Viscous pumps, bearing devices, and turbine generators

Abstract

To provide a viscous pump that can improve pump efficiency by properly discharging lubricating oil pumped through a flow path. [Solution] The viscous pump of the bearing device of the rotating machine according to the embodiment comprises a pump fixed part and a pump rotating part. The pump fixed part has a flow path outer surface and has a suction hole and a discharge hole. The pump rotating part is positioned on the inner circumference side of the pump fixed part such that a flow path is formed between it and the flow path outer surface along the circumferential direction, and rotates together with the machine shaft about the rotation axis, thereby pressurizing lubricating oil through the flow path from the suction hole to the discharge hole. In the viscous pump, a discharge-side oil reservoir is formed from the outlet position to the discharge hole, with the cross-sectional area gradually decreasing toward the outlet position of the flow path, and an outlet connection surface is formed adjacent to the discharge-side oil reservoir from the outer circumference side, which is tangentially continuous with the flow path outer surface at the outlet position of the flow path.

Description

Technical Field

[0001] Embodiments of the present invention relate to a viscous pump, a bearing device, and a waterwheel generator.

Background Art

[0002] In a waterwheel generator which is a type of rotating equipment, a machine shaft is rotatable about a rotation axis, and a waterwheel is attached to the machine shaft. Then, due to the pressure of the water flowing through the waterwheel, the impeller of the waterwheel rotates, and the machine shaft rotates about the rotation axis. Further, in a waterwheel generator, the machine shaft penetrates through the generator in the axial direction along the rotation axis, and a rotor of the generator is attached to the machine shaft. When the machine shaft rotates about the rotation axis, the rotor of the generator rotates, and electric power is generated in the generator.

[0003] In rotating equipment such as the waterwheel generator as described above, a bearing device is provided, and the machine shaft penetrates through the bearing device in the axial direction. In the bearing device, a viscous pump, bearings, etc. are housed inside an outer box serving as an exterior, and an oil sump for storing lubricating oil is formed inside the outer box. In the bearing device, the machine shaft is rotatably supported about the rotation axis by bearings including a thrust bearing, etc., and the bearings receive the load of the machine shaft. Further, in the bearing device, the pump rotating part of the viscous pump rotates together with the machine shaft about the rotation axis.

[0004] In the viscous pump, the pump rotating part is arranged on the inner peripheral side of the pump fixed part, and a flow path for lubricating oil is formed between the pump fixed part and the pump rotating part. Further, in the viscous pump, suction holes and discharge holes are formed in the pump fixed part. In the bearing device, when the pump rotating part rotates, the lubricating oil in the oil sump flows into the flow path through the suction holes, and the lubricating oil is pressure-fed from the suction holes to the discharge holes through the flow path. Further, in the bearing device, the lubricating oil discharged from the viscous pump through the discharge holes is pressure-fed to an oil cooler outside the outer box, and the lubricating oil cooled by the oil cooler is supplied to the bearings inside the outer box.

Prior Art Documents

[0005] [Patent Document 1] Japanese Patent Application Publication No. 1-88000 [Overview of the project] [Problems that the invention aims to solve]

[0006] As mentioned above, in viscous pumps installed in bearing devices of rotating machinery such as hydroelectric generators, it is required that the lubricating oil pumped through the flow path is properly discharged through the discharge port. Furthermore, it is required that the pump efficiency of viscous pumps be improved.

[0007] The problem that the present invention aims to solve is to provide a viscous pump capable of properly discharging lubricating oil pumped through a flow path and improving pump efficiency, as well as a bearing device and a hydroelectric generator equipped with the viscous pump. [Means for solving the problem]

[0008] In this embodiment, a viscous pump is provided for pumping lubricating oil in a bearing device of a rotating machine. The viscous pump comprises a pump stationary section and a pump rotating section. The pump stationary section has a curved outer surface of a flow path, and a suction hole and a discharge hole are formed in the pump stationary section. The pump rotating section is positioned on the inner circumference side of the pump stationary section such that a flow path for lubricating oil is formed between it and the outer surface of the flow path along the circumferential direction. The pump rotating section rotates together with the machine shaft of the rotating machine around the axis of rotation, thereby pumping lubricating oil through the flow path from the suction hole to the discharge hole. The pump stationary section and the pump rotating section form a discharge-side oil reservoir from the outlet position to the discharge hole, the cross-sectional area of ​​which gradually decreases toward the outlet position of the flow path. The pump stationary section has an outlet connection surface adjacent to the discharge-side oil reservoir from the outer circumference side, which is tangentially continuous with the outer surface of the flow path at the outlet position of the flow path. [Brief explanation of the drawing]

[0009] [Figure 1] Figure 1 is a side view showing an example of a water turbine generator according to this embodiment. [Figure 2] Figure 2 is a cross-sectional view showing an example of the internal configuration of the outer box in the bearing device, which is the turbine-side bearing device of the turbine generator shown in Figure 1. [Figure 3] Figure 3 is a cross-sectional view showing the section along line A1-A1 in Figure 2. [Figure 4] Figure 4 is a schematic diagram showing the path for pumping lubricating oil in a bearing device, which is a turbine-side bearing device of the embodiment. [Figure 5] Figure 5 is a cross-sectional view of the line A2-A2 in Figure 3, with the holder omitted. [Figure 6] Figure 6 is a cross-sectional view showing the suction port, discharge port, and the vicinity thereof in a viscous pump bearing device according to an embodiment. [Figure 7] Figure 7 is a cross-sectional view showing the suction port, discharge port, and the vicinity thereof in a comparative example of a viscous pump. [Figure 8] Figure 8 is a cross-sectional view illustrating an example of the lubricating oil flow velocity in the vicinity of the oil reservoir (discharge side oil reservoir), discharge port, and other components in the configuration of the comparative example shown in Figure 7. [Figure 9] Figure 9 is a cross-sectional view illustrating an example of the flow velocity of lubricating oil in the oil reservoir (discharge side oil reservoir), discharge port, and its vicinity in the viscous pump of the embodiment. [Figure 10] Figure 10 is a schematic diagram showing an example of the pressure distribution of lubricating oil pumped through the flow path for each of the viscous pumps of the embodiment shown in Figure 6 and the comparative example shown in Figure 7. [Figure 11] Figure 11 is a cross-sectional view showing an example of a sealing structure in the flow path of a comparative example viscous pump. [Figure 12] Figure 12 is a cross-sectional view showing an example of the configuration of the oil reservoir (discharge-side oil reservoir), discharge port, and the vicinity thereof in a viscous pump according to the first modified example. [Figure 13] Figure 13 is a cross-sectional view showing an example of the configuration of the oil reservoir (discharge side oil reservoir), discharge port, and the vicinity thereof in a viscous pump according to a second modified example. [Figure 14] Figure 14 is a cross-sectional view showing an example of the configuration of the oil reservoir (discharge side oil reservoir), discharge port, and vicinity thereof in a viscous pump according to the third modified example. [Figure 15] Figure 15 is a cross-sectional view showing an example of the internal configuration of the outer casing box in the bearing device of a hydroelectric generator according to the fourth modified example. [Modes for carrying out the invention]

[0010] The embodiments and other details will be described below with reference to the drawings.

[0011] Figure 1 is a side view showing an example of a hydroelectric generator 1 according to an embodiment. As shown in Figure 1, the hydroelectric generator 1, which is a type of rotating machine, is equipped with a shaft 2, and the shaft 2 has a rotation axis P. The shaft 2 is rotatable about the rotation axis P. In the hydroelectric generator 1, the axial direction along the rotation axis P of the shaft 2, the circumferential direction which is the direction around the axis of rotation axis P, and the radial direction which intersects (is orthogonal or substantially orthogonal to) both the axial and circumferential directions are defined. In addition, in the hydroelectric generator 1, the side that approaches the rotation axis P in the radial direction is the inner circumference side, and the side that moves away from the rotation axis P in the radial direction is the outer circumference side.

