Bearing supporting structure of centrifugal or turbine fluid machine

Abstract

According to the bearing supporting structure of the centrifugal or turbine fluid machine, the cylindrical roller bearing and the thrust roller bearing are combined to serve as the bearing supporting structure of the driving part, the self-aligning ball bearing and the thrust ball bearing are combined to serve as the bearing supporting structure of the driven part, and the influence of overlapped vibration or disturbance is weakened by combining the two stages of springs; the operation stability is improved; a double-suction impeller is installed on the rotating shaft in the balance shell and accelerates flowing of cooling fluid in the driving cooling flow channel and the driven cooling flow channel, so that the bearing structure is easier to dissipate heat and stable in operation. The active lubricating flow channel is communicated with a cavity of the active buffer spring; the active cooling flow channel is communicated with a right inlet fluid of the double-suction impeller; the driven lubricating flow channel is communicated with a cavity of the driven buffer spring; the driven cooling flow channel is communicated with a left inlet fluid of the double-suction impeller; due to the arrangement of the structure, the lubricating effect of the bearing structures on the two sides is better, the friction loss is reduced, and the service life is prolonged.

Description

Technical Field

[0001] The present invention relates to the technical field of fluid machinery, and particularly relates to a bearing support structure, and more particularly to a bearing support structure for a centrifugal or turbomachinery fluid machine. Background Art

[0002] A bearing is a component in a machine that supports a rotating part, which can reduce friction and support loads. Bearings in fluid machinery need to cope with complex working conditions, and their selection and technological innovation directly affect the efficiency and reliability of the equipment.

[0003] Under high-temperature and high-speed working conditions, the problems of stable operation, lubrication, and cooling of bearings are particularly prominent. How to improve their operating stability, lubrication performance, and cooling effect is a problem that needs to be directly faced currently. Thus, it is very necessary to optimize the design of the bearing support structure.

[0004] The prior art CN102410242A discloses a sliding bearing of a magnetic pump and its clearance compensation structure, including a bearing bush 4 sleeved on an impeller shaft 8, and a bearing housing 3 for installing the bearing bush 4 and connected to a pump body 1. At least one limiting platform 41 for preventing its rotation is provided on the outer circumference of the bearing bush 4, and the limiting platform 41 is a flat platform or a convex platform. A flat platform or a groove adapted to the limiting platform 41 is provided in a bearing bush installation hole on the bearing housing 3. It can effectively avoid the phenomenon that the bearing bush follows the rotation due to insufficient interference when the temperature changes in the traditional structure, making the assembly and replacement operations of the bearing bush simpler and easier, and the bearing bush will not be damaged by extrusion during the assembly process; it plays a better protective role for the bearing bush.

[0005] However, the above-mentioned bearing does not involve relatively prominent problems such as lubrication and cooling, and the means for its stable operation are too single, and the conversion and application effects are not good. Therefore, in view of these problems, the applicant proposes a bearing support structure for a centrifugal or turbomachinery fluid machine to solve the above-mentioned problems and improve the working condition performance and efficiency. Summary of the Invention

[0006] The purpose of the present invention is to solve the drawbacks existing in the prior art, and to propose a bearing support structure for a centrifugal or turbomachinery fluid machine.

[0007] In order to achieve the above purpose, the present invention adopts the following technical solutions:

