JP7135164B1 - Bearing structure of water turbine generator - Google Patents

Abstract

A bearing structure for a water turbine generator capable of suppressing the occurrence of aeration and stabilizing the supply of lubricating oil even when the speed and size of the water turbine generator are increased. According to an embodiment, a bearing structure for a water turbine generator includes a bearing that supports a rotating shaft of the water turbine generator, and lubricating oil provided in the bearing for cooling the bearing. A transfer section that transfers from the inside to the outside, and a cooling section that cools the lubricating oil transferred by the transfer section, wherein the transfer section sucks the lubricating oil stored in a storage tank provided in the bearing from a suction port, Lubricating oil sucked from the suction port by rotating the rotating portion into a belt-shaped flow path that is formed between the rotating portion and the fixed portion by facing the rotating portion and the fixed portion and is in communication with the suction port. The shape of the suction port is made rectangular so that the length of the side in the direction of the rotation axis of the rotating part corresponds to the width of the flow path. [Selection drawing] Fig. 3

Description

An embodiment of the present invention relates to a bearing structure for a water turbine generator.

In recent years, from the viewpoint of preventing global warming, renewable energy such as natural energy power generation such as solar power, wind power, and water power generation, and renewable energy such as biomass power generation have been attracting attention in power supply, and efforts are being made to promote their introduction. The installation of hydroelectric power plants, which is one of them, is being actively carried out more than ever before.
Hydraulic power generation uses the flow of water to turn a water wheel, which in turn drives a generator to generate electricity.
Hydro turbine generators are roughly classified into vertical shaft type, in which the generator shaft is installed vertically, and horizontal shaft type, in which the generator shaft is installed horizontally.

FIG. 5 is a side cross-sectional view showing a configuration example of a conventional horizontal shaft type water turbine generator.

The horizontal shaft type water turbine generator 10 illustrated in FIG. A brake ring 28 and the like are attached, and the rotating shaft 12 is supported by two bearings 30 and 50 .

Of the two bearings 30 and 50, the one arranged between the water turbine 14 and the generator 18 is the water turbine side bearing 30, and the one arranged between the generator 18 and the brake ring 28 is the anti-water turbine side bearing. 50.

Each of the bearings 30 and 50 incorporates a journal bearing that receives a load in the diameter direction of the rotating shaft 12 (hereinafter also referred to as “radial load”).

The bearings 30, 50 are also provided with reservoirs for storing lubricating oil for lubricating the bearings. Bearing 30 also includes an oil cooler 34 for cooling the lubricating oil.

The water turbine 14 illustrated in FIG. 5 is the most common water turbine called a Francis turbine. The impeller 16 is installed in a casing that takes in water, and the pressure of the water flowing toward the discharge pipe 80 causes the impeller 16 to move. Rotate to get power.

Structurally, a reaction water turbine represented by a Francis turbine of this type generates a thrust force T, which is a large force, in the axial direction of the generator 18 due to water pressure. In order to limit the axial movement of the rotating shaft 12, a thrust bearing is required to support the axial load (hereinafter also referred to as "thrust load") generated by the thruster T. As shown in FIG.

In order to make the horizontal shaft type water turbine generator 10 as a whole compact, the thrust bearing is generally arranged on the same bearing as the journal bearing, that is, on the water turbine side bearing 30 .

FIG. 6 is a side sectional view showing a configuration example of a conventional water turbine side bearing.

7 is a cross-sectional view taken along line AA in FIG. 6. FIG.

FIG. 8 is a diagram showing details of part B in FIG.

In the turbine-side bearing 30, during operation, the lubricating oil in the storage tank 32 must be pressure-fed by a pump to supply the thrust bearing 31 with the oil.

