A bearing support structure for a centrifugal or turbomachinery

Abstract

The bearing support structure of the centrifugal or turbine fluid machine of the application adopts the combination of cylindrical roller bearings and thrust roller bearings as the bearing support structure of the driving part, the combination of self-aligning ball bearings and thrust ball bearings as the bearing support structure of the driven part, and the combination of two-stage spring weakening and superposition of vibration or disturbance to improve the stability of operation; the rotating shaft in the balance casing is provided with a double-suction impeller, the double-suction impeller accelerates the flow of the cooling fluid in the driving cooling flow channel and the driven cooling flow channel, and the bearing structure is easier to dissipate heat and operate stably. The driving lubrication flow channel is communicated with the cavity of the driving buffer spring, the driving cooling flow channel is in fluid communication with the right side inlet of the double-suction impeller; the driven lubrication flow channel is communicated with the cavity of the driven buffer spring, and the driven cooling flow channel is in fluid communication with the left side inlet of the double-suction impeller; the above structure makes the lubrication effect of the bearing structures on both sides better, reduces the loss of friction, and prolongs the service life.

Description

Technical Field

[0001] This invention relates to the field of fluid machinery technology, specifically to a bearing support structure, and more specifically to a bearing support structure for centrifugal or turbine fluid machinery. Background Technology

[0002] Bearings are mechanical components that support rotating parts, reducing friction and supporting loads. In fluid machinery, bearings must withstand complex operating conditions, and their selection and technological innovation directly impact equipment efficiency and reliability.

[0003] Bearings face particularly critical challenges in stable operation, lubrication, and cooling under high-temperature and high-speed conditions. Improving their operational stability, lubrication performance, and cooling efficiency are pressing issues that require immediate attention. Therefore, optimizing the design of the bearing support structure is essential.

[0004] Existing technology CN102410242A discloses a sliding bearing for a magnetic pump and its clearance compensation structure, including a bearing bush 4 sleeved on an impeller shaft 8, and a bearing housing 3 connected to the pump body 1 and mounting the bearing bush 4. At least one limiting platform 41 is provided on the outer circumference of the bearing bush 4 to prevent its rotation. The limiting platform 41 is a platform or a boss. The bearing bush mounting hole on the bearing housing 3 has a platform or groove adapted to the limiting platform 41. This effectively avoids the phenomenon of insufficient interference causing the bearing bush to rotate during temperature changes, which is common in traditional structures. It simplifies and facilitates the assembly and replacement of the bearing bush, preventing damage from compression during assembly and providing better protection for the bearing bush.

[0005] However, the aforementioned bearings do not address relatively prominent issues such as lubrication and cooling, and their stable operation relies on overly simplistic methods, resulting in poor application conversion effects. Therefore, in response to these issues, the applicant proposes a bearing support structure for centrifugal or turbine fluid machinery to solve the aforementioned problems and improve operating performance and efficiency. Summary of the Invention

[0006] The purpose of this invention is to address the shortcomings of existing technologies by proposing a bearing support structure for centrifugal or turbine fluid machinery.

[0007] To achieve the above objectives, the present invention adopts the following technical solution:

[0008] A bearing support structure for centrifugal or turbine fluid machinery, wherein the centrifugal or turbine fluid machinery includes a balance housing, the right end of which is connected to the active part via an active bearing structure, and the left end of which is connected to the driven part via a driven bearing structure; a rotating shaft passes sequentially 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; characterized in that: a double suction impeller is installed on the rotating shaft inside the balance housing; one end of the active fixing seat in the active bearing structure is connected to the right end of the balance housing, and the other end of the active fixing seat is fixedly connected to the upper ends of a cylindrical roller bearing and a thrust roller bearing on both sides respectively; 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; and an active support ring is installed on the active thrust limiting protrusion away from the active impeller. On the side of the rotating shaft, the active support ring and the thrust roller bearing are connected by an active balance spring. The active lubrication channel is connected to the cavity of the active buffer spring. An active cooling channel is provided at the right end of the rotating shaft, which is in fluid communication with the right 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 fixedly connected to the upper end of the self-aligning ball bearing and the upper end of the thrust ball bearing on both sides respectively. A driven buffer spring is provided between the lower end of the self-aligning ball bearing and the lower end of the thrust ball bearing. The other 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. The driven lubrication channel is connected to the cavity of the driven buffer spring. A driven cooling channel is provided at the left end of the rotating shaft, which is in fluid communication with the left inlet of the double suction impeller.

[0009] Furthermore, the active support ring and the driven support ring have a "Γ" shaped cross-section, 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] Furthermore, the radial heights of the active thrust limiting protrusion and the driven thrust limiting protrusion are smaller than the radial heights of the active support ring and the driven support ring.