[0008] A bearing support structure for a centrifugal or turbine fluid machine, wherein the centrifugal or turbine fluid machine includes a balance housing. The right end of the balance housing is connected to the active part through an active bearing structure, and the left end is connected to the driven part through a driven bearing structure. The rotating shaft sequentially passes through the active part, the active bearing structure, the balance housing, the driven bearing structure, and the driven part. The active part includes an active impeller and an active inlet housing, and the driven part includes a driven impeller and a driven outlet housing. It is characterized in that: a double-suction impeller is installed on the rotating shaft inside the balance housing. One end of the active fixed seat in the active bearing structure is connected to the right end of the balance housing. The other end of the active fixed seat is respectively fixedly connected to the upper ends of a cylindrical roller bearing and a thrust roller bearing on both sides. An active buffer spring is arranged between one side of the lower end of the cylindrical roller bearing and one side of the lower end of the thrust roller bearing. The other side of the lower end of the thrust roller bearing is fixed through an active thrust limit projection. The active support ring is installed on the rotating shaft on the side of the active thrust limit projection away from the active impeller. The active support ring is connected to the thrust roller bearing through an active balance spring. The active lubrication flow channel communicates with the cavity of the active buffer spring. An active cooling flow channel is arranged at the right end of the rotating shaft, and the active cooling flow channel is in fluid communication with the right-side inlet of the double-suction impeller. In the driven bearing structure, one end of the driven fixed seat is connected to the left end of the balance housing. The other end of the driven fixed seat is respectively fixedly connected to the upper ends of a spherical roller bearing and a thrust ball bearing on both sides. A driven buffer spring is arranged between one side of the lower end of the spherical roller bearing and one side of the lower end of the thrust ball bearing. The other side of the lower end of the thrust ball bearing is fixed through a driven thrust limit projection. The driven support ring is installed on the rotating shaft on the side of the driven thrust limit projection away from the driven impeller. The driven support ring is connected to the thrust ball bearing through a driven balance spring. The driven lubrication flow channel communicates with the cavity of the driven buffer spring. A driven cooling flow channel is arranged at the left end of the rotating shaft, and the driven cooling flow channel is in fluid communication with the left-side inlet of the double-suction impeller.

[0009] Further, the cross-sections of the active support ring and the driven support ring are in a "Γ" shape structure, and there are gaps between the active support ring and the driven support ring and the thrust roller bearing and the thrust ball bearing.

[0010] Further, the radial heights of the active thrust limit projection and the driven thrust limit projection are less than the radial heights of the active support ring and the driven support ring.

[0011] Further, the driven part further includes a nozzle and a nozzle seat. The nozzle is fixed to one end of the driven impeller, and the nozzle seat is fixedly connected to the driven fixed seat.

[0012] Further, a lubricant inlet is arranged at the upper part of the balance housing, and an exhaust port is arranged at the lower part.

[0013] Further, a pressure sensor is arranged on the inner wall of the balance housing.

[0014] Furthermore, there are sealing compensation rings between the active thrust limiting protrusion and the driven thrust limiting protrusion and the thrust roller bearing and the thrust ball bearing respectively, and the sealing compensation rings are made of superelastic materials.

[0015] Furthermore, the double-suction impeller is arranged on the side closer to the active part.

[0016] Furthermore, the right inlet diameter of the double-suction impeller is D1, and the left inlet diameter is D2, where D1 > D2, and D1 = (1.2 - 2.5)D2.

[0017] Furthermore, the right-side blades of the double-suction impeller are twisted blades, and the left-side blades are straight blades.

[0018] Furthermore, the included angle between the outlet edge of the right-side blades and the outlet edge of the left-side blades is A, where 30° < A < 60°.

[0019] Furthermore, the number of blades on the right side is N1, and the number of blades on the left side is N2, where N1 > N2, and N1 = (2 - 3)N2 + 1.

[0020] Furthermore, the active cooling flow channel and the driven cooling flow channel are in a straight line or a square wave shape.

[0021] Furthermore, the outlets of the active cooling flow channel and the driven cooling flow channel are respectively located at the two side inlets of the double-suction impeller 9.

[0022] Furthermore, the included angle between the outlet directions of the active cooling flow channel and the driven cooling flow channel and the central axis of the rotating shaft (3) is 0° to 60°.

[0023] The present invention has the following advantages compared with the prior art:

[0024] 1. An active buffer spring is provided between the lower end side of the cylindrical roller bearing and the lower end side of the thrust roller bearing. The other side of the lower end of the thrust roller bearing is fixed by an active thrust limit projection. The active support ring is installed on the rotating shaft on the side of the active thrust limit projection away from the active impeller. The active support ring and the thrust roller bearing are connected by an active balance spring. A driven buffer spring is provided between the lower end side of the self-aligning ball bearing and the lower end side of the thrust ball bearing. The other side of the lower end of the thrust ball bearing is fixed by a driven thrust limit projection. The driven support ring is installed on the rotating shaft on the side of the driven thrust limit projection away from the driven impeller. The driven support ring and the thrust ball bearing are connected by a driven balance spring. When the active part and the driven part operate, there will be superimposed vibrations or disturbances. Based on this, considering that the axial forces and radial forces borne by the bearings on both sides are different, the active part will have greater axial and radial forces. The applicant selects the combination of a cylindrical roller bearing and a thrust roller bearing as the bearing support structure of the active part, and the combination of a self-aligning ball bearing and a thrust ball bearing as the bearing support structure of the driven part, which can better improve the operating stability based on the operating conditions. In addition, using two-stage springs will weaken the influence of superimposed vibrations or disturbances and can also better improve the operating stability.

[0025] 2. A double-suction impeller is installed on the rotating shaft in the balance housing. The double-suction impeller accelerates the flow of the cooling fluid in the active cooling channel and the driven cooling channel, making it easier for the bearing structure to dissipate heat and operate stably.

[0026] 3. The active lubricating channel communicates with the cavity of the active buffer spring. An active cooling channel is provided at the right end of the rotating shaft, and the active cooling channel is fluidly connected to the right inlet of the double-suction impeller. The driven lubricating channel communicates with the cavity of the driven buffer spring. A driven cooling channel is provided at the left end of the rotating shaft, and the driven cooling channel is fluidly connected to the left inlet of the double-suction impeller. The setting of the above structure makes the lubrication and cooling effects of the bearing structures on both sides better, reduces the loss of friction, and extends the service life. Brief Description of the Drawings

[0027] Figure 1 It is a bearing support structure for a centrifugal or turbine fluid machine;

[0028] Figure 2 It is a double-suction impeller structure.

[0029] In the figure: driving part 1, driving impeller 11, driving inlet housing 12, driven part 2, driven impeller 21, driven outlet housing 22, rotating shaft 3, balance housing 4, nozzle 5, nozzle seat 6, driving bearing structure 7, cylindrical roller bearing 71, driving fixed seat 72, thrust roller bearing 73, driving buffer spring 74, driving lubricating flow channel 75, driving balance spring 76, driving support ring 77, driving cooling flow channel 78, driving thrust limit projection 79, driven bearing structure 8, self-aligning ball bearing 81, driven fixed seat 82, thrust ball bearing 83, driven buffer spring 84, driven lubricating flow channel 85, driven balance spring 86, driven support ring 87, driven cooling flow channel 88, driven thrust limit projection 89, double-suction impeller 9, lubricant inlet 10, pressure sensor 11, exhaust port 12, seal compensation ring 13, right-side inlet diameter D1 of double-suction impeller 9, left-side inlet diameter D2 of double-suction impeller 9, included angle A between the right-side blade outlet edge and the left-side blade outlet edge of double-suction impeller 9, number of blades N1 on the right-side blades of double-suction impeller 9, number of blades N2 on the left-side blades of double-suction impeller 9. Detailed implementation manners

[0030] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are some, but not all, of the embodiments of the present invention. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0031] The present invention will be further described in detail below with reference to the accompanying drawings.