Since the thrust bearing 31 is at a position higher than the liquid level L of the storage tank 32, the lubricating oil is lifted by the viscous pump 33 in order to fill the thrust bearing 31 with the lubricating oil. Around the viscous pump rotating portion 33a (thrust collar) which is the rotating portion of the viscous pump 33, as shown in FIG. A member called a viscous pump fixing portion 33b (casing) that forms a groove that becomes The lower end of the viscous pump rotating portion 33 a is immersed in the lubricating oil in the storage tank 32 . At the lower end of the viscous pump rotating portion 33a, a viscous pump suction port 33c that takes in lubricating oil from the storage tank 32 and a viscous pump outlet port 33d that discharges the lubricating oil are provided.

As shown in FIG. 7, by rotating the viscous pump rotating portion 33a, the lubricating oil rises through the flow path 33e (pressurizing portion), that is, the viscous pump fixing portion 33b due to the viscosity of the lubricating oil. 33 have been realized.

FIG. 1 is a conceptual diagram showing a pumping route of lubricating oil in a turbine-side bearing.

As the rotating shaft 12 rotates, the lubricating oil in the storage tank 32 in the turbine-side bearing 30 is taken in from the viscous pump suction port 33c as shown in FIG. As a result, the oil is pressure-fed to the viscous pump discharge port 33d and, as shown in FIG.

In the heat exchanger 46, the lubricating oil is cooled by the electric blower 47 and then returned to the turbine side bearing 30. As shown in FIG. Through the oil supply passage, the thrust bearing 31 and the journal bearing 36 are pumped and supplied with oil.

The lubricating oil then lubricates the thrust bearing 31 and is heated by frictional heat before being discharged into the storage tank 32 through an oil drain port 37 provided at a position higher than the topmost portions of the thrust bearing 31 and the journal bearing 36. .

Also, the lubricating oil that lubricates the journal bearing 36 and is heated by frictional heat passes through the oil disk oil supply hole 38 and is discharged from the oil disk oil supply port 39 during steady operation.

Further, the oil disk supply port 39 supplies the lubricating oil scooped up by the oil disk 40 to the journal bearing 36 until the oil is supplied to the journal bearing 36 by pressure feeding by the viscous pump 33 at the beginning of the operation. It's mouth

The holder 41 holds the thrust bearing 31, the journal bearing 36, and the viscous pump rotating portion 33a, and forms a lubricating oil path. The holder 41 is supported by being sandwiched from above and below by supports (not shown) fixed inside the storage tank 32 and the cover 42 . The contact surface between the support and the holder 41 is spherically processed so that it can follow the displacement of the shaft during operation.

The journal bearing 36 of the turbine-side bearing 30 is provided with an oil disk 40 for initial lubrication until lubricating oil is supplied by the viscous pump 33 . Oil is raised up to journal bearing 36 .

In such a water turbine side bearing 30, the viscous pump 33 is an important component involved in supplying lubricating oil to the sliding surface of the thrust bearing 31 with the viscous pump rotating portion 33a and cooling the lubricating oil.

FIG. 9 is a developed view of the lubricating oil flow path in the viscous pump 33 . FIG. 9(B) is a diagram showing a flow path 33e from the viscous pump suction port 33c to the viscous pump discharge port 33d, and FIG. 9(A) is a cross-sectional view along the CC cross section shown in FIG. 9(B). is.

As shown in FIG. 9B, the lubricating oil flowing from the viscous pump suction port 33c flows from the pressurizing portion inlet 33f into the gap between the viscous pump fixing portion 33b (casing) and the viscous pump rotating portion 33a (thrust collar). It flows into the formed channel 33e. The lubricating oil filled in the flow path 33e is pressure-fed by a shearing force due to viscosity when the viscous pump rotating part 33a rotates in the flow direction of the lubricating oil. The lubricating oil pressure-fed through the flow path 33e flows out of the flow path 33e through the pressurizing portion outlet 33g and is sent to the viscous pump discharge port 33d.

