WO2015098896A1

WO2015098896A1 - Bearing device and pump

Info

Publication number: WO2015098896A1
Application number: PCT/JP2014/084007
Authority: WO
Inventors: 成吉川; 栄作兼村; 平田　和也; 山中　隆司
Original assignee: 株式会社荏原製作所
Priority date: 2013-12-26
Filing date: 2014-12-23
Publication date: 2015-07-02
Also published as: JPWO2015098896A1

Abstract

The present invention pertains to a bearing device which is more compact than the prior art and does not require complicated machining, and with which lubricating oil can be supplied in an appropriate amount and in a stable manner to a bearing, even when the peripheral speed of a rotary shaft is increased to a high speed. In addition, the present invention pertains to a pump equipped with such a bearing device. The bearing device is equipped with: a bearing (32) that receives the load of a rotary shaft (1); a lubricating oil reservoir (10) arranged below the bearing (32); an oil disk (11) that is affixed to and rotates integrally with the rotary shaft (1), thereby scooping up the lubricating oil stored in the lubricating oil reservoir (10); a lubricating oil passage (17) extending to the bearing (32); and a guide casing (15) that guides the lubricating oil scooped up by the oil disk (11) to the lubricating oil passage (17). The guide casing (15) has an inner surface that faces the side surface and the outer peripheral surface of the oil disk (11).

Description

Bearing device and pump

The present invention relates to a bearing device used for a horizontal shaft pump or the like, and more particularly, to a bearing device capable of appropriately supplying lubricating oil to a bearing even when the diameter of a rotating shaft is increased or the rotational speed is increased. . The present invention also relates to a pump provided with such a bearing device.

In a horizontal axis type rotary machine (for example, a horizontal axis pump) in which a rotary shaft is installed horizontally, a bearing device is disposed in the vicinity of the end of the rotary shaft in order to rotatably support the rotary shaft. Further, a lubricating oil storage tank in which lubricating oil for lubricating and cooling the bearing is stored is provided inside or outside the bearing device. Examples of means for supplying lubricating oil from the lubricating oil storage tank to the bearing include a forced oil supply device using external power or a self-lubricating device that does not use external power. The forced oil supply device supplies lubricating oil to a bearing arranged inside the bearing device using external power from a lubricating oil storage tank arranged outside the bearing device. In the self-lubricating device, the lubricating oil is pumped up from the lubricating oil storage tank disposed below the rotating shaft inside the bearing device by using the rotational force of the rotating shaft and supplied to the bearing.

An example of the forced oiling device is shown in FIGS. FIG. 11 is a cross-sectional view showing a bearing device when a forced oil supply device is used. FIG. 12 is a piping and instrument system diagram of the forced oiling device. FIG. 13A and FIG. 13B are a schematic side view and a schematic plan view showing the arrangement of the pump when the forced oil supply device is used.

As shown in FIG. 11, the rotary shaft 1 of the horizontal shaft pump 100 extends horizontally, and the end of the rotary shaft 1 is rotatably supported by

bearings

9A and 9B. As shown in FIG. 12, a forced oil supply device 26 is disposed outside the horizontal shaft pump 100. Lubricating oil is forcibly supplied from the forced oil supply device 26 to the

bearings

9A and 9B. The forced oil supply device 26 includes a plurality of components such as a lubricating oil pump 21, a filter 24, a lubricating oil cooler 23, a plurality of hydraulic pressure monitoring instruments 25, and a lubricating oil tank 22. Therefore, the cost of the forced oil supply device 26 is increased.

Furthermore, as shown in FIG. 13A and FIG. 13B, in addition to the installation space of the horizontal axis pump 100 and the electric motor 200 for driving the horizontal axis pump 100, the installation space of the forced oil supply device 26 is required. In this case, since the volume of each component which comprises the forced oil supply apparatus 26 is large, the installation space for the forced oil supply apparatus 26 also becomes large. As a result, the installation space required for the entire pump system becomes large, which may cause a reduction in product competitiveness in the market as a rotating machine.