[0032] As Figure 1-2As shown, a bearing support structure for a centrifugal or turbomachinery fluid machine, wherein the centrifugal or turbomachinery fluid machine includes a balance housing 4. The right end of the balance housing 4 is connected to the active part 1 through the active bearing structure 7, and the left end is connected to the driven part 2 through the driven bearing structure 8. The rotating shaft 3 sequentially passes through the active part 1, the active bearing structure 7, the balance housing 4, the driven bearing structure 8, and the driven part 2. The active part 1 includes an active impeller 11 and an active inlet housing 12, and the driven part 2 includes a driven impeller 21 and a driven outlet housing 22. It is characterized in that: a double-suction impeller 9 is installed on the rotating shaft 3 in the balance housing 4. One end of the active fixed seat 72 in the active bearing structure 7 is connected to the right end of the balance housing 4. The upper ends of the cylindrical roller bearings 71 and the upper ends of the thrust roller bearings 73 are respectively and fixedly connected to both sides of the other end of the active fixed seat 72. An active buffer spring 74 is provided between one side of the lower end of the cylindrical roller bearing 71 and one side of the lower end of the thrust roller bearing 73. The other side of the lower end of the thrust roller bearing 73 is fixed through an active thrust limit projection 79. An active support ring 77 is installed on the rotating shaft 3 on the side of the active thrust limit projection 79 away from the active impeller 11. The active support ring 77 is connected to the thrust roller bearing 73 through an active balance spring 76. The active lubrication flow channel 75 communicates with the cavity of the active buffer spring 74. An active cooling flow channel 78 is provided at the right end of the rotating shaft 3, and the active cooling flow channel 78 is in fluid communication with the right-side inlet of the double-suction impeller 9. In the driven bearing structure 8, one end of the driven fixed seat 82 is connected to the left end of the balance housing 4. The upper ends of the self-aligning ball bearings 81 and the upper ends of the thrust ball bearings 83 are respectively and fixedly connected to both sides of the other end of the driven fixed seat 82. A driven buffer spring 84 is provided between one side of the lower end of the self-aligning ball bearing 81 and one side of the lower end of the thrust ball bearing 83. The other side of the lower end of the thrust ball bearing 83 is fixed through a driven thrust limit projection 89. A driven support ring 87 is installed on the rotating shaft 3 on the side of the driven thrust limit projection 89 away from the driven impeller 21. The driven support ring 87 is connected to the thrust ball bearing 83 through a driven balance spring 86. The driven lubrication flow channel 85 communicates with the cavity of the driven buffer spring 84. A driven cooling flow channel 88 is provided at the left end of the rotating shaft 3, and the driven cooling flow channel 88 is in fluid communication with the left-side inlet of the double-suction impeller 9.

[0033] Among them, an active buffer spring is provided between one side of the lower end of the cylindrical roller bearing and one side of the lower end of the thrust roller bearing. The other side of the lower end of the thrust roller bearing is fixed by an active thrust limiting protrusion. The active support ring is installed on the rotating shaft on the side of the active thrust limiting protrusion away from the active impeller. The active support ring and the thrust roller bearing are connected by an active balance spring; a driven buffer spring is provided between one side of the lower end of the self-aligning ball bearing and one side of the lower end of the thrust ball bearing. The other side of the lower end of the thrust ball bearing is fixed by a driven thrust limiting protrusion. The driven support ring is installed on the rotating shaft on the side of the driven thrust limiting protrusion away from the driven impeller. The driven support ring and the thrust ball bearing are connected by a driven balance spring; there will be superimposed vibrations or disturbances when the active part and the driven part operate. Based on this, considering that the axial forces and radial forces borne by the bearings on both sides are different, the active part will have greater axial and radial forces. The applicant selects the combination of a cylindrical roller bearing and a thrust roller bearing as the bearing support structure for the active part, and the combination of a self-aligning ball bearing and a thrust ball bearing as the bearing support structure for the driven part, which can better improve the running stability based on the operating conditions; in addition, using two-stage springs will weaken the influence of the superimposed vibrations or disturbances and can also better improve the running stability.

[0034] Secondly, a double-suction impeller is installed on the rotating shaft in the balance housing. The double-suction impeller accelerates the flow of the cooling fluid in the active cooling channel and the driven cooling channel, making it easier for the bearing structure to dissipate heat and operate stably.

[0035] Thirdly, the active lubricating channel communicates with the cavity of the active buffer spring. An active cooling channel is provided at the right end of the rotating shaft, and the active cooling channel is in fluid communication with the right-side inlet of the double-suction impeller; the driven lubricating channel communicates with the cavity of the driven buffer spring. A driven cooling channel is provided at the left end of the rotating shaft, and the driven cooling channel is in fluid communication with the left-side inlet of the double-suction impeller; the above structure settings make the lubrication and cooling effects of the bearing structures on both sides better, reduce the loss of friction, and extend the service life.

[0036] Furthermore, the cross-sections of the active support ring 77 and the driven support ring 87 are in a "Γ" shape structure, and there are gaps between the active support ring 77 and the driven support ring 87 and the thrust roller bearing 73 and the thrust ball bearing 83.