FIG. 10 is a diagram showing a shape from a viscous pump suction port 33c to a flow path 33e in a conventional viscous pump. FIG. 10(B) is a cross-sectional view of the periphery from the viscous pump suction port 33c to the flow path 33e on the AA cross section shown in FIG. 6, and FIG. FIG. 10B is a cross-sectional view of the periphery shown in FIG. 10B corresponding to the C cross section;

As shown in FIGS. 9(A) and 10(A), the viscous pump suction port 33c has a cylindrical shape and communicates near the end of a flow path 33e formed by a band-shaped groove.

As shown in FIG. 10, the viscous pump rotating portion 33a (thrust collar) above the viscous pump suction port 33c rotates to the right in the drawing, thereby dragging the lubricating oil sucked from the viscous pump suction port 33c. and push it into the pressure inlet 33f. At this time, the viscous pump suction port 33c becomes negative pressure.

JP-A-01-88000

In the case of the conventional horizontal-axis hydraulic turbine generator using the bearing structure described above, there were the following two problems due to the increase in speed and size of the hydraulic turbine generator.

(Problem 1) When air bubbles are generated in the lubricating oil supplied to the bearing, the bearing may burn out.

(Problem 2) The amount of pressure-fed oil to the heat exchanger (oil cooler) is reduced, and the heat dissipation capability is lowered.

(Cause of Problem) Since 6 to 12% (volume ratio) of air is dissolved in lubricating oil at atmospheric pressure, air bubbles are generated even if the pressure does not decrease to the saturated vapor pressure that causes cavitation.

This phenomenon is called aeration. The pressure inside the viscous pump decreases from the viscous pump suction port 33c to the pressurizing section inlet 33f, resulting in a negative pressure state lower than the atmospheric pressure. In addition, when lubricating oil taken in from the viscous pump suction port 33c enters the flow path 33e (pressurizing portion) through the pressurizing portion inlet 33f, the flow is rapidly throttled. Here, the pressure drops further due to the resulting pressure loss.

Due to the resistance due to this pressure loss, the flow of lubricating oil flowing near the viscous pump rotating part 33a (thrust collar) is dragged by the rotation of the viscous pump rotating part 33a, and the amount of lubricating oil taken in from the viscous pump suction port 33c. Since the flow rate cannot catch up, the supply of lubricating oil to the flow path 33e accompanying the rotation of the viscous pump rotating portion 33a is hindered.
This creates areas of locally low pressure. As a result, aeration occurs.

The present invention has been made in view of such circumstances, and even when the speed and size of the water turbine generator are increased, it is possible to suppress the occurrence of aeration and stabilize the supply of lubricating oil. To provide a bearing structure for a water turbine generator capable of

In order to solve the above problems, a bearing structure for a water turbine generator according to the invention corresponding to claim 1 comprises: a bearing for supporting a rotating shaft of the water turbine generator; a transfer section that transfers lubricating oil supplied to the bearing from inside the bearing to the outside; and a cooling section that cools the lubricating oil transferred by the transfer section, wherein the transfer section is provided in the bearing Lubricating oil stored in a storage tank is sucked from a suction port, and a band-shaped flow communicating with the suction port is formed between the rotating portion and the fixed portion by facing the rotating portion and the fixed portion. The lubricating oil sucked from the suction port is pumped into the passage by rotating the rotating portion, and the shape of the suction port is such that the length of the side of the rotating portion in the direction of the rotation axis is the length of the passage. to a rectangle corresponding to the width of .

To provide a bearing structure for a water turbine generator capable of suppressing the occurrence of aeration and stabilizing the supply of lubricating oil even when the speed and size of the water turbine generator are increased. can be done.

FIG. 1 is a lubricating oil path diagram for explaining a configuration example of a bearing structure of a water turbine generator according to an embodiment of the present invention. FIG. 2 is an exploded view of the lubricating oil flow path in the viscosity pump of the embodiment of the present invention. FIG. 3 is a diagram showing the shape of the viscous pump 33 according to the embodiment of the present invention from the viscous pump suction port to the channel. FIG. 4 is a diagram showing an example in which the connecting portion between the suction port of the viscous pump and the oil reservoir is not curved. FIG. 5 is a side cross-sectional view showing a configuration example of a conventional horizontal shaft type water turbine generator. FIG. 6 is a side sectional view showing a configuration example of a conventional water turbine side bearing. 7 is a cross-sectional view taken along line AA in FIG. 6. FIG. FIG. 8 is a diagram showing details of part B in FIG. FIG. 9 is a developed view of a lubricating oil flow path in a viscous pump. FIG. 10 is a diagram showing the shape of a conventional viscous pump from a viscous pump suction port to a flow path.