[0012] In the example shown in Figure 1, the shaft 2 (rotation axis P and axial direction) extends along the horizontal plane, and the turbine generator 1 becomes a horizontal-axis type turbine generator. In addition, for a horizontal-axis type turbine generator 1, a width direction is defined that intersects (is perpendicular or nearly perpendicular to) both the axial direction and the vertical direction (indicated by arrow Z). Figure 1 shows the turbine generator 1 as viewed from one side in the width direction.

[0013] The waterwheel generator 1 includes a waterwheel 3 and a generator 5. The waterwheel 3 is, for example, a Francis waterwheel, and includes a supply pipe, a waterwheel casing 11, an impeller 12, and a discharge pipe 13. In the waterwheel 3, the impeller 12 is housed inside the waterwheel casing 11, and the waterwheel 3 is attached to the machine shaft 2 in a state where the impeller 12 is fixed to the machine shaft 2. In the waterwheel 3, the impeller 12 rotates due to the pressure of the water flowing from the supply pipe to the discharge pipe 13. Then, when the impeller 12 rotates, power is generated to rotate the machine shaft 2 around the rotation axis P. Therefore, the machine shaft 2 rotates due to the pressure of the water flowing through the waterwheel 3. Note that in the machine shaft 2 of the waterwheel generator 1, an axial thrust force T is generated due to the pressure of the water flowing through the waterwheel 3.

[0014] The generator 5 includes a generator rotor 15. In the waterwheel generator 1, the machine shaft 2 axially penetrates the generator 5, and the generator rotor 15 of the generator 5 is attached to the machine shaft 2. When the machine shaft 2 rotates around the rotation axis P, the generator rotor 15 of the generator 5 rotates, and electric power is generated in the generator 5.

[0015] Also, the waterwheel generator 1 includes an exciter 6 and a brake device 7. In an example of FIG. 1, the exciter 6 and the brake device 7 are arranged away from the generator 5 on the side opposite to the side where the axial waterwheel 3 is located. Also, in an example of FIG. 1, the brake device 7 and the exciter 6 are arranged in this order from the side closer to the generator 5. The exciter 6 includes an exciter rotor 16, and the brake device 7 includes a brake ring 17 and an electromagnetic brake 18. In the waterwheel generator 1, the exciter rotor 16 and the brake ring 17 are attached to the machine shaft 2. Also, in the brake device 7, the rotation of the brake ring 17 is stopped by the electromagnetic brake 18.

[0016] In the example shown in Figure 1, the turbine generator 1 is equipped with two bearing devices 8 and 10, and the shaft 2 passes through each of the bearing devices 8 and 10 in the axial direction. Each of the bearing devices 8 and 10 is equipped with a bearing, and the shaft 2 is rotatably supported about the rotation axis P by the bearings of the bearing devices 8 and 10. The bearings of the bearing devices 8 and 10 also bear the load of the shaft 2. In the example shown in Figure 1, the bearing device 8 is positioned on the opposite side of the generator 5 from the side where the turbine 3 is located in the axial direction, and is positioned between the generator 5 and the brake device 7. The bearing device 10 is positioned on the side of the generator 5 where the turbine 3 is located in the axial direction, and is positioned between the generator 5 and the turbine 3. Here, the bearing device 8 is also referred to as the "anti-turbine side bearing device," and the bearing device 10 is also referred to as the "turbine side bearing device."

[0017] Each of the bearing devices 8 and 10 is equipped with a journal bearing. Each journal bearing in bearing devices 8 and 10 receives the radial load from the shaft 2. This radial load from the shaft 2 is also called the "radial load". In addition, bearing device 10, which is the turbine-side bearing device, is equipped with a thrust bearing in addition to the journal bearing. The thrust bearing in bearing device 10 receives the axial load from the shaft 2 caused by the thrust force T, etc. This axial load from the shaft 2 is also called the "thrust load".

[0018] The bearing device 10, which is the turbine-side bearing device, includes an outer casing box 21 and an oil cooler 22. In the bearing device 10, the shaft 2 passes through the outer casing box 21 in the axial direction. The oil cooler 22 is located outside the outer casing box 21.

[0019] Figure 2 is a cross-sectional view showing an example of the internal configuration of the outer box 21 in the bearing device 10, which is the turbine-side bearing device of the turbine generator 1 shown in Figure 1. In Figure 2, a cross-section perpendicular or approximately perpendicular to the width direction of the turbine generator 1 (bearing device 10) is shown. Therefore, cross-sections along both the vertical direction and the axial direction of the turbine generator 1 are shown. As shown in Figure 2, in the bearing device 10, the thrust bearing 23 and journal bearing 25 mentioned above are housed inside the outer box 21 as bearings. In addition, an oil tank 27 for storing lubricating oil 26 is formed inside the outer box 21. In Figure 2, the oil level L of the lubricating oil 26 stored in the oil tank 27 is shown.

[0020] In the bearing device 10, the viscous pump 30 and holder 31 are housed inside the outer casing 21. Inside the outer casing 21, the holder 31 holds the thrust bearing 23, journal bearing 25, and viscous pump 30 from the outer circumference. The holder 31 is also subjected to loads from the thrust bearing 23 and journal bearing 25. The holder 31 is supported by support members (not shown) fixed to the inner surface of the outer casing 21, such as being sandwiched from both sides in the vertical direction, and is attached to the outer casing 21 via the support members. In the bearing device 10, the shaft 2 passes through the viscous pump 30 and holder 31 in the axial direction.

[0021] Figure 3 is a cross-sectional view showing the section along line A1-A1 in Figure 2. In Figure 3, a cross-section is shown that passes through the viscous pump 30 and is perpendicular or approximately perpendicular to the axial direction. As shown in Figures 2 and 3, the viscous pump 30 includes a pump fixing part 32 and a pump rotating part 33. The pump fixing part 32 is also called the "casing," and the pump rotating part 33 is also called the "collar." The pump rotating part 33 is formed integrally with the machine shaft 2, or is fixed to the machine shaft 2. In addition, the viscous pump 30 also has defined axial, circumferential, and radial directions, similar to the turbine generator 1.

[0022] In the turbine generator 1 and bearing device 10, the shaft 2 rotates around the rotation axis P, causing the pump rotating part 33 of the viscous pump 30 to rotate together with the shaft 2. The viscous pump 30 operates as the pump rotating part 33 rotates around the rotation axis P. As the viscous pump 30 operates, the lubricating oil 26 stored in the oil tank 27 is pumped by the viscous pump 30.

[0023] In the viscous pump 30, the pump rotating part 33 is positioned on the inner circumference side of the pump fixing part 32. In the viscous pump 30, a lubricating oil flow path 35 is formed radially between the pump fixing part 32 and the pump rotating part 33. In the viscous pump 30, the pump fixing part 32 is fixed to the holder 31 from the inner circumference side. As the machine shaft 2 rotates, the pump rotating part 33 rotates around the rotation axis P relative to the holder 31 and the pump fixing part 32.

[0024] In the flow path 35, an inlet position E1 where lubricating oil flows into the flow path 35 and an outlet position E2 where lubricating oil flows out of the flow path 35 are defined. The flow path 35 extends along the longitudinal direction from the inlet position E1 to the outlet position E2. In addition, the flow path 35 has a width direction that intersects (orthogonal or nearly orthogonal to) the longitudinal direction and a height direction that intersects (orthogonal or nearly orthogonal to) both the longitudinal and width directions. In the viscous pump 30, the flow path 35 is formed from the inlet position E1 to the outlet position E2 with its longitudinal direction aligned with the circumferential direction (around the axis). Therefore, in the viscous pump 30, the flow path 35 is formed along the circumferential direction between the pump fixed part 32 and the pump rotating part 33. Furthermore, in the viscous pump 30, the width direction of the flow path 35 is aligned with the axial direction, and the height direction of the flow path 35 is aligned with the radial direction.