[0037] Furthermore, the radial heights of the active thrust limiting protrusion 79 and the driven thrust limiting protrusion 89 are smaller than the radial heights of the active support ring 77 and the driven support ring 87.

[0038] The above structure settings can better support the thrust roller bearing 73 and the thrust ball bearing 83 to improve the running stability of the device.

[0039] Furthermore, the driven part 2 further includes a nozzle 5 and a nozzle seat 6. The nozzle 5 is fixed to one end of the driven impeller 21, and the nozzle seat 6 is fixedly connected to the driven fixed seat 82.

[0040] Furthermore, a lubricant inlet 10 is provided at the upper part of the balance housing 4, and an exhaust port 12 is provided at the lower part.

[0041] Furthermore, a pressure sensor 11 is provided on the inner wall of the balance housing 4.

[0042] When the pressure in the balance housing 4 is too high, the pressure sensor 11 senses the pressure in time. When the pressure exceeds the preset value, the exhaust port 12 opens and decompression is carried out.

[0043] Furthermore, there are sealing compensation rings 13 between the active thrust limiting protrusion 79 and the driven thrust limiting protrusion 89 and the thrust roller bearing 73 and the thrust ball bearing 83 respectively. The sealing compensation rings 13 are made of superelastic materials.

[0044] The sealing compensation rings 13 improve the sealing stability and reduce the loss of lubricating fluid.

[0045] Furthermore, the double-suction impeller 9 is arranged on the side closer to the active part 1.

[0046] Furthermore, the diameter of the right inlet of the double-suction impeller 9 is D1, and the diameter of the left inlet is D2, where D1 > D2, and D1 = (1.2 - 2.5)D2.

[0047] Furthermore, the right blades of the double-suction impeller 9 are twisted blades, and the left blades are straight blades.

[0048] Furthermore, the included angle between the outlet edge of the right blade and the outlet edge of the left blade is A, where 30° < A < 60°.

[0049] Furthermore, the number of blades on the right side of the double-suction impeller 9 is N1, and the number of blades on the left side is N2, where N1 > N2, and N1 = (2 - 3)N2 + 1.

[0050] In view of the fact that there will be greater axial force and radial force in the active part, the applicant, considering the need for cooling and heat dissipation, arranges the double-suction impeller on the side close to the active part, and at the same time optimizes the structure of the right impeller to better dissipate heat and cool the spherical roller bearing and the thrust ball bearing.

[0051] Furthermore, the active cooling channel 78 and the driven cooling channel 88 are linear or square-wave shaped.

[0052] Furthermore, the outlets of the active cooling channel 78 and the driven cooling channel 88 are respectively located at the two inlet sides of the double-suction impeller 9.

[0053] Furthermore, the included angle between the outlet directions of the active cooling channel 78 and the driven cooling channel 88 and the central axis of the rotating shaft (3) is 0° to 60°.

[0054] The structures of the active cooling channels and the passive cooling channels are set to form a better optimized design with the double-suction impeller, so as to improve the pumping efficiency and enhance the cooling and heat dissipation effect.

