar, 60 ... bearing, 60A ... first bearing, 60B ... second bearing, 61 ... journal bearing portion, 61a ... journal surface, 61b ... oil supply groove, 62 ... Thrust bearing part, 75 ... Bearing fixing hole (fixing part, first fixing part, second fixing part), 100 ... dividing surface

Claims (8)

An oil supply groove is formed along the axial direction of the rotor on the rotor provided along the reference plane and rotationally driven by a driving machine, and on the journal surface facing the circumferential surface of the rotor, and along the oil supply groove. And a bearing having a split surface that can be split,
The turbo compressor according to claim 1, wherein the dividing surface is disposed at a position different from a direction of a load applied to the journal surface from the rotor that is rotationally driven.   A fixing portion for fixing the bearing in a posture in which the dividing surface is inclined with respect to the reference plane based on a load including a horizontal component applied to the journal surface from the rotor that is rotationally driven; The turbo compressor according to claim 1.   The turbo compressor according to claim 1, wherein the dividing surface is inclined with respect to a horizontal plane. The rotor has a gear that rotationally drives the second rotor and the third rotor,
The bearing has a first bearing provided on the driving machine side with the gear interposed therebetween, and a second bearing provided on the opposite side of the driving machine with the gear interposed therebetween,
The fixing portion includes a first fixing portion that fixes the first bearing in a first posture, and a second fixing portion that fixes the second bearing in the first posture. The turbo compressor as described in any one of Claims 1-3 characterized by the above-mentioned. The rotor has a gear that rotationally drives the second rotor and the third rotor,
The bearing has a first bearing provided on the driving machine side with the gear interposed therebetween, and a second bearing provided on the opposite side of the driving machine with the gear interposed therebetween,
The fixing portion includes a first fixing portion that fixes the first bearing in a first posture, and a second fixing portion that fixes the second bearing in a second posture different from the first posture. The turbo compressor according to any one of claims 1 to 3, wherein   6. The turbo compressor according to claim 4, wherein each of the second rotor and the third rotor has a thrust collar capable of contacting the gear in the axial direction.   The said 2nd rotor and the said 3rd rotor are provided along the said reference plane, respectively, and have the positional relationship which pinched | interposed the said rotor, It is any one of Claims 4-6 characterized by the above-mentioned. The turbo compressor described.   The turbo bearing according to claim 1, wherein the bearing includes a journal bearing portion having the journal surface and a thrust bearing portion provided integrally with the journal bearing portion. Compressor.

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