[0025] Furthermore, in the viscous pump 30, a suction hole 36 and a discharge hole 37 are formed in the pump fixing part 32. Each of the suction hole 36 and the discharge hole 37 penetrates the pump fixing part 32 in the radial direction. The flow path 35 communicates with the suction port 41 formed in the holder 31 via the suction hole 36, and with the discharge port 42 formed in the holder 31 via the discharge hole 37. Each of the suction hole 36 and the discharge hole 37 is formed in the shape of a rectangular parallelepiped or a substantially rectangular parallelepiped. Therefore, in each of the suction hole 36 and the discharge hole 37, the cross-sectional shape perpendicular to the axial direction of the viscous pump 30, the cross-sectional shape perpendicular to the circumferential direction of the viscous pump 30, and the cross-sectional shape perpendicular to the radial direction of the viscous pump 30 are rectangular or substantially rectangular.

[0026] The rotation of the pump rotating section 33 operates the viscous pump 30, drawing the lubricating oil 26 from the oil tank 27 through the suction port 41 into the suction hole 36. The drawn-in lubricating oil then flows from the suction hole 36 into the flow path 35 and is pumped through the flow path 35 from the suction hole 36 to the discharge port 37. Finally, the lubricating oil is discharged from the discharge port 37 through the discharge port 42 to the outside of the viscous pump 30. Inside the outer box 21, the suction port 41 is immersed in the accumulated lubricating oil 26 in the oil tank 27.

[0027] Figure 4 is a schematic diagram showing the path for pumping lubricating oil 26 in a bearing device 10, which is a turbine-side bearing device of the embodiment. As shown in Figure 4, in the bearing device 10, by operating the viscous pump 30, the lubricating oil 26 stored in the oil tank 27 is drawn into the flow path 35 of the viscous pump 30 through the suction hole 36, and the drawn-in lubricating oil is pumped through the flow path 35 to the discharge hole 37. In the viscous pump 30, the lubricating oil is heated by frictional heat as it passes through the flow path 35. Then, the lubricating oil is discharged to the outside of the viscous pump 30 from the discharge hole 37, and the lubricating oil discharged through the discharge hole 37 is pumped to the oil cooler 22 outside the outer box 21.

[0028] In the oil cooler 22, the pressurized lubricating oil is cooled. The cooled lubricating oil is then pressurized into the outer box 21 and supplied to the thrust bearing 23 and journal bearing 25. In each of the thrust bearing 23 and journal bearing 25, the lubricating oil is heated by sliding friction, etc. Then, the lubricating oil is discharged from each of the thrust bearing 23 and journal bearing 25 into the oil tank 27 inside the outer box 21.

[0029] The following mainly describes the viscous pump 30 of the bearing device 10. As mentioned above, in the viscous pump 30, a flow path 35 is formed radially between the pump fixed part 32 and the pump rotating part 33. Therefore, the outer circumferential surface of the pump rotating part 33 forms an inner flow path surface 43 adjacent to the flow path 35 from the inner circumferential side. Also, the inner circumferential surface of the pump fixed part 32 forms an outer flow path surface 45 adjacent to the flow path 35 from the outer circumferential side. Thus, in the viscous pump 30, a flow path is formed between the inner flow path surface 43 and the outer flow path surface 45 along the circumferential direction (around the axis). Each of the inner flow path surface 43 and the outer flow path surface 45 is formed in a curved shape, and in a cross section perpendicular or approximately perpendicular to the rotation axis P (axial direction), it is in the shape of a circular arc or approximately a circular arc with the rotation axis P as the center or approximately the center.

[0030] Furthermore, in the flow path 35, the cross-sectional area perpendicular to the longitudinal direction (circumferential direction of the viscous pump 30) is uniform or nearly uniform from the inlet position E1 to the outlet position E2. In addition, in the flow path 35, the dimensions along the width direction (axial direction of the viscous pump 30) and the dimensions along the height direction (radial direction of the viscous pump 30) are uniform or nearly uniform from the inlet position E1 to the outlet position E2. Note that the radius of the outer surface 45 of the flow path is larger than the radius of the inner surface 43 of the flow path by the dimension of the flow path 35 along the height direction.

[0031] Figure 5 is a cross-sectional view of the A2-A2 line in Figure 3, with the holder 31 omitted. In Figure 5, a cross-section perpendicular or approximately perpendicular to the circumferential direction (axial direction) of the viscous pump 30 is shown, and a cross-section perpendicular or approximately perpendicular to the longitudinal direction of the flow path 35 is shown. As shown in Figure 5, the viscous pump 30 is provided with sealing members 46 and 47, and each of the sealing members 46 and 47 is fixed to the pump fixing part 32. Therefore, even if the pump rotating part 33 rotates, the sealing members 46 and 47 do not rotate together with the pump rotating part 33. Each of the sealing members 46 and 47 is sandwiched between the outer circumferential surface 45 of the flow path of the pump fixing part 32 and the inner circumferential surface 43 of the flow path of the pump rotating part 33. The sealing member 46 is adjacent to the flow path 35 from one side in the axial direction (width direction of the flow path 35) of the viscous pump 30, and the sealing member 47 is adjacent to the flow path 35 from the side opposite to the side in the axial direction of the viscous pump 30 where the sealing member 46 is located.

[0032] Each of the sealing members 46 and 47 forms a sealing portion between the outer circumferential surface 45 of the flow path and the inner circumferential surface 43 of the flow path to suppress leakage of lubricating oil. The sealing portion formed by the sealing members 46 and 47 suppresses leakage of lubricating oil from the flow path 35 in the width direction of the flow path 35. In the example shown in Figure 5, each of the sealing members 46 and 47 forms a sealing portion only between the outer circumferential surface 45 of the flow path and the inner circumferential surface 43 of the flow path, and no sealing portion is formed by the sealing members 46 and 47 in any other area.

[0033] Figure 6 is a cross-sectional view showing the suction hole 36, discharge hole 37, and the vicinity thereof in the viscous pump 30 of the bearing device 10 of the embodiment. In Figure 6, cross-sections perpendicular or substantially perpendicular to the axial direction (rotation axis P) are shown. As shown in Figure 6, the viscous pump 30 is provided with a sealing member 48, which is fixed to the pump fixing part 32. Therefore, even if the pump rotating part 33 rotates, the sealing member 48 does not rotate together with the pump rotating part 33. The sealing member 48 is sandwiched between the inner circumferential surface of the pump fixing part 32 and the outer circumferential surface of the pump rotating part 33.

[0034] Furthermore, the sealing member 48 is positioned between the suction hole 36 and the discharge hole 37 in the circumferential direction. The suction hole 36 is adjacent to the sealing member 48 from one side in the circumferential direction, and the discharge hole 37 is adjacent to the sealing member 48 from the side opposite to the side where the suction hole 36 is located in the circumferential direction. The sealing member 48 forms a sealing portion between the inner circumferential surface of the pump fixing portion 32 and the outer circumferential surface of the pump rotating portion 33. The sealing portion formed by the sealing member 48 prevents the lubricating oil, which is pressurized to flow through the flow path 35 to the discharge hole 37, from flowing into the suction hole 36.

[0035] Furthermore, in the viscous pump 30, oil reservoirs 51 and 52 are formed by the pump fixed part 32 and the pump rotating part 33, and each of the oil reservoirs 51 and 52 is formed radially between the pump rotating part 33 and the pump fixed part 32. The outer circumferential surface of the pump rotating part 33 is adjacent to each of the oil reservoirs 51 and 52 from the inner circumferential side, and the inner circumferential surface of the pump fixed part 32 is adjacent to each of the oil reservoirs 51 and 52 from the outer circumferential side. In a cross section perpendicular or nearly perpendicular to the rotation axis P (axial direction), the outer circumferential surface of the pump rotating part 33, including the part that forms the inner circumferential surface 43 of the flow path, is in the shape of a circular arc with the rotation axis P as the center or nearly center over the entire circumference in the circumferential direction.