Next, FIG. 14 shows an example of a conventional bearing device using a self-lubricating device. As FIG. 14 shows, the edge part of the rotating shaft 1 is rotatably supported by bearing 9A, 9B. The lubricating oil storage tank 10 in which the lubricating oil is stored is disposed below the

bearings

9A and 9B. An oil ring 20 is provided as a self-lubricating device for scooping up the lubricating oil in the lubricating oil storage tank 10. The oil ring 20 is disposed so as to surround the outer peripheral surface of the rotating shaft 1 and rotates with the rotation of the rotating shaft 1. Then, the lubricating oil is supplied to the bearings 9 A and 9 B by scooping up the lubricating oil in the lubricating oil storage tank 10 by the rotating oil ring 20. Such a self-lubricating device using the oil ring 20 is conventionally known as an oil ring self-lubricating device.

However, in such a conventional oil ring self-lubricating device, the circumferential speed (hereinafter simply referred to as the circumferential speed) of the outer peripheral surface of the rotating shaft 1 due to the increase in the diameter of the rotating shaft 1 or the speeding up of the rotating shaft 1 or the like. ) Rises, the rotation of the oil ring 20 cannot follow the rotation of the rotary shaft 1. That is, the rotational speed of the oil ring 20 with respect to the rotating shaft 1 is greatly reduced, and the oil ring 20 cannot properly scoop up the lubricating oil. As a result, desired lubrication performance and cooling performance cannot be obtained.

For this reason, an upper limit of the peripheral speed of the rotary shaft 1 inevitably exists in a horizontal shaft pump employing an oil ring type self-lubricating device. For this reason, when the pump is required to have a peripheral speed exceeding the upper limit, a forced oiling device has been employed. However, as described above, the horizontal shaft pump in which the forced oil supply device is employed is a large-sized facility, which may reduce the competitiveness in the market.

Furthermore, when the amount of lubricating oil supplied to the bearing is excessive, friction loss in the bearing portion increases, which contributes to an increase in the temperature of the bearing portion. In the conventional self-lubricating method, it is extremely difficult to control the supply amount of the lubricating oil from the oil ring 20 to the bearing. For this reason, when an excessive amount of lubricating oil is supplied to the bearing, the lubricating oil that is originally expected to have a cooling action causes heat generation due to increased friction, resulting in an opposite effect to the expected action.

In the self-lubricating bearing device disclosed in Patent Document 1, it is not necessary to install a separate forced oil supply device. However, piping for circulating the lubricating oil needs to be arranged outside or inside the bearing device, and an oil ring is required as auxiliary oil supply means at the time of startup.

In the bearing device disclosed in Patent Document 2, a resin oil case facing the disk fixed to the rotating shaft is provided. Since this oil case is made of resin, there is a problem that when the oil case is worn out and the gap with the disk is widened, the ability to suck up the lubricating oil is lowered and the amount of oil supplied to the bearing is insufficient. Further, in this bearing device, the lubricating oil adhering to the disk is collected on the outer edge of the disk by centrifugal force caused by the rotation of the disk, and is collected by the oil case on the outer peripheral arc surface of the disk. However, the lubricating oil overflows and scatters from the outer circumferential arc surface, or the lubricating oil scatters from a portion other than the outer circumferential arc surface. In addition, the lubricating oil is lifted above the outer periphery of the disk through the flexible tube using the pressure of the lubricating oil gathered at the outer edge of the disk by centrifugal force, and further provided outside the flexible tube. Supplied to the journal bearing through the introduced hole. For this reason, the entire bearing device is large in the radial direction, and the processing of the introduction hole is complicated and takes time.

Patent Document 3 discloses a technique for guiding oil pumped up by an oil ring to a bearing. However, the amount of lubricating oil supplied to the bearing when this technology is used varies depending on operating conditions. Further, the above-described problem that the oil ring does not follow the rotation shaft as the rotation shaft rotates at high speed is not taken into consideration. Further, it is predicted that the amount of lubricating oil flying from the oil surface due to the rotation of the oil ring increases as the peripheral speed of the rotating shaft increases. In the invention disclosed in Patent Document 3, no consideration is given to the loss of lubricating oil in the axial direction of the rotating shaft, and there is a concern about oil leakage from the shaft seal portion or the like of the bearing device.