A bearing structure for a water turbine generator according to an embodiment of the present invention will be described below with reference to the drawings.

Note that the bearing structure of the water turbine generator according to the embodiment of the present invention is basically the same as the structure already explained with reference to FIGS. 5 to 8. FIG. Accordingly, in the following description of the embodiments, the same reference numerals are used to denote the same parts as those already described, and redundant description is avoided. The bearing structure of the embodiment of the present invention differs from the structure shown in FIGS. 9 and 10 in the structure of the viscous pump 33 (transfer section).

FIG. 1 is a lubricating oil path diagram for explaining a configuration example of a bearing structure of a water turbine generator according to an embodiment of the present invention.

That is, the bearing structure of the horizontal shaft type water turbine generator of the embodiment of the present invention includes a first bearing (hereinafter referred to as a "turbine side bearing") 30 that supports the rotating shaft 12 of the horizontal shaft type water turbine generator, and a second bearing. 2 bearings (hereinafter referred to as “anti-turbine side bearings”) 50 .

The turbine-side bearing 30 includes a reservoir 32 for storing lubricating oil provided for cooling the thrust bearing 31 and the journal bearing 36 in the turbine-side bearing 30, and a reservoir 32 for storing the lubricating oil stored in the reservoir 32. A viscous pump 33, which is a transfer section for pressure-feeding from the inside of the bearing 30 to the outside, is provided inside.

An oil cooler 34 , which is a cooling portion for cooling the lubricating oil transferred by the viscous pump 33 , is provided outside the turbine-side bearing 30 . The oil cooler 34 has a heat exchanger 46 and an electric blower 47 . Lubricating oil is transferred to the heat exchanger 46 by the viscous pump 33 . The lubricating oil transferred to the heat exchanger 46 is cooled by cooling air from the electric blower 47 .

The lubricating oil cooled in the heat exchanger 46 in this manner is transferred into the turbine side bearing 30 via the return pipes H ₀ and H ₁ from the heat exchanger 46 by the driving force of the viscous pump 33 . Alternatively, part of it may be transferred into the anti-waterwheel side bearing 50 .

FIG. 2 is a developed view of the lubricating oil flow path in the viscous pump 33 of the embodiment of the present invention. FIG. 2(B) is a diagram showing the flow path 33e1 from the viscous pump suction port 33c1 to the viscous pump discharge port 33d1, and FIG. 2(A) is a cross-sectional view along the DD cross section shown in FIG. is.

FIG. 3 is a diagram showing the shape from the viscous pump suction port 33c1 to the flow path 33e1 in the viscous pump 33 of the embodiment of the present invention. FIG. 3B is a cross-sectional view of the periphery from the viscous pump suction port 33c1 to the flow path 33e1, and FIG. ) is a cross-sectional view of the periphery shown in FIG.

In the side cross-sectional view of FIG. 6 showing the configuration example of the conventional water turbine side bearing, the shape of the openings of the viscous pump suction port 33c and the viscous pump discharge port 33d is circular. In the pump 33, the openings of the viscous pump suction port 33c1 and the viscous pump discharge port 33d1 are rectangular (not shown).

As shown in FIGS. 2A and 3A, the viscous pump suction port 33c1 has a rectangular cross-sectional shape, and the gap between the viscous pump rotating portion 33a (thrust collar) and the viscous pump fixing portion 33b (casing) is is communicated with the strip-shaped flow path 33e1 composed of. That is, the shape of the viscous pump suction port 33c1 is made rectangular so that the length of the sides in the direction of the rotational axis of the viscous pump rotating portion 33a corresponds to the width of the band-shaped flow path 33e1.