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

[0012] Furthermore, the upper part of the balance housing is provided with a lubricant inlet, and the lower part is provided with an exhaust port.

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

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

[0015] Furthermore, the dual-suction impeller is positioned 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 blade of the double-suction impeller is a curved-twisted blade, while the left blade is a straight-plate blade.

[0018] Furthermore, the angle between the exit edge of the right blade and the exit edge of the left blade is A, where 30° < A < 60°.

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

[0020] Furthermore, the active cooling channel and the driven cooling channel are either straight or square wave shaped.

[0021] Furthermore, the outlets of the active cooling channel and the driven cooling channel are located at the inlets on both sides of the double suction impeller 9.

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

[0023] Compared with the prior art, the present invention has the following advantages:

[0024] 1. An active buffer spring is installed between one lower end of the cylindrical roller bearing and one lower end of the thrust roller bearing. The other lower end of the thrust roller bearing is fixed by an active thrust limiting protrusion. An active support ring is installed on the 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. 2. A driven buffer spring is installed between one lower end of the self-aligning ball bearing and one lower end of the thrust ball bearing. The other lower end of the thrust ball bearing is fixed by a driven thrust limiting protrusion. A driven support ring is installed on the shaft on the side of the driven thrust limiting protrusion away from the driven impeller. The support ring and the thrust ball bearing are connected by a driven balancing spring. During operation, the driving and driven parts experience superimposed vibrations or disturbances. Considering the difference in axial and radial forces on the bearings on both sides, with the driving part experiencing greater axial and radial forces, the applicant chose a combination of cylindrical roller bearings and thrust roller bearings as the bearing support structure for the driving part, and a combination of self-aligning ball bearings and thrust ball bearings as the bearing support structure for the driven part. This approach better improves operational stability based on the operating conditions. Furthermore, using a two-stage spring reduces the impact of superimposed vibrations or disturbances, further enhancing operational stability.

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

[0026] 3. The active lubrication channel is connected to the cavity of the active buffer spring, and an active cooling channel is provided at the right end of the shaft, which is in fluid communication with the right inlet of the double suction impeller; the driven lubrication channel is connected to the cavity of the driven buffer spring, and a driven cooling channel is provided at the left end of the shaft, which is in fluid communication with the left inlet of the double suction impeller; the above structure configuration improves the lubrication and cooling effect of the bearing structure on both sides, reduces friction loss, and extends service life. Attached Figure Description

[0027] Figure 1 For bearing support structures of centrifugal or turbine fluid machinery;

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

[0029] In the diagram: 1. Active part, 11. Active impeller, 12. Active inlet housing, 2. Driven part, 21. Driven impeller, 22. Driven outlet housing, 3. Shaft, 4. Balance housing, 5. Nozzle, 6. Nozzle seat, 7. Active bearing structure, 71. Cylindrical roller bearing, 72. Active fixed seat, 73. Thrust roller bearing, 74. Active buffer spring, 75. Active lubrication channel, 76. Active balance spring, 77. Active support ring, 78. Active cooling channel, 79. Active thrust limiting protrusion, 81. Driven bearing structure, 82. Self-aligning ball bearing, 81. Driven fixed seat, 82. Thrust ball bearing. 83. Bearing; 84. Driven buffer spring; 85. Driven lubrication channel; 86. Driven balance spring; 87. Driven support ring; 88. Driven cooling channel; 89. Driven thrust limit protrusion; 9. Double suction impeller; 10. Lubricant inlet; 11. Pressure sensor; 12. Exhaust port; 13. Sealing compensation ring; 14. Right inlet diameter D1 of double suction impeller 9; 15. Left inlet diameter D2 of double suction impeller 9; 16. Angle A between the right blade outlet edge and the left blade outlet edge of double suction impeller 9; 17. Number of blades N1 on the right side of double suction impeller 9; 18. Number of blades N2 on the left side of double suction impeller 9. Detailed Implementation