[0036] The oil reservoir (suction-side oil reservoir) 51 is formed along the circumferential direction from the inlet position E1 of the flow path 35 to the suction hole 36. Therefore, one end of the oil reservoir 51 in the circumferential direction is connected to the inlet position E1 of the flow path 35, and the end opposite to the side connected to the flow path 35 in the circumferential direction is connected to the suction hole 36. In the oil reservoir 51, the cross-sectional area perpendicular or nearly perpendicular to the circumferential direction (flow path cross-sectional area) gradually decreases from the suction hole 36 toward the inlet position E1 of the flow path 35.

[0037] The oil reservoir (discharge-side oil reservoir) 52 is formed along the circumferential direction from the outlet position E2 of the flow path 35 to the discharge hole 37. Therefore, one end of the oil reservoir 52 in the circumferential direction is connected to the outlet position E2 of the flow path 35, and the end opposite to the side connected to the flow path 35 in the circumferential direction is connected to the discharge hole 37. In the oil reservoir 52, the cross-sectional area perpendicular or nearly perpendicular to the circumferential direction (flow path cross-sectional area) gradually decreases from the discharge hole 37 toward the outlet position E2 of the flow path 35. That is, in the oil reservoir 52, the cross-sectional area gradually increases toward the discharge hole 37.

[0038] In a viscous pump 30, the pump fixing section 32 includes a suction hole circumferential surface 56 surrounding the suction hole 36 and a discharge hole circumferential surface 57 surrounding the discharge hole 37. The suction hole circumferential surface 56 forms the circumferential surface of the suction hole 36, and the discharge hole circumferential surface 57 forms the circumferential surface of the discharge hole 37. The inner circumferential surface of the pump fixing section 32 includes an inlet connection surface 53 and an outlet connection surface 55. The inlet connection surface 53 is connected to the outer circumferential surface 45 of the flow path 35 at the inlet position E1 and is formed in a location adjacent to the oil reservoir (suction-side oil reservoir) 51 from the outer circumferential side. The outlet connection surface 55 is connected to the outer circumferential surface 45 of the flow path 35 at the outlet position E2 and is formed in a location adjacent to the oil reservoir (discharge-side oil reservoir) 52 from the outer circumferential side.

[0039] In the example shown in Figure 6, the inlet connection surface 53 extends circumferentially from the inlet position E1 to the suction hole circumferential surface 56. Therefore, the end of the inlet connection surface 53 opposite to the side connected to the circumferential flow path outer surface 45 is connected to the suction hole circumferential surface 56. In addition, in the oil reservoir 51, the cross-sectional area (flow path cross-sectional area) gradually decreases toward the inlet position E1 of the flow path 35. Therefore, the distance from the outer surface of the pump rotating part 33 to the inlet connection surface 53 gradually decreases as it approaches the inlet position E1.

[0040] Furthermore, in the example shown in Figure 6, the outlet connection surface 55 extends in the circumferential direction from the outlet position E2 to the discharge hole circumferential surface 57. Therefore, the end of the outlet connection surface 55 opposite to the side connected to the circumferential flow path outer surface 45 is connected to the discharge hole circumferential surface 57. Also, in the oil reservoir 52, the cross-sectional area (flow path cross-sectional area) gradually decreases toward the outlet position E2 of the flow path 35. Therefore, the distance from the outer surface of the pump rotating part 33 to the outlet connection surface 55 gradually decreases as it approaches the outlet position E2.

[0041] Furthermore, in a cross section perpendicular or nearly perpendicular to the axial direction, the tangent α1 of the outer surface 45 of the flow channel 35 at the inlet position E1 and the tangent α2 of the outer surface 45 of the flow channel 35 at the outlet position E2 are defined. That is, the tangent α1 that is tangent to the outer surface 45 of the flow channel at the inlet position E1 and the tangent α2 that is tangent to the outer surface 45 of the flow channel at the outlet position E2 are defined as virtual tangents. In addition, a virtual line segment U1 extending from the connection point of the outer surface 45 of the flow channel 45 with the inlet connection surface 53 to the rotation axis P, which is the center of the outer surface 45 of the flow channel, and a virtual line segment U2 extending from the connection point of the outer surface 45 of the flow channel 45 with the rotation axis P are defined. The angle formed by the tangent α1 and the line segment U1 is a right angle, and the angle formed by the tangent α2 and the line segment U2 is a right angle.

[0042] In the embodiments, the inlet connection surface 53 is linear along the tangent α1 in a cross section perpendicular or nearly perpendicular to the axial direction. Therefore, the inlet connection surface 53 is formed in a planar shape along the tangent α1, and the angle between the inlet connection surface 53 and the aforementioned line segment U1 is a right angle. That is, the inlet connection surface 53 is formed in a planar shape along the tangential direction of the outer surface 45 of the flow path at the inlet position E1 of the flow path 35. Consequently, the inlet connection surface 53 is tangentially continuous with the outer surface 45 of the flow path at the inlet position E1 of the flow path 35. Because the inlet connection surface 53 is tangentially continuous with the outer surface 45 of the flow path, the cross-sectional area (flow path cross-sectional area) in the oil reservoir 51 gradually decreases toward the inlet position E1 of the flow path 35.

[0043] Furthermore, in the embodiments, etc., in a cross-section perpendicular or nearly perpendicular to the axial direction, the outlet connection surface 55 is a straight line along the tangent α2. Therefore, the outlet connection surface 55 is formed in a planar shape along the tangent α2, and the angle between the outlet connection surface 55 and the aforementioned line segment U2 is a right angle. That is, the outlet connection surface 55 is formed in a planar shape along the tangential direction of the outer surface 45 of the flow path at the outlet position E2 of the flow path 35. Therefore, the outlet connection surface 55 is tangentially continuous with the outer surface 45 of the flow path at the outlet position E2 of the flow path 35. Because the outlet connection surface 55 is tangentially continuous with the outer surface 45 of the flow path, in the oil reservoir 52, the cross-sectional area (flow path cross-sectional area) gradually decreases toward the outlet position E2 of the flow path 35. Note that in a configuration in which a curved surface and a plane are connected, when the curved surface and the plane are tangentially continuous, the plane extends along the tangential direction of the curved surface at the connection point of the curved surface and the plane.

[0044] Here, as a comparative example of the embodiment, a viscous pump 30 shown in Figure 7 will be described. Figure 7 is a cross-sectional view showing the suction hole 36, the discharge hole 37, and the vicinity thereof in the comparative example viscous pump 30. In Figure 7, cross-sections perpendicular or approximately perpendicular to the axial direction (rotation axis P) are shown. As shown in Figure 7, in the comparative example viscous pump 30, an oil reservoir (suction-side oil reservoir) 51 is formed along the circumferential direction from the inlet position E1 of the flow path 35 to the suction hole 36, and an oil reservoir (discharge-side oil reservoir) 52 is formed along the circumferential direction from the outlet position E2 of the flow path 35 to the discharge hole 37. In the pump fixing part 32, the inlet connection surface 53 is connected to the outer surface 45 of the flow path at the inlet position E1 of the flow path 35, and the outlet connection surface 55 is connected to the outer surface 45 of the flow path at the outlet position E2 of the flow path 35.

[0045] However, in the comparative example in Figure 7, the inlet connection surface 53 and the outlet connection surface 55 are not tangentially continuous with the outer surface 45 of the flow path. Therefore, when tangents α1 and α2 are defined as described above, in a cross section perpendicular or nearly perpendicular to the axial direction, the inlet connection surface 53 does not follow tangent α1, and the outlet connection surface 55 does not follow tangent α2. Also, when line segments U1 and U2 are defined as described above, the angle between the inlet connection surface 53 and line segment U1 is obtuse, and the angle between the outlet connection surface 55 and line segment U2 is obtuse.