As a result, when the viscosity of the lubricating oil drags the lubricating oil from the viscous pump suction port 33c1 toward the flow channel 33e1 due to the rotation of the viscous pump rotating part 33a, it communicates with the flow channel 33e1 of the viscous pump suction port 33c1. It is supplied as a uniform flow across the entire width. That is, since the lubricating oil is supplied from the viscous pump suction port 33c1 to the flow path 33e1 as a uniform flow without a locally high velocity region, the pressure drop is reduced and the aeration is suppressed.

As shown in FIGS. 2A, 2B, 3A, and 3B, the flow path 33e1 is provided with an oil reservoir 33j on the viscous pump suction port 33c1 side, and an oil reservoir 33j on the viscous pump discharge port 33d1 side. Between the oil reservoirs 33j and 33k, there is provided a pressurizing portion 33h corresponding to the flow path 33e in the conventional structure for pumping the lubricating portion. The pressurizing portion 33h has a constant flow passage cross-sectional area between the oil reservoir 33j and the oil reservoir 33k.

The oil reservoir 33j is provided at the inflow portion into which the lubricating oil flows from the viscous pump suction port 33c1 of the flow channel 33e1 by chamfering the viscous pump fixing portion 33b at the connection portion between the viscous pump suction port 33c1 and the flow channel 33e1. be done. The oil reservoir 33j is formed by chamfering the connecting portion between the flow path 33e1 of the viscous pump fixing portion 33b and the viscous pump suction port 33c1, so that the cross-sectional area of the flow path 33e1 at the pressurizing portion 33h becomes wider than that of the flow path 33e1. It is formed.

Similarly, the oil reservoir 33k is formed by chamfering the viscous pump fixing portion 33b at the connecting portion between the viscous pump outlet 33d1 and the flow path 33e1, thereby lubricating the viscous pump outlet 33d1 from the pressurizing portion 33h of the flow path 33e1. It is provided at the outflow part from which the oil flows out. The oil reservoir 33k is formed by chamfering the connecting portion between the flow path 33e1 of the viscous pump fixing portion 33b and the viscous pump discharge port 33d1, so that the cross-sectional area of the flow path 33e1 at the pressurizing portion 33h is wider than that of the flow path 33e1. It is formed.

As a result, there are no factors that cause pressure loss such as contraction loss and expansion loss in the path of lubricating oil from the viscous pump suction port 33c1 to reach the viscous pump rotating portion 33a, and the negative pressure is reduced. In addition, by suppressing the pressure loss, the flow rate of lubricating oil drawn from the viscous pump suction port 33c into the flow rate of the lubricating oil flowing near the viscous pump rotating part 33a that is dragged by the rotation of the viscous pump rotating part 33a. catches up, and a flow that pushes the lubricating oil into the flow path 33e (pressurizing portion) can be created with the rotation of the viscous pump rotating portion 33a. As a result, aeration can be suppressed and the supply of lubricating oil can be stabilized. In addition, it is possible to increase the discharge amount of the lubricating oil pressure-fed in the pressurizing portion 33h from the viscous pump discharge port 33d1.

Furthermore, as shown in FIGS. 2(B) and 3(B), the oil reservoir 33j gradually narrows the flow passage cross-sectional area from the oil reservoir inlet 33m to the pressurizing portion inlet 33f1. That is, a wedge-shaped gap is formed between the oil reservoir inlet 33m and the pressurizing portion inlet 33f1. Further, as shown in FIGS. 2B and 3B, the oil reservoir 33k gradually widens the channel cross-sectional area from the oil reservoir outlet 33n to the viscous pump discharge port 33d1.