Further, in any of the conventional self-lubricating bearing devices disclosed in any of the above-mentioned patent documents, the influence of excessive lubrication oil supply to the bearing on both the rolling bearing and the sliding bearing, that is, the rotation loss No mention is made of measures against the increase and the associated fever. Therefore, the above-described conventional self-lubricating bearing device provides an appropriate self-lubricating technique considering the rotational speed, the diameter of the rotating shaft, the viscosity of the lubricating oil to be used, and the oil viscosity change due to the ambient temperature and operating time. It's hard to say. Further, in other related literatures and prior arts, there is no technique related to suppressing an excessive amount of lubricating oil supplied and optimizing the amount of lubricating oil supplied.

Japanese Patent No. 3637269 Japanese Patent Laid-Open No. 2002-188637 JP 58-63050 A

The present invention has been made in view of the above-described conventional problems, and even when the peripheral speed of the rotating shaft is increased, the lubricating oil can be stably supplied to the bearing in an appropriate amount. And it aims at providing the bearing apparatus which is compact compared with the past, and does not require a complicated process. Moreover, an object of this invention is to provide the pump provided with such a bearing apparatus.

One aspect of the present invention for solving the above-described problems is a bearing that receives a load of a rotating shaft, a lubricating oil storage tank that is disposed below the bearing, and is fixed to the rotating shaft so as to be integrated with the rotating shaft. An oil disk that pumps up the lubricating oil stored in the lubricating oil storage tank by rotating, a lubricating oil passage that extends to the bearing, and a guide casing that guides the lubricating oil pumped up by the oil disk to the lubricating oil passage And the guide casing has an inner surface facing a side surface and an outer peripheral surface of the oil disk.

In a preferred aspect of the present invention, a lubricating oil introduction groove connected to the lubricating oil passage is formed on an inner surface of the guide casing, and the lubricating oil introduction groove is adjacent to a side surface of the oil disk. It is characterized by that.
In a preferred aspect of the present invention, the lubricating oil passage extends from the inner surface of the guide casing in the axial direction of the rotating shaft, and further extends in a direction perpendicular to the axial direction to reach the bearing. .
In a preferred aspect of the present invention, an annular groove is provided on the outer peripheral surface of the oil disk.
In a preferred aspect of the present invention, a plurality of depressions are provided on the outer peripheral surface of the oil disk.
In a preferred aspect of the present invention, a plurality of radial grooves are provided on a side surface of the oil disk.

In a preferred aspect of the present invention, a key is provided on the outer peripheral surface of the rotating shaft, and a key groove is formed on an inner peripheral surface of a through hole formed at the center of the oil disk. The oil disk is fixed to the rotating shaft in a state in which the groove is engaged.
In a preferred aspect of the present invention, the bearing is one of at least two bearings arranged in series on the rotating shaft, and an annular spacer is arranged between the at least two bearings. It is characterized by that.
In a preferred aspect of the present invention, the spacer has an oil supply hole extending from an outer peripheral surface to an inner peripheral surface, and the oil supply hole is connected to the lubricating oil passage.

In a preferred aspect of the present invention, the bearing is a thrust bearing that receives an axial load of the rotating shaft.
In a preferred aspect of the present invention, the thrust bearing is configured to receive both an axial load and a radial load of the rotating shaft.

Another aspect of the present invention is a pump including a rotating shaft, an impeller fixed to the rotating shaft, and the bearing device that rotatably supports the rotating shaft.