Claims

1. A bearing support structure for a centrifugal or turbine fluid machinery, wherein the centrifugal or turbine fluid machinery comprises a balancing housing (4), the right end of the balancing housing (4) is connected to an active part (1) via an active bearing structure (7), and the left end is connected to a driven part (2) via a driven bearing structure (8); a rotating shaft (3) passes through the active part (1), the active bearing structure (7), the balancing housing (4), the driven bearing structure (8), and the driven part (2) in sequence; the active part (1) comprises an active impeller (11) and an active inlet shell (12), and the driven part (2) comprises a driven impeller (21) and a driven outlet shell (22); the characteristics are: A double-suction impeller (9) is installed on the rotating shaft (3) in the balancing housing (4); one end of an active fixed seat (72) in the active bearing structure (7) is connected to the right end of the balancing housing (4); the other end of the active fixed seat (72) is respectively fixedly connected to the upper end of a cylindrical roller bearing (71) and the upper end of a thrust roller bearing (73); an active buffer spring (74) is arranged between one side of the lower end of the cylindrical roller bearing (71) and one side of the lower end of the thrust roller bearing (73); The other side of the lower end of the rotating shaft (3) is fixed by an active thrust stop limit protrusion (79), an active support ring (77) is installed on the rotating shaft (3) on the side of the active thrust stop limit protrusion (79) away from the active impeller (11), the active support ring (77) and the thrust roller bearing (73) are connected by an active balance spring (76), the active lubrication flow channel (75) is connected to the cavity of the active buffer spring (74), and an active cooling flow channel (78) is arranged at the right end of the rotating shaft (3), and the active cooling flow channel (78) is connected to the double The right inlet of the suction impeller (9) is connected to the fluid; one end of the driven fixed seat (82) in the driven bearing structure (8) is connected to the left end of the balancing housing (4); the other end of the driven fixed seat (82) is respectively fixedly connected to the upper end of the self-aligning ball bearing (81) and the upper end of the thrust ball bearing (83); a driven buffer spring (84) is arranged between one side of the lower end of the self-aligning ball bearing (81) and one side of the lower end of the thrust ball bearing (83); the other side of the lower end of the thrust ball bearing (83) is connected to the driven buffer spring (84) by the driven thrust limit spring (84). The driven support ring (87) is mounted on the rotating shaft (3) at the side of the driven thrust limiting protrusion (89) away from the driven impeller (21); the driven support ring (87) is connected to the thrust ball bearing (83) via a driven balance spring (86); the driven lubrication channel (85) is connected to the cavity of the driven buffer spring (84); a driven cooling channel (88) is provided at the left end of the rotating shaft (3); and the driven cooling channel (88) is connected to the left inlet fluid of the double-suction impeller (9).

2. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 1, characterized in that: The cross-sections of the active support ring (77) and the driven support ring (87) are in a "Γ"-shaped structure, and there are gaps between the active support ring (77) and the driven support ring (87) and the thrust roller bearing (73) and the thrust ball bearing (83).

3. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 1, characterized in that: The radial heights of the active thrust stop limit protrusion (79) and the driven thrust stop limit protrusion (89) are smaller than the radial heights of the active support ring (77) and the driven support ring (87).

4. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 1, characterized in that: The driven part (2) also includes a nozzle (5) and a nozzle seat (6); the nozzle (5) is fixed to one end of the driven impeller (21); and the nozzle seat (6) is fixedly connected to the driven fixed seat (82).

5. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 1, characterized in that: The balancing housing (4) is provided with a lubricant inlet (10) at the top and an exhaust port (12) at the bottom.

6. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 5, characterized in that: A pressure sensor (11) is arranged on the inner wall of the balancing housing (4).

7. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 1, characterized in that: There are sealing compensation rings (13) between the active thrust limit protrusion (79) and the driven thrust limit protrusion (89) and the thrust roller bearing (73) and the thrust ball bearing (83), respectively, and the sealing compensation rings (13) are made of superelastic material.

8. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 1, characterized in that: The double-suction impeller (9) is arranged on a side closer to the active part (1).

9. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 1, characterized in that: The right inlet diameter of the double-suction impeller (9) is D1, and the left inlet diameter is D2, wherein D1>D2, and D1=(1.2-2.5)D2.

10. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 9, characterized in that: The right blades of the double-suction impeller (9) are twisted blades, and the left blades are straight blades.

11. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 10, characterized in that: The included angle between the right blade outlet edge and the left blade outlet edge is A, wherein 30°<A<60°.

12. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 11, characterized in that: The number of blades on the right side is N1, and the number of blades on the left side is N2, wherein N1>N2, and N1=(2-3)N2+1.

13. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 1, characterized in that: The active cooling channel (78) and the passive cooling channel (88) are in a straight line or square wave shape.

14. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 13, characterized in that: The outlets of the active cooling channel (78) and the passive cooling channel (88) are respectively located at the inlets on both sides of the double-suction impeller (9).

15. A bearing support structure for a centrifugal or turbine fluid machinery as claimed in claim 14, characterized in that: The angle between the outlet directions of the active cooling channel (78) and the driven cooling channel (88) and the central axis of the rotating shaft (3) is 0° to 60°.

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