[0046] Due to the configuration described above, in the comparative example, compared to the example in Figure 6 where the inlet connection surface 53 is tangentially continuous with the outer surface of the flow path 45, the change in the distance between the inlet connection surface 53 and the outer surface of the pump rotating part 33 becomes more rapid, and the change in the cross-sectional area (flow path cross-sectional area) of the oil reservoir 51 becomes more rapid. For this reason, in the comparative example, compared to the example in Figure 6, the cross-sectional area of ​​the oil reservoir 51 decreases rapidly toward the inlet position E1 of the flow path 35.

[0047] Furthermore, in the comparative example, compared to the example shown in Figure 6 where the outlet connection surface 55 is tangentially continuous with the outer surface of the flow path 45, the change in the distance between the outlet connection surface 55 and the outer surface of the pump rotating part 33 becomes more rapid, and the change in the cross-sectional area of ​​the oil reservoir 52 (flow path cross-sectional area) becomes more rapid. For this reason, in the comparative example, compared to the example shown in Figure 6, the cross-sectional area of ​​the oil reservoir 52 decreases rapidly toward the outlet position E2 of the flow path 35. In other words, in the comparative example, compared to the example shown in Figure 6, the cross-sectional area of ​​the oil reservoir 52 increases rapidly toward the discharge hole 37.

[0048] Figure 8 is a cross-sectional view illustrating an example of the flow velocity of lubricating oil in the oil reservoir (discharge-side oil reservoir) 52, the discharge port 37, and their vicinity, in the configuration of the comparative example in Figure 7. In Figure 8, cross-sections perpendicular or approximately perpendicular to the axial direction (rotation axis P) are shown. In the example in Figure 8, downstream of the outlet position E2, the flow velocity of the lubricating oil becomes the reference flow velocity in the portion along the dashed line β. Then, downstream of the outlet position E2, the flow velocity of the lubricating oil becomes faster than the reference flow velocity in region Q1, and slower than the reference flow velocity in region Q2. In region Q1, where the flow velocity is faster than the reference flow velocity, the lubricating oil tends to flow more easily toward the discharge port 42 (arrow B1).

[0049] In the comparative example configuration shown in Figure 7, lubricating oil is more easily entangled in the rotation of the pump rotating section 33 in the oil reservoir 52 and discharge port 37, and the lubricating oil is more easily separated from the flow toward the discharge port 42. For this reason, in the comparative example configuration, as shown in Figure 8, the region Q1 where the flow velocity is faster than the reference flow velocity becomes relatively narrow downstream of the outlet position E2, and the region Q2 where the flow velocity is slower than the reference flow velocity becomes relatively wide. As the region Q1 where the flow velocity is faster than the reference flow velocity becomes narrower, the flow rate of lubricating oil flowing toward the discharge port 42 decreases, and the amount of lubricating oil discharged from the viscous pump 30 decreases.

[0050] Furthermore, in the comparative example configuration, the region Q2 where the flow velocity is slower than the reference flow velocity becomes wider, which can cause backflow of lubricating oil separated from the flow toward the discharge port 42 downstream of the outlet position E2 (arrow B2). Due to the occurrence of backflow of lubricating oil, the inflow of lubricating oil from the flow path 35 to the oil reservoir 52 is obstructed, and the flow rate of lubricating oil flowing toward the discharge port 42 decreases.

[0051] Furthermore, in the comparative example configuration, the pressure of the lubricating oil rapidly increases at and near the outlet position E2 of the flow path 35 due to the occurrence of backflow and the rapid change in the cross-sectional area of ​​the oil reservoir 52. As a result, pressure loss occurs as resistance to the flowing lubricating oil at and near the outlet position E2 of the flow path 35. In the comparative example configuration, the discharge pressure of the lubricating oil from the viscous pump 30 is reduced due to the pressure loss at and near the outlet position E2. Due to the phenomena described above, in the comparative example configuration, the flow rate of lubricating oil flowing toward the discharge port 42 decreases, and the amount of lubricating oil discharged from the viscous pump 30 decreases.

[0052] Figure 9 is a cross-sectional view illustrating an example of the flow velocity of lubricating oil in the oil reservoir (discharge side oil reservoir) 52, the discharge port 37, and their vicinity in the viscous pump 30 of the embodiment. In Figure 9, cross-sections perpendicular or approximately perpendicular to the axial direction (rotation axis P) are shown. In the example in Figure 9, downstream of the outlet position E2, the flow velocity of the lubricating oil becomes the reference flow velocity in the portion along the imaginary line β. Then, downstream of the outlet position E2, in region Q1, the flow velocity of the lubricating oil becomes faster than the reference flow velocity, and in region Q2, the flow velocity of the lubricating oil becomes slower than the reference flow velocity.

[0053] In the configuration of this embodiment, lubricating oil is less likely to be entangled in the rotation of the pump rotating part 33 in the oil reservoir 52 and discharge port 37, and lubricating oil is less likely to separate from the flow toward the discharge port 42. For this reason, in the configuration of this embodiment, as shown in Figure 9, the region Q1 where the flow velocity is faster than the reference flow velocity is relatively wide downstream from the outlet position E2, and the region Q2 where the flow velocity is slower than the reference flow velocity is relatively narrow. By widening the region Q1 where the flow velocity is faster than the reference flow velocity, the flow rate of lubricating oil flowing toward the discharge port 42 increases, and the amount of lubricating oil discharged from the viscous pump 30 increases. Furthermore, in the configuration of this embodiment, because the region Q2 where the flow velocity is slower than the reference flow velocity is narrow and lubricating oil is less likely to separate from the flow toward the discharge port 42, backflow of lubricating oil is less likely to occur.

[0054] Furthermore, in the configuration of this embodiment, the cross-sectional area of ​​the oil reservoir 52 changes gradually, so that the pressure of the lubricating oil in the oil reservoir 52 and its vicinity is gradually converted from dynamic pressure to static pressure, and the pressure of the lubricating oil increases gradually. As a result, pressure loss in the flowing lubricating oil downstream of the outlet position E2 is suppressed. In the configuration of this embodiment, the suppression of pressure loss downstream of the outlet position E2 increases the discharge pressure of the lubricating oil from the viscous pump 30. Because of the phenomena described above, in the configuration of this embodiment, the flow rate of the lubricating oil flowing toward the discharge port 42 increases, and the discharge amount of lubricating oil discharged from the viscous pump 30 increases. Therefore, the lubricating oil pumped through the flow path 35 is appropriately discharged from the viscous pump 30.

[0055] Figure 10 is a schematic diagram showing an example of the pressure distribution of lubricating oil pumped through the flow path 35 for the viscous pump 30 of the embodiment shown in Figure 6 and the comparative example viscous pump 30 shown in Figure 7. In Figure 10, the horizontal axis represents the distance from the suction port 41. Therefore, the horizontal axis shows the position in the path of the lubricating oil from the suction port 41 to the discharge port 42, including the flow path 35. In Figure 10, the position corresponding to the suction port 41 and the position corresponding to the discharge port 42 are shown by dashed lines. Also in Figure 10, the vertical axis represents the pressure of the lubricating oil. In Figure 10, the pressure corresponding to atmospheric pressure (0.1013 MPa) is shown by a dashed line. Furthermore, in Figure 10, the pressure change in the viscous pump 30 of the embodiment is shown by a solid line, and the pressure change in the viscous pump 30 of the comparative example is shown by a dashed line.