Since the oil disk always rotates at the same rotational speed as the rotational shaft, even if the rotational speed of the rotational shaft increases, slippage does not occur and the follow-up performance does not decrease as in the conventional oil ring. . Therefore, according to the present invention, it is possible to stably supply the lubricating oil to the bearing even under the high peripheral speed condition of the rotating shaft, which is difficult to supply with conventional technology such as an oil ring. As a result, the forced oiling device is not required, the installation area of the pump is reduced, and the cost is reduced, so that the product competitiveness in the market can be increased.
Furthermore, since the oil disk is surrounded by a guide casing disposed opposite to and in close proximity to the oil disk, it is possible to prevent wasteful splashing of the lubricating oil scooped up by the oil disk. As a result, an amount of lubricating oil more than necessary and sufficient can be led to the lubricating oil passage leading to the bearing. Since the lubricating oil passage extends in the axial direction at a position close to the rotating shaft, a compact bearing device can be provided as compared with the conventional one without requiring complicated processing.
The amount of lubricating oil supplied to the bearing is determined by the circumferential position of the lubricating oil passage port and the shape of the passage (cross-sectional area, length, passage direction with respect to the oil disk rotation direction, flow resistance factors such as surface roughness, Alternatively, the amount is limited to a suitable amount by an excessive lubricating oil discharge hole provided in the course of the passage. Therefore, an increase in rotation loss due to the excessive supply of lubricating oil and the accompanying heat generation are prevented.

FIG. 1 is a cross-sectional view showing an example of a horizontal shaft single-stage pump provided with a bearing device according to an embodiment of the present invention. FIG. 2 is a cross-sectional view showing an example of a horizontal shaft multi-stage pump provided with a bearing device according to an embodiment of the present invention. FIG. 3 is a cross-sectional view showing the structure of a self-lubricating bearing device according to an embodiment of the present invention. FIG. 4A is a longitudinal sectional view of the oil disk. FIG. 4B is a partial plan view of the oil disk shown in FIG. 4A as viewed from the axial direction. FIG. 4C is a perspective view of the oil disc shown in FIG. 4A. FIG. 5A is a longitudinal sectional view of another example oil disk. FIG. 5B is a partial plan view of the oil disk shown in FIG. 5A as viewed from the axial direction. FIG. 5C is a perspective view of the oil disk shown in FIG. 5A. FIG. 6A is a longitudinal sectional view of still another example of an oil disk. FIG. 6B is a partial plan view of the oil disk shown in FIG. 6A as viewed from the axial direction. 6C is a perspective view of the oil disk shown in FIG. 6A. FIG. 7 is an enlarged sectional view showing the oil disk and the guide casing. FIG. 8 is a view showing an inner side surface of a guide casing provided with a plurality of lubricating oil introduction grooves. FIG. 9 is a view showing the inner surface of the guide disk that is not provided with the lubricating oil introduction groove and that faces the side surface of the oil disk. FIG. 10A is a cross-sectional view showing a part of the bearing device along the longitudinal direction of the rotating shaft. FIG. 10B is a diagram showing a cross section of the bearing device as viewed from the longitudinal direction of the rotating shaft. FIG. 11 is a cross-sectional view showing a bearing device when a forced oil supply device is used. FIG. 12 is a piping and instrument system diagram of the forced oiling device. FIG. 13A is a schematic side view showing the arrangement of pumps when a forced oiling device is used. FIG. 13B is a schematic plan view showing the arrangement of the pumps when the forced oiling device is used. FIG. 14 is a cross-sectional view showing an example of a conventional bearing device using a self-lubricating device.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a cross-sectional view showing an example of a horizontal shaft single-stage pump provided with a bearing device according to an embodiment of the present invention. A horizontal axis single-stage pump 100 as a rotating machine shown in FIG. 1 has an impeller 2 and a rotating shaft 1 to which the impeller 2 is fixed. The rotating shaft 1 extends horizontally. One end of the rotary shaft 1 is connected to a drive machine such as an electric motor (not shown), and the rotary shaft 1 and the impeller 2 are rotated by this drive machine. Moreover, the rotating shaft 1 is rotatably supported by bearing

devices

9 and 9 provided in the vicinity of both ends thereof.