As a result, the lubricating oil from the viscous pump suction port 33c1 is drawn from the oil reservoir inlet 33m toward the pressurizing portion inlet 33f1 due to the wedge film effect of the oil reservoir 33j, and reaches the pressurizing portion inlet 33f1. pressurized. Therefore, the negative pressure, which is the cause of bubble generation, is reduced. As a result, aeration can be suppressed and the supply of lubricating oil can be stabilized. In addition, in the oil reservoir 33k, the cross-sectional area of the flow passage from the oil reservoir outlet 33n to the viscous pump outlet 33d1 is gradually widened, so that the discharge amount of the lubricating oil pressure-fed in the pressurizing portion 33h at the viscous pump outlet 33d1 is increased. can be increased.

Furthermore, the provision of the oil reservoir 33k results in an enlarged flow path at the discharge portion, so that dynamic pressure is converted into static pressure. As a result, the discharge pressure is increased, and the discharge oil amount can be increased.

Further, as shown in FIGS. 3B and 7, the pressurizing portion 33h of the flow path 33e1 is formed between the viscous pump rotating portion 33a and the viscous pump fixing portion 33b and has an arc shape. The surface of the oil reservoir 33j on the side of the viscous pump fixing portion 33b faces the viscous pump fixing portion 33b side of the pressure portion 33h at the pressure portion inlet 33f1 of the pressure portion 33h (the flow path 33e1 having a constant flow passage cross-sectional area). on the tangent of the arc-shaped face of . That is, the surface of the viscous pump fixing portion 33b from the oil reservoir 33j to the pressurizing portion 33h is formed smoothly.

Similarly, the surface of the oil reservoir 33k on the side of the viscous pump fixing portion 33b is tangential to the arc-shaped surface of the pressure portion 33h on the side of the viscous pump fixing portion 33b at the pressure portion outlet 33g1 of the pressure portion 33h. Connecting. That is, the surface of the viscous pump fixing portion 33b from the pressurizing portion 33h to the oil reservoir 33k is formed smoothly.

As a result, the lubricating oil can smoothly flow from the viscous pump suction port 33c1 to the pressurizing portion 33h through the oil reservoir 33j. Also, the lubricating oil can be smoothly flowed from the pressurizing portion 33h to the viscous pump discharge port 33d1 through the oil reservoir 33j.

Furthermore, as shown in FIG. 3B, the surface of the viscous pump fixing portion 33b of the oil reservoir inlet 33m, that is, the connection portion 33p of the oil reservoir 33j with the viscous pump suction port 33c1 is formed into a curved surface. Similarly, the surface of the viscous pump fixing portion 33b of the oil reservoir outlet 33n, that is, the connecting portion between the viscous pump discharge port 33d1 and the oil reservoir 33j is formed into a curved surface.

As a result, the lubricating oil sucked from the viscous pump suction port 33c1 can be more smoothly flowed into the oil reservoir 33j. In addition, the lubricating oil pressure-fed from the pressurizing portion 33h to the oil reservoir 33k can be more smoothly discharged to the viscous pump discharge port 33d1.

In addition, in FIG. 3B, the connecting portion between the viscous pump suction port 33c1 and the oil reservoir 33j is formed into a curved surface, but it is not necessarily a curved surface. FIG. 4 is a diagram showing an example in which the connecting portion between the viscous pump suction port 33c1 and the oil reservoir 33j is not curved. FIG. 4B is a cross-sectional view of the periphery from the viscous pump suction port 33c1 to the flow path 33e1, and FIG. ) is a cross-sectional view of the periphery shown in FIG.

In the example shown in FIG. 4B, the oil reservoir 33j1 is formed by chamfering the viscous pump fixing portion 33b at the connecting portion between the viscous pump suction port 33c1 and the flow path 33e1. The chamfering of the viscous pump fixing portion 33b flattens the surface of the viscous pump fixing portion 33b in the range from the viscous pump suction port 33c1 (oil reservoir inlet 33m) to the pressurizing portion 33h (oil reservoir outlet 33n). Further, in the same manner as the oil reservoir 33j shown in FIG. 3B, the oil reservoir 33j1 is connected on a tangent line to the arc-shaped surface of the pressure member 33h on the side of the viscous pump fixing portion 33b at the pressure member inlet 33f1. Thus, the surface of the viscous pump fixing portion 33b from the oil reservoir 33j to the pressurizing portion 33h is formed smoothly.