[0056] In the comparative example configuration, as described above, downstream of outlet position E2, the flow rate of lubricating oil flowing toward discharge port 42 decreases, and the amount of lubricating oil discharged from viscous pump 30 decreases. Therefore, when the pressure of the lubricating oil rises to a pressure higher than atmospheric pressure, i.e., a pressure close to the discharge pressure, at inlet position E1 and its vicinity, the pressure of the lubricating oil is maintained at a high pressure without decreasing. For this reason, in the comparative example configuration, the pressure of the lubricating oil over most of the flow path 35 between inlet position E1 and outlet position E2 is much higher than atmospheric pressure, which corresponds to the pressure outside the viscous pump 30.

[0057] On the other hand, in the viscous pump 30 of the embodiment, the pressure of the lubricating oil rises to a pressure higher than atmospheric pressure at and near the inlet position E1 (range ε1 in Figure 10). However, in the viscous pump of the embodiment, after passing the inlet position E1, the pressure of the lubricating oil decreases in the flow path 35 to atmospheric pressure and near atmospheric pressure, and then to a pressure lower than the discharge pressure. Then, the pressure of the lubricating oil is maintained at atmospheric pressure and near atmospheric pressure until the pressure rises in the oil reservoir (discharge side oil reservoir) 52. For this reason, in the configuration of the embodiment, the pressure of the lubricating oil is maintained at atmospheric pressure and near atmospheric pressure, which corresponds to the pressure outside the viscous pump 30, over most of the flow path 35 between the inlet position E1 and the outlet position E2. Then, in the viscous pump 30 of the embodiment, the pressure of the lubricating oil is slowly converted from dynamic pressure to static pressure in the oil reservoir 52, and the pressure of the lubricating oil rises slowly (range ε2 in Figure 10).

[0058] In this embodiment, the pressure of the lubricating oil is approximately atmospheric pressure over most of the flow path 35 between the inlet position E1 and the outlet position E2. Therefore, the pressure resistance from the lubricating oil acting on the pump rotating part 33, which is the collar, is reduced over most of the flow path 35. As a result, the work (power) required for pumping the lubricating oil through the flow path 35 in the viscous pump 30 is reduced, and the rotational torque of the pump rotating part 33 can be reduced. Consequently, the pumping efficiency of the viscous pump 30 can be improved. By improving the pumping efficiency of the viscous pump 30, the overall operating efficiency of the turbine generator 1 is also improved.

[0059] Figure 11 is a cross-sectional view showing an example of a seal structure in the flow path 35 of a comparative example viscous pump 30. In Figure 11, a cross-section perpendicular or approximately perpendicular to the circumferential direction (axial direction) of the viscous pump 30 is shown, and a cross-section perpendicular or approximately perpendicular to the longitudinal direction of the flow path 35 is shown. In the comparative example of Figure 11, as in the example of Figure 5, seal members 46 and 47 are provided, and each of the seal members 46 and 47 is sandwiched between the outer circumferential surface 45 of the flow path of the pump fixed part 32 and the inner circumferential surface 43 of the flow path of the pump rotating part 33. Each of the seal members 46 and 47 forms a seal portion between the outer circumferential surface 45 and the inner circumferential surface 43 of the flow path to suppress leakage of lubricating oil.

[0060] However, in the comparative example in Figure 11, the pump fixing portion 32 is provided with protruding pieces 65 and 66 that project inward, and the protruding pieces 65 and 66 are formed spaced apart from each other in the axial direction of the viscous pump 30. The protruding piece 65 faces a surface 61 of the pump rotating portion 33 that faces one side in the axial direction, and the protruding piece 66 faces a surface 62 of the pump rotating portion 33 that faces the opposite side from the side that the axial surface 61 faces. In the comparative example in Figure 11, the sealing member 46 is sandwiched between the outer circumferential surface 45 of the flow path and the inner circumferential surface 43 of the flow path, and also sandwiched between the surface 61 of the pump rotating portion 33 and the protruding piece 65 of the pump fixing portion 32. Therefore, the sealing member 46 forms a sealing portion not only between the outer circumferential surface 45 of the flow path and the inner circumferential surface 43 of the flow path, but also between the surface 61 and the protruding piece 65.

[0061] Furthermore, in the comparative example of Figure 11, the sealing member 47 is sandwiched between the outer circumferential surface 45 of the flow path and the inner circumferential surface 43, as well as between the surface 62 of the pump rotating part 33 and the protruding part 66 of the pump fixed part 32. Therefore, the sealing member 47 forms a sealing portion not only between the outer circumferential surface 45 and the inner circumferential surface 43 of the flow path, but also between the surface 62 and the protruding part 66. Due to this configuration, in the comparative example of Figure 11, each of the sealing members 46 and 47 forms a sealing portion not only between the outer circumferential surface 45 and the inner circumferential surface 43 of the flow path, but also in other areas. Consequently, in the comparative example of Figure 11, the sealing structure in the flow path 35 formed by the sealing members 46 and 47 is more complex than in the example of Figure 5, etc.

[0062] In the comparative example viscous pump 30, as described above, the pressure of the lubricating oil is much higher than atmospheric pressure over most of the flow path 35 between the inlet position E1 and the outlet position E2. Therefore, with a seal structure such as the example in Figure 5, there is a possibility that the leakage of lubricating oil from the flow path 35 to the outside of the viscous pump 30 will be large. In other words, in the comparative example configuration, in order to suppress the leakage of lubricating oil from the flow path 35, it is necessary to form a seal portion not only between the outer surface 45 and the inner surface 43 of the flow path, as shown in the configuration in Figure 11, but also in other areas. As a result, the seal structure in the flow path 35 becomes complicated in the comparative example configuration.

[0063] On the other hand, in this embodiment, since the pressure of the lubricating oil is approximately atmospheric pressure over most of the flow path 35, it becomes possible to simplify the sealing structure in the flow path 35 formed by the sealing members 46 and 47. In other words, even if the sealing structure in the flow path 35 is simplified, leakage of lubricating oil from the flow path 35 can be suppressed. In this embodiment, for example, as shown in the example in Figure 5, even if the sealing members 46 and 47 form a sealing portion only between the outer circumferential surface 45 of the flow path and the inner circumferential surface 43 of the flow path, leakage of lubricating oil from the flow path 35 can be appropriately suppressed.

[0064] Furthermore, by changing the seal structure 35 in the flow path from the configuration shown in Figure 11 to the example configuration shown in Figure 5, the friction acting on the pump rotating part 33, which is a collar, by the seal structure is reduced. This makes it possible to further reduce the rotational torque of the pump rotating part 33, and to further improve the pumping efficiency of the viscous pump 30.

[0065] As described above, in this embodiment, an outlet connection surface 55 is formed in the pump fixing part 32 at a portion adjacent to the oil reservoir (discharge side oil reservoir) 52 from the outer circumference side, and the outlet connection surface 55 is tangentially continuous with the outer surface 45 of the flow path 35 at the outlet position E2 of the flow path 35. With this configuration, the phenomenon described above occurs, so that the lubricating oil pumped through the flow path 35 is discharged appropriately, and the pumping efficiency of the viscous pump 30 can be improved.

[0066] Furthermore, in the embodiment, an inlet connection surface 53 is formed in the pump fixing part 32 at a portion adjacent to the oil reservoir (suction-side oil reservoir) 51 from the outer circumference side, and the inlet connection surface 53 is tangentially continuous with the outer surface 45 of the flow path 35 at the inlet position E1 of the flow path 35. With this configuration, the lubricating oil that flows into the viscous pump 30 through the suction hole 36 rises to a pressure higher than atmospheric pressure at the inlet position E1 of the flow path 35 and its vicinity. As a result, the generation of negative pressure is suppressed at the inlet position E1 and its vicinity in the path through which the lubricating oil is pumped, and the generation of bubbles is appropriately suppressed. In other words, the generation of aeration is appropriately suppressed at the inlet position E1 and its vicinity.