The impeller 2 is disposed in the pump casing 5. The pump casing 5 shown in FIG. 1 has a spiral chamber 5a therein, and the impeller 2 is disposed in the spiral chamber 5a. When the impeller 2 rotates with the rotation of the rotating shaft 1, a liquid such as water is sucked from the suction port 3, the pressure of the liquid is increased by the action of the impeller 2 and the spiral chamber 5 a, and the liquid is discharged from the discharge port 4. It is.

The impeller 2 in the illustrated example has a double suction structure for sucking liquid from both sides. The

caps

2A and 2B are attached to the liquid inlet of the impeller 2, respectively. By designing the diameters of the

caps

2A and 2B to be different from each other, a thrust force due to a pressure difference can be applied in one direction of the rotating shaft 1 and the rotating shaft 1 can be rotated in a stable state. This thrust force is supported by a thrust bearing unit 9A of the bearing device 9. Since a thrust force acts on the thrust bearing unit 9A as a load, it is necessary to supply an appropriate amount of lubricating oil to the thrust bearing unit 9A and cool the thrust bearing unit 9A while lubricating it.

In addition to the thrust bearing unit 9A, two

radial bearing units

9B and 9B are disposed in the vicinity of both end portions of the rotary shaft 1. The rotary shaft 1 is supported by a total of three bearings including these two

radial bearing units

9B and 9B and one thrust bearing unit 9A. In the present embodiment, sleeve-type bearings are used for the

radial bearing units

9B and 9B, and a conventional self-lubricating oil supply device having an oil ring 20 is provided in the sleeve-type

radial bearing units

9B and 9B. It has been adopted. The configuration of the present invention described later is applied to the thrust bearing unit 9A.

FIG. 2 is a cross-sectional view showing an example of a horizontal multistage pump provided with a bearing device according to an embodiment of the present invention. A horizontal axis multistage pump 100 as a rotating machine shown in FIG. 2 includes a plurality of impellers 2 and a rotary shaft 1 to which the impellers 2 are fixed. The rotating shaft 1 extends horizontally. The plurality of impellers 2 are arranged in series on the rotary shaft 1, and a plurality of guide vanes 6 are arranged so as to surround each of the impellers 2. One end of the rotary shaft 1 is connected to a drive machine such as an electric motor (not shown), and the rotary shaft 1 and the impeller 2 are rotated by this drive machine. Moreover, the rotating shaft 1 is rotatably supported by bearing

devices

9 and 9 provided in the vicinity of both ends thereof.

The impeller 2 is disposed in the pump casing 5. When the plurality of impellers 2 rotate with the rotation of the rotating shaft 1, liquid such as water is sucked from the suction port 3, and the pressure of the liquid is increased by the action of the impeller 2 and the guide vane 6, and the liquid is discharged from the discharge port. 4 is spit out. Since the plurality of impellers 2 are arranged in the same direction, the thrust force generated by the pressure difference between the adjacent impellers 2 is overlapped by the number of impellers 2, and a large thrust force is generated. This thrust force is offset by the balance device 7 provided in the horizontal multistage pump 100, but a certain amount of thrust force remains during transient operation. This residual thrust force is supported by the thrust bearing unit 9A of the bearing device 9. Since the residual thrust force acts on the thrust bearing unit 9A as a load, it is necessary to supply an appropriate amount of lubricating oil to the thrust bearing unit 9A and cool the thrust bearing unit 9A while lubricating it.

In addition to the thrust bearing unit 9A, two

radial bearing units

9B and 9B. It has been adopted. The configuration of the present invention described later is applied to the thrust bearing unit 9A. The configuration of the

bearing devices

9 and 9 disposed in the vicinity of both ends of the rotary shaft 1 is the same as that of the horizontal axis single-stage pump shown in FIG.

1 and 2, the rotary shaft 1 extends through the pump casing 5 in both cases of the horizontal shaft pump 100 shown in FIGS. A gap between the rotary shaft 1 and the pump casing 5 is sealed by

shaft sealing devices

8 and 8 such as mechanical seals. Therefore, the liquid pressurized by the impeller 2 does not enter the

bearing devices

9 and 9.