[0030] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

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

[0032] like Figure 1-2As shown, a bearing support structure for centrifugal or turbine fluid machinery includes a balance housing 4. The right end of the balance housing 4 is connected to the active part 1 via an active bearing structure 7, and the left end is connected to the driven part 2 via a driven bearing structure 8. A rotating shaft 3 passes sequentially 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. The characteristic feature is that the rotating shaft 3 inside the balance housing 4... The active bearing structure 7 is equipped with a double-suction impeller 9. One end of the active fixing seat 72 is connected to the right end of the balance housing 4. The other end of the active fixing seat 72 is fixedly connected to the upper ends of the cylindrical roller bearing 71 and the upper ends of the thrust roller bearing 73 on both sides. An active buffer spring 74 is provided between the lower end of the cylindrical roller bearing 71 and the lower end of the thrust roller bearing 73. The other lower end of the thrust roller bearing 73 is fixed by an active thrust limiting protrusion 79. An active support ring 77 is installed on the side of the active thrust limiting protrusion 79 away from the active impeller 11. On shaft 3, the active support ring 77 and the thrust roller bearing 73 are connected by an active balance spring 76. The active lubrication channel 75 is connected to the cavity of the active buffer spring 74. An active cooling channel 78 is provided at the right end of the shaft 3, and the active cooling channel 78 is connected to the right inlet fluid 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 other end of the driven fixed seat 82 is fixedly connected to the upper end of the self-aligning ball bearing 81 and the upper end of the thrust ball bearing 83 on both sides respectively. The lower end of the self-aligning ball bearing 81 is connected to the thrust roller bearing 83 on one side. A driven buffer spring 84 is provided between the lower end of the push ball bearing 83 and one side. The lower end of the thrust ball bearing 83 is fixed by a driven thrust limiting protrusion 89. A driven support ring 87 is installed on the shaft 3 on the side of the driven thrust limiting protrusion 89 away from the driven impeller 21. The driven support ring 87 and the thrust ball bearing 83 are connected by a driven balance spring 86. A 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 shaft 3. The driven cooling channel 88 is in fluid communication with the left inlet of the double suction impeller 9.

[0033] In this design, an active buffer spring is installed between one lower end of the cylindrical roller bearing and one lower end of the thrust roller bearing. The other lower end of the thrust roller bearing is fixed by an active thrust limiting protrusion. An active support ring is mounted on the 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 installed between one lower end of the self-aligning ball bearing and one lower end of the thrust ball bearing. The other lower end of the thrust ball bearing is fixed by a driven thrust limiting protrusion. A driven support ring is mounted on the shaft on the side of the driven thrust limiting protrusion away from the driven impeller. The moving support ring and the thrust ball bearing are connected by a driven balance spring. During operation, the driving and driven parts experience superimposed vibrations or disturbances. Considering the difference in axial and radial forces on the bearings on both sides, with the driving part experiencing greater axial and radial forces, the applicant chose a combination of cylindrical roller bearings and thrust roller bearings as the bearing support structure for the driving part, and a combination of self-aligning ball bearings and thrust ball bearings as the bearing support structure for the driven part. This approach better improves operational stability based on the operating conditions. Furthermore, using a two-stage spring reduces the impact of superimposed vibrations or disturbances, further enhancing operational stability.

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

[0035] Furthermore, the active lubrication channel is connected to the cavity of the active buffer spring, and an active cooling channel is provided at the right end of the shaft, which is in fluid communication with the right inlet of the double suction impeller; the driven lubrication channel is connected to the cavity of the driven buffer spring, and a driven cooling channel is provided at the left end of the shaft, which is in fluid communication with the left inlet of the double suction impeller; the above structure configuration improves the lubrication and cooling effect of the bearing structure on both sides, reduces friction loss, and extends service life.

[0036] Furthermore, the active support ring 77 and the driven support ring 87 have a "Γ" shaped cross-section, and there is a gap 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 less than the radial heights of the active support ring 77 and the driven support ring 87.

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

[0039] Furthermore, 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.

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

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

[0042] When the pressure inside 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 the pressure is reduced.

[0043] Furthermore, the active thrust limiting protrusion 79 and the driven thrust limiting protrusion 89 are respectively connected to the thrust roller bearing 73 and the thrust ball bearing 83 by sealing compensation rings 13, which are made of superelastic material.

[0044] The sealing compensation ring 13 improves the stability of the seal and reduces the loss of lubricant.

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

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

[0047] Furthermore, the right blade of the double-suction impeller 9 is a curved and twisted blade, while the left blade is a straight blade.

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

[0049] Furthermore, the number of leaves on the right side is N1, and the number of leaves on the left side is N2, where N1 > N2, and N1 = (2~3)N2+1.

[0050] Given that the active part will have greater axial and radial forces, the applicant, taking into account the need for cooling and heat dissipation, placed the double suction impeller on the side closer to the active part, while optimizing the structure of the right impeller to better dissipate heat and cool the self-aligning ball bearing and thrust ball bearing.

[0051] Furthermore, the active cooling channel 78 and the passive cooling channel 88 are either straight or square wave shaped.

[0052] Furthermore, the outlets of the active cooling channel 78 and the passive cooling channel 88 are located at the inlets on both sides of the double-suction impeller 9.