[0067] In the embodiments described above, the outlet connection surface 55 extends from the outlet position E2 of the flow path 35 to the circumferential surface 57 of the discharge hole, but it is not limited to this. Figure 12 is a cross-sectional view showing an example of the configuration of the oil reservoir (discharge-side oil reservoir) 52, the discharge hole 37, and their vicinity in a viscous pump 30 according to the first modified example. In Figure 12, a cross-section perpendicular or approximately perpendicular to the axial direction (rotation axis P) is shown. In this modified example as well, as shown in Figure 12, the outlet connection surface 55 is tangentially continuous with the circumferential surface 45 of the flow path at the outlet position E2 of the flow path 35, and is planar in shape along the tangential direction of the circumferential surface 45 of the flow path at the outlet position E2 of the flow path 35.

[0068] However, in this modified example, the pump fixing portion 32 is provided with an extended curved surface 71, which extends between the outlet connection surface 55 and the discharge hole 37 in the portion adjacent to the oil reservoir 52 from the outer circumference side. The outlet connection surface 55 is connected to the extended curved surface 71 at the end opposite to the side connected to the outer surface 45 of the circumferential flow path, and the outlet connection surface 55 is connected to the circumferential surface 57 of the discharge hole via the extended curved surface 71. In the example shown in Figure 12, the extended curved surface 71 is arc-shaped or substantially arc-shaped in a cross-section perpendicular to the rotation axis P. The center of the arc of the extended curved surface 71 is located on the outer circumference side of the viscous pump 30 relative to the extended curved surface 71.

[0069] In the modified example shown in Figure 12, only one extended curved surface 71 is provided between the outlet connection surface 55 and the discharge hole 37, but this is not the only modification. In one modified example, two or more extended curved surfaces may be formed between the outlet connection surface 55 and the discharge hole 37 in a portion adjacent to the oil reservoir 52 from the outer circumferential side. In this case, the outlet connection surface 55 is connected to the discharge hole circumferential surface 57 via two or more extended curved surfaces. In another modified example, one or more extended curved surfaces may be provided between the inlet connection surface 53 and the suction hole 36 in a portion adjacent to the oil reservoir 51 from the outer circumferential side. In this case, the inlet connection surface 53 is connected to the suction hole circumferential surface 56 via one or more extended curved surfaces.

[0070] Furthermore, in the embodiments described above, the outlet connection surface 55 is formed in a planar shape, but it is not limited to this. Figure 13 is a cross-sectional view showing an example of the configuration of the oil reservoir (discharge-side oil reservoir) 52, the discharge hole 37, and their vicinity in a viscous pump 30 according to the second modified example. In Figure 13, a cross-section perpendicular or substantially perpendicular to the axial direction (rotation axis P) is shown. In this modified example as well, as shown in Figure 13, the outlet connection surface 55 is connected to the outer peripheral surface 45 of the flow path at the outlet position E2 of the flow path 35 and is formed in a portion adjacent to the oil reservoir (discharge-side oil reservoir) 52 from the outer peripheral side.

[0071] However, in this modified example, the outlet connection surface 55 is an arc shape or approximately arc shape that, in a cross section perpendicular to the rotation axis P, is tangent to the tangent α2 of the outer surface 45 of the flow path at the outlet position E2 of the flow path 35. The center of the arc of the outlet connection surface 55 is located on the outer surface side of the viscous pump 30 relative to the outlet connection surface 55. Due to this configuration, in this modified example, the outlet connection surface 55 is formed as a curved surface tangent to the tangent α2, and the tangent α2 is the tangent to the outlet connection surface 55 at the outlet position E2. That is, the outlet connection surface 55 is formed as a curved surface such that the tangential direction of the flow path 35 at the outlet position E2 coincides with that of the outer surface 45 of the flow path.

[0072] In this modified example, the outlet connection surface 55 is tangentially continuous with the outer surface 45 of the flow path at the outlet position E2 of the flow path 35. Because the outlet connection surface 55 is tangentially continuous with the outer surface 45 of the flow path, the cross-sectional area (flow path cross-sectional area) in the oil reservoir 52 gradually decreases toward the outlet position E2 of the flow path 35. In a configuration in which two curved surfaces are connected, if the two curved surfaces are tangentially continuous, the tangential directions of the two curved surfaces coincide at the connection point between them.

[0073] In one modified example, the inlet connection surface 53 is formed in a curved shape. In this case, the inlet connection surface 53 is formed in a curved shape tangent to the tangent line α1, and the tangent line α1 is tangent to the inlet connection surface 53 at the inlet position E1. That is, the inlet connection surface 53 is formed in a curved shape such that the tangential direction of the flow path 35 at the inlet position E1 coincides with the outer surface 45 of the flow path. In this modified example as well, the inlet connection surface 53 is tangentially continuous with the outer surface 45 of the flow path at the inlet position E1 of the flow path 35.

[0074] Figure 14 is a cross-sectional view showing an example of the configuration of the oil reservoir (discharge-side oil reservoir) 52, the discharge hole 37, and their vicinity in a viscous pump 30 according to the third modified example. In Figure 14, the cross-section is perpendicular or approximately perpendicular to the axial direction (rotation axis P). In this modified example, the outlet connection surface 55 is formed in a curved shape and, similar to the modified example in Figure 13, is tangentially continuous with the outer surface 45 of the flow path at the outlet position E2 of the flow path 35. That is, the outlet connection surface 55 is formed in a curved shape such that the tangential direction at the outlet position E2 of the flow path 35 coincides with the outer surface 45 of the flow path.

[0075] However, in this modified example, the pump fixing portion 32 is provided with an extended curved surface 72, which extends between the outlet connection surface 55 and the discharge hole 37 in the portion adjacent to the oil reservoir 52 from the outer circumference side. The outlet connection surface 55 is connected to the extended curved surface 72 at the end opposite to the side connected to the outer surface 45 of the circumferential flow path, and the outlet connection surface 55 is connected to the circumferential surface 57 of the discharge hole via the extended curved surface 72. In the example shown in Figure 14, the extended curved surface 72 is arc-shaped or substantially arc-shaped in a cross section perpendicular to the rotation axis P. The center of the arc of the extended curved surface 72 is located on the inner circumference side of the viscous pump 30 relative to the extended curved surface 71.

[0076] In one modified example, the outlet connection surface 55 is formed in a curved shape, similar to the modified examples in Figure 13 and Figure 14, and two or more extended curved surfaces may be formed between the outlet connection surface 55 and the discharge hole 37 in the portion adjacent to the oil reservoir 52 from the outer circumference. In another modified example, the inlet connection surface 53 is formed in a curved shape, and one or more extended curved surfaces may be provided between the inlet connection surface 53 and the suction hole 36 in the portion adjacent to the oil reservoir 51 from the outer circumference.

[0077] In all of the modifications described above, the outlet connection surface 55 is tangentially continuous with the outer surface 45 of the flow path at the outlet position E2 of the flow path 35. Therefore, all of the modifications produce the same functions and effects as the embodiments described above. In other words, in all of the modifications, the lubricating oil pumped through the flow path 35 is discharged appropriately, and the pumping efficiency of the viscous pump 30 can be improved.

[0078] Furthermore, the embodiments described above described a horizontal-axis type hydroelectric generator in which the shaft 2 (rotating axis P) is aligned with the horizontal plane. However, the configuration of the viscous pump 30 in the embodiments described above is also applicable to a vertical-axis type hydroelectric generator in which the shaft 2 (rotating axis P) is aligned with the vertical direction. Figure 15 is a cross-sectional view showing an example of the internal configuration of the outer box 21 in the bearing device 10 of the hydroelectric generator 1 according to the fourth modified example. In Figure 15, the internal configuration of the outer box 21 in a vertical-axis type hydroelectric generator is shown, and cross-sections along the axial direction and the vertical direction (direction indicated by arrow Z) of the hydroelectric generator 1 and the viscous pump 30 are shown. Note that in Figure 15, only one side of the horizontal direction is shown with respect to the rotating axis P which is aligned with the vertical direction.