As a result, the lubricating oil can smoothly flow into the pressurizing portion 33h from the viscous pump suction port 33c1 through the oil reservoir 33j1.

An oil reservoir similar to the oil reservoir 33j1 can also be formed on the viscous pump discharge port 33d1 side.

In this way, in the bearing structure of the hydraulic turbine generator of the present embodiment, even if the hydraulic turbine generator is increased in speed and size, the occurrence of aeration in the flow path of the lubricating oil of the viscous pump 33 is suppressed. to stabilize the lubricating oil supply.

It should be noted that although several embodiments of the invention have been described, these embodiments are provided by way of example and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and modifications can be made without departing from the scope of the invention. These embodiments and their modifications are included in the scope and spirit of the invention, as well as the scope of the invention described in the claims and equivalents thereof.

REFERENCE SIGNS LIST 10 Horizontal shaft type water turbine generator 12 Rotating shaft 14 Water turbine 16 Impeller 18 Generator 20 Rotor 22 Exciter 24 Rotor 26 Electromagnetic brake 28 Brake ring 30 Water turbine side bearing 31 Thrust bearing 32 Storage tank 33 Viscosity pump 33a Viscosity pump rotating part (thrust collar)
33b Viscosity pump fixing part 33c, 33c1 Viscosity pump suction port 33d, 33d1 Viscosity pump discharge port 33e, 33e1 Flow path 33f, 33f1 Pressure part inlet 33h Pressure part 33j, 33j1, 33k Oil reservoir 33m Oil reservoir inlet 33n Oil reservoir outlet 34 Oil cooler 35 Bearing oil supply port 36 Journal bearing 37 Oil drain port 38 Oil disk oil supply hole 39 Oil disk oil supply port 40 Oil disk 41 Holder 42 Cover 46 Heat exchanger 47 Electric blower 50 Anti-turbine side bearing 80 Discharge pipe

Claims (6)

A bearing structure for a water turbine generator,
a bearing that supports the rotating shaft of the water turbine generator;
a transfer unit provided in the bearing for transferring lubricating oil provided for cooling the bearing from the inside of the bearing to the outside;
A cooling unit that cools the lubricating oil transferred by the transfer unit,
The transfer portion is formed between the rotating portion and the fixed portion by sucking the lubricating oil stored in the storage tank provided in the bearing from the suction port, and making the rotating portion and the fixed portion face each other. , the lubricating oil sucked from the suction port is pressure-fed by rotating the rotating part to a belt-shaped flow path that communicates with the suction port,
A bearing structure for a water turbine generator, wherein the shape of the suction port is a rectangle whose side length in the rotation axis direction of the rotating portion corresponds to the width of the flow path. The fixed portion of the connecting portion between the suction port and the flow path is chamfered, and an oil reservoir having a flow path cross-sectional area larger than that of the flow path is formed in an inflow portion of the flow path into which the lubricating oil flows. A bearing structure for a water turbine generator according to claim 1, which is formed. 3. The bearing structure for a water turbine generator according to claim 2, wherein the flow passage cross-sectional area of said oil reservoir is gradually narrowed from the connecting portion with said suction port. 4. The bearing structure for a water turbine generator according to claim 2, wherein said oil reservoir is connected on a tangential line of an inlet portion of said flow passage where the cross-sectional area of said flow passage is constant. 5. The bearing structure for a water turbine generator according to claim 2, wherein a surface of said fixed portion of an inlet portion of said lubricating oil from said suction port to said oil sump is curved. The transfer unit transfers the lubricating oil pressure-fed through the flow path from a discharge port to the cooling unit,
2. The bearing structure for a water turbine generator according to claim 1, wherein said discharge port has a rectangular shape whose side length in the rotation axis direction of said rotating portion corresponds to the width of said flow path.

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