FIG. 3 is a cross-sectional view showing the structure of a self-lubricating bearing device according to an embodiment of the present invention. As shown in FIG. 3, the bearing device 9 includes a thrust bearing unit 9 A that receives the axial load and the radial load of the rotating shaft 1 that extends horizontally, and a radial bearing unit 9 B that receives the radial load of the rotating shaft 1. Have. A plurality of angular ball bearings are used for the thrust bearing unit 9A.

A lubricating oil storage tank 10 is disposed below the thrust bearing unit 9A and the radial bearing unit 9B, and the oil level of the lubricating oil stored in the lubricating oil storage tank 10 is indicated by a dotted line with a reference numeral 10A. ing. The amount of lubricating oil is controlled so that the oil level 10A in the lubricating oil storage tank 10 is constant. A cooling jacket 27 is provided below the lubricating oil storage tank 10, and the lubricating oil in the lubricating oil storage tank 10 is cooled by the coolant flowing through the cooling jacket 27. Instead of the cooling jacket 27, an air cooling structure with fins may be employed. Or it is good also as a structure which inserts a cooling liquid tube with a fin in the lubricating oil storage tank 10, and cools lubricating oil directly.

The bearing device 9 further includes a lubricating oil pumping means 11 that is fixed to the rotating shaft 1 and rotates together with the rotating shaft 1 to pump up the lubricating oil stored in the lubricating oil storage tank 10. The lubricating oil lifting means 11 is configured as a circular oil disk. The oil disk 11 is fixed to the rotary shaft 1 so as to rotate integrally with the rotary shaft 1. Specifically, a key 1 a is provided on the outer peripheral surface of the rotating shaft 1, and a key groove 11 a is formed on the inner peripheral surface of a through hole formed at the center of the oil disk 11. The rotary shaft 1 is inserted into the through hole of the oil disk 11 so that the key 1a is inserted into the key groove 11a. Due to the engagement between the key 1a and the key groove 11a, the torque of the rotary shaft 1 is transmitted to the oil disc 11, and the oil disc 11 rotates integrally with the rotary shaft 1. Therefore, the oil disk 11 always rotates at the same rotational speed as the rotary shaft 1.

The lower part of the oil disk 11 is immersed in the lubricating oil in the lubricating oil storage tank 10, and the rotating oil disk 11 scoops up the lubricating oil stored in the lubricating oil storage tank 10. In order to increase the amount of lubricating oil that the oil disk 11 scoops up, various undulating shapes may be provided on the peripheral edge of the oil disk 11.

4A to 4C are diagrams showing an example in which an annular groove 12 is provided on the outer peripheral surface of the oil disk 11. FIG. As shown in FIGS. 4A to 4C, an annular groove 12 extending in the circumferential direction is provided on the outer peripheral surface of the oil disk 11. A part of the outer peripheral surface of the oil disk 11 is always immersed in the lubricating oil in the lubricating oil storage tank 10. When the oil disk 11 rotates, the lubricating oil is held in the annular groove 12 formed on the outer peripheral surface thereof, so that it is possible to increase the amount of lubricating oil that the oil disk 11 scoops up.

FIGS. 5A to 5C are views showing an example in which a plurality of depressions 13 are provided on the outer peripheral surface of the oil disk 11. As shown in FIGS. 5A to 5C, a plurality of depressions 13 are provided on the outer peripheral surface of the oil disk 11. These recesses 13 are arranged at equal intervals along the circumferential direction of the oil disk 11. When the oil disk 11 rotates, the lubricating oil is held in the plurality of recesses 13 formed on the outer peripheral surface thereof, so that the amount of lubricating oil that the oil disk 11 scoops up can be increased. The recess 13 of the present embodiment is conical, but may have other shapes such as a cylindrical shape.