[0079] As shown in Figure 15, even in the vertical-shaft type hydroelectric generator 1, an oil tank 27 for storing lubricating oil 26 is formed inside the outer box 21 of the bearing device 10. Bearings are also provided inside the outer box 21. In the vertical-shaft type hydroelectric generator 1, a thrust bearing (not shown) is housed inside the outer box 21 as a bearing, and a guide bearing 75 is housed instead of a journal bearing. In this modified example, the thrust bearing receives the axial load of the shaft 2 caused by the thrust force T, etc. Also in this modified example, the guide bearing 75 receives the radial load of the shaft 2.

[0080] In this modified example, the viscous pump 30 and holder 31 are housed inside the outer box 21. The viscous pump 30 includes a pump fixing part (casing) 32 and a pump rotating part (collar) 33. In the viscous pump 30, the pump rotating part 33 is positioned on the inner circumference side of the pump fixing part 32, and a lubricating oil flow path 35 is formed radially between the pump fixing part 32 and the pump rotating part 33. In this modified example, the path for pumping the lubricating oil 26 in the viscous pump 30, including the flow path 35, has the same configuration as any of the embodiments described above. For example, the cross section along line A3-A3 in Figure 15 has the same configuration as the one shown in Figure 3.

[0081] In this modified example applied to the vertical-shaft hydroelectric generator 1, the outlet connection surface 55 of the viscous pump 30 is tangentially continuous with the outer surface 45 of the flow path at the outlet position E2 of the flow path 35. Therefore, this modified example also provides the same functions and effects as the embodiments described above. That is, in this modified example as well, the lubricating oil pumped through the flow path 35 is discharged appropriately, and the pumping efficiency of the viscous pump 30 can be improved.

[0082] Furthermore, in the embodiments, the sealing structure of the flow path 35 is not limited to the example configuration shown in Figure 5, provided that the outlet connection surface 55 is tangentially continuous with the outer surface 45 of the flow path 35 at the outlet position E2 of the flow path 35. In one example of the embodiments, the sealing structure of the flow path 35 may be the same as the configuration shown in Figure 11, etc., in a configuration where the outlet connection surface 55 is tangentially continuous with the outer surface 45 of the flow path 35 at the outlet position E2 of the flow path 35.

[0083] Furthermore, although the above-described embodiments described the turbine generator 1 as a rotating device, the configuration of the viscous pump 30 and bearing device 10 described above is also applicable to rotating devices other than the turbine generator 1. In other words, the configuration of the viscous pump 30 and bearing device 10 described above can be applied to any rotating device equipped with a shaft similar to the shaft shaft 2, including generators other than turbine generators and electric motors.

[0084] According to at least one embodiment or example, the pump stationary part and the pump rotating part form a discharge-side oil reservoir from the outlet position to the discharge hole, the cross-sectional area of ​​which gradually decreases toward the outlet position of the flow path. The pump stationary part is provided with an outlet connection surface adjacent to the discharge-side oil reservoir from the outer circumference side, which is tangentially continuous with the outer surface of the flow path at the outlet position of the flow path. This makes it possible to provide a viscous pump that can properly discharge the lubricating oil pumped through the flow path and improve pump efficiency, as well as a bearing device and a hydroelectric generator equipped with the viscous pump.

[0085] While several embodiments of the present invention have been described, these embodiments are presented as examples only and are not intended to limit the scope of the invention. These novel embodiments can be carried out in a variety of other forms, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their variations are included in the scope and spirit of the invention, as well as in the claims and their equivalents. [Explanation of Symbols]

[0086] 1...Hydrogen turbine, 2...Shaft, 3...Hydrogen turbine, 5...Generator, 6...Exciter, 7...Brake system, 8...Bearing system (anti-hydro turbine side bearing system), 10...Bearing system (hydro turbine side bearing system), 11...Hydrogen turbine casing, 12...Impeller, 13...Discharge pipe, 15...Generator rotor, 16...Exciter rotor, 17...Brake ring, 18...Electromagnetic brake, 21...Outer box, 22...Oil cooler, 23...Thrust bearing, 25...Journal bearing, 26...Lubricating oil, 27...Oil tank, 30...Viscous pump , 31...Holder, 32...Pump fixing part, 33...Pump rotating part, 35...Flow path, 36...Suction hole, 37...Discharge hole, 41...Suction port, 42...Discharge port, 43...Inner surface of the flow path, 45...Outer surface of the flow path, 46, 47, 48...Sealing members, 51...Oil reservoir (suction side oil reservoir), 52...Oil reservoir (discharge side oil reservoir), 53...Inlet connection surface, 55...Outlet connection surface, 56...Suction hole circumferential surface, 57...Discharge hole circumferential surface, 71, 72...Extended curved surface, E1...Inlet position, E2...Outlet position, P...Rotation axis, L...Oil level, α1, α2...Tangential.

Claims

1. A viscous pump for pumping lubricating oil in a bearing device of rotating machinery, A pump fixing part having a curved outer surface for the flow path and having suction holes and discharge holes formed therein, A pump rotating section is positioned on the inner circumference of the pump fixing section, such that the flow path for the lubricating oil is formed between it and the outer surface of the flow path along the circumferential direction, and rotates together with the axis shaft of the rotating equipment about the axis of rotation, thereby pressurizing the lubricating oil from the suction hole to the discharge hole through the flow path, It is equipped with, The pump fixing portion and the pump rotating portion form a discharge-side oil reservoir from the outlet position to the discharge hole, wherein the cross-sectional area gradually decreases toward the outlet position of the flow path. The pump fixing portion is provided with an outlet connection surface adjacent to the discharge side oil reservoir from the outer circumference, which is tangentially continuous with the outer surface of the flow path at the outlet position of the flow path. Viscous pump.

2. The pump fixing portion and the pump rotating portion are configured to form a suction-side oil reservoir from the inlet position to the suction hole, the cross-sectional area of ​​which gradually decreases toward the inlet position of the flow path. The pump fixing portion is provided with an inlet connection surface adjacent to the suction-side oil reservoir from the outer circumference side, which is tangentially continuous with the outer surface of the flow path at the inlet position of the flow path. A viscous pump according to claim 1.

3. The viscous pump according to claim 1, wherein the outlet connection surface is formed in a planar shape along the tangential direction of the outer surface of the flow path at the outlet position of the flow path.

4. The viscous pump according to claim 1, wherein the outlet connection surface is formed in a curved shape such that the tangential direction of the flow path at the outlet position coincides with the outer surface of the flow path.

5. The viscous pump according to claim 1, wherein the pump fixing portion includes an extended curved surface that extends between the outlet connection surface and the discharge hole in the portion adjacent to the discharge side oil reservoir from the outer circumference side.

6. A viscous pump according to any one of claims 1 to 5, A bearing supports the shaft of the rotating device so as to be rotatable about the aforementioned rotation axis, and receives the load of the shaft. A holder that holds the viscous pump and the bearing from the outer circumference, A bearing device equipped with the following:

7. An outer box in which the viscous pump, the bearing and the holder are housed, and an oil tank for storing the lubricating oil is formed inside the outer box, An oil cooler is provided, which is located outside the outer box and cools the lubricating oil pumped by the viscous pump. The bearing device according to claim 6, further comprising the above.

8. The bearing device according to claim 6 above, The axial shaft, which passes through the viscous pump and the holder in the axial direction along the rotation axis and rotates the pump rotating part of the viscous pump by rotating about the rotation axis, A water turbine is attached to the aforementioned shaft and rotates the shaft by the pressure of water, The aforementioned shaft rotates to generate electricity, and a generator is formed. A water turbine generator equipped with the following features.

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