[0053] Furthermore, 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°.

[0054] The active and passive cooling channels are designed to work in conjunction with the dual-suction impeller to improve suction efficiency and enhance cooling performance.

Claims

1. A bearing support structure for centrifugal or turbine fluid machinery, wherein the centrifugal or turbine fluid machinery includes a balancing housing (4), the right end of the balancing housing (4) is connected to the driving part (1) via a driving bearing structure (7), and the left end is connected to the driven part (2) via a driven bearing structure (8); a rotating shaft (3) passes sequentially through the driving part (1), the driving bearing structure (7), the balancing housing (4), the driven bearing structure (8), and the driven part (2); the driving part (1) includes a driving impeller and a driving inlet housing, and the driven part (2) includes a driven impeller (21) and a driven outlet housing (22); characterized in that: A double suction impeller (9) is installed on the rotating shaft (3) inside the balance housing (4). One end of the active fixing seat (72) in the active bearing structure (7) is connected to the right end of the balance housing (4). The other end of the active fixing seat (72) is fixedly connected to the upper end of the cylindrical roller bearing (71) and the upper end of the thrust roller bearing (73) on both sides respectively. An active buffer spring (74) is provided between the lower end of the cylindrical roller bearing (71) and the lower end of the thrust roller bearing (73). The other lower end of the thrust roller bearing (73) is fixed by an active thrust limiting protrusion (79). An active support ring (77) is installed on the main... On the shaft (3) away from the active impeller, the active support ring (77) and the thrust roller bearing (73) are connected by an active balance spring (76). The active lubrication channel (75) is connected to the cavity of the active buffer spring (74). An active cooling channel (78) is provided at the right end of the shaft (3), and the active cooling channel (78) is connected to the right inlet fluid 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), and the other end of the driven fixed seat (82) is fixedly connected to the two sides of the self-aligning ball bearing (81). The upper end of the self-aligning ball bearing (81) and the upper end of the thrust ball bearing (83) are connected. 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 by a driven thrust limiting protrusion (89). A driven support ring (87) is installed on the shaft (3) on the side of the driven thrust limiting protrusion (89) away from the driven impeller (21). The driven support ring (87) and the thrust ball bearing (83) are connected by a driven balance spring (86). The driven lubrication channel (85) is connected to the cavity of the driven buffer spring (84). The shaft (3) A driven cooling channel (88) is provided at the left end, and the driven cooling channel (88) is in fluid communication with the left inlet of the double suction impeller (9); the right inlet diameter of the double suction impeller (9) is D1, and the left inlet diameter is D2, where D1 > D2, and D1 = (1.2~2.5)D2; the right blade of the double suction impeller (9) is a bent-twisted blade, and the left blade is a straight blade; the angle between the outlet edge of the right blade and the outlet edge of the left blade is A, where 30° < A < 60°; the number of blades on the right is N1, and the number of blades on the left is N2, where N1 > N2, and N1 = (2~3)N2+1.

2. The bearing support structure for centrifugal or turbine fluid machinery as described in claim 1, characterized in that, The active support ring (77) and the driven support ring (87) have a "Γ" shaped cross section, and there is a gap 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. The bearing support structure for centrifugal or turbine fluid machinery as described in claim 1, characterized in that, The radial heights of the active thrust limiting protrusion (79) and the driven thrust limiting protrusion (89) are less than the radial heights of the active support ring (77) and the driven support ring (87).

4. The bearing support structure for centrifugal or turbine fluid machinery as described 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. The bearing support structure for centrifugal or turbine fluid machinery as described in claim 1, characterized in that, The balance housing (4) has a lubricant inlet (10) at the top and an exhaust port at the bottom.

6. The bearing support structure for centrifugal or turbine fluid machinery as described in claim 5, characterized in that, A pressure sensor is installed on the inner wall of the balance housing (4).

7. The bearing support structure for centrifugal or turbine fluid machinery as described in claim 1, characterized in that, The active thrust limiting protrusion (79) and the driven thrust limiting protrusion (89) are respectively connected to the thrust roller bearing (73) and the thrust ball bearing (83) with sealing compensation rings (13), and the sealing compensation rings (13) are made of superelastic material.

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

9. The bearing support structure for centrifugal or turbine fluid machinery as described in claim 1, characterized in that, The active cooling channel (78) and the passive cooling channel (88) are either straight or square wave type.

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

11. The bearing support structure for centrifugal or turbine fluid machinery as described in claim 10, characterized in that, The angle between the outlet direction of the active cooling channel (78) and the passive cooling channel (88) and the central axis of the rotating shaft (3) is 0° to 60°.

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