FIGS. 6A to 6C are views showing an example in which a plurality of radial grooves 14 are provided on both side surfaces of the oil disk 11. As shown in FIGS. 6A to 6C, a plurality of radial grooves 14 extending in the radial direction of the oil disk 11 are provided on both side surfaces of the oil disk 11. The plurality of radial grooves 14 are arranged at equal intervals around the center of the oil disk 11. These radial grooves 14 extend to the outer peripheral surface of the oil disk 11, and the outer end of each radial groove 14 is on the outer peripheral surface of the oil disk 11. When the oil disk 11 rotates, the lubricating oil is held in the radial grooves 14 formed on both side surfaces thereof, so that the amount of lubricating oil that the oil disk 11 scoops up can be increased. In addition, although the radial groove 14 of the illustrated embodiment extends in the radial direction of the oil disk 11, the radial groove 14 may be inclined from the radial direction. The radial groove in this case also extends to the outer peripheral surface of the oil disk 11. The radial groove may be inclined toward the rotation direction of the oil disk 11 or may be inclined toward a direction opposite to the rotation direction. The amount of lubricating oil that the oil disk 11 scoops up can be adjusted by the inclination direction and the inclination angle of the radial groove.

As shown in FIG. 3, the bearing device 9 prevents the lubricating oil pumped up by the oil disk 11 from scattering around and prevents the lubricating oil from dropping from both sides of the oil disk 11. The guide casing 15 is provided. FIG. 7 is an enlarged cross-sectional view showing the oil disk 11 and the guide casing 15. As shown in FIG. 7, the guide casing 15 is disposed in the vicinity of the oil disk 11. The guide casing 15 is composed of two

annular guide disks

15A and 15B arranged to face both side surfaces (two side surfaces aligned in the axial direction) of the oil disk 11. In the example illustrated in FIG. 7, the guide casing 15 includes two guide disks 15 A and 15 B that are arranged so as to sandwich both side surfaces of the oil disk 11. Further, the guide casing 15 is disposed in the vicinity of the outer peripheral surface of the oil disk 11. The outer peripheral surface of the oil disk 11 is the outermost peripheral surface located between both side surfaces of the oil disk 11.

The inner surface of the guide casing 15 is disposed close to both side surfaces and the outer peripheral surface of the oil disk 11 and faces both side surfaces and the outer peripheral surface of the oil disk 11. More specifically, in the example shown in FIG. 7, annular guide disks 15 A and 15 B are arranged so as to face both side surfaces of the oil disk 11, and the outer peripheral surface of the oil disk 11 is also surrounded by the guide casing 15. ing. Between the oil disk 11 and the guide casing 15, an axial gap W1 and a radial gap W2 are formed. The axial gap W 1 is a gap between the side surface of the oil disk 11 and the guide casing 15, and the radial gap W 2 is a gap between the outer peripheral surface of the oil disk 11 and the guide casing 15.

These gaps W1 and W2 are set to appropriate values so that the lubricating oil pumped up on the oil disk 11 does not scatter or fall based on the pump operating conditions such as the viscosity of the lubricating oil used and the rotational speed of the rotary shaft 1. Is set. For example, the axial gap W1 is 2 mm to 4 mm, and the radial gap W2 is 3 mm to 6 mm. Further, by setting these gaps W1 and W2 to appropriate values, the guide casing 15 surrounding the oil disk 11 is disposed close to the oil disk 11 at a suitable distance. Therefore, even if the lubricating oil pumped up on the oil disk 11 is scattered from the oil disk 11, the lubricating oil accompanies the rotation direction due to the rotation of the oil disk 11, and the oil disk 11 and the guide casing 15 The gaps W1 and W2 are held. Accordingly, the amount of lubricating oil held in the gaps W1 and W2 is appropriately adjusted according to the dimensions of the gaps W1 and W2 between the oil disk 11 and the guide casing 15. As a result, the lubricating oil pumped up by the oil disk 11 is directly guided to the lubricating oil passage 17 (described later) and the communication passage 28 extending in the axial direction and directly communicating with the bearing 32 constituting the thrust bearing unit 9A. By suitably designing the dimensions of the passage 17 and the communication passage 28, the supply amount of the lubricating oil can be adjusted. Therefore, the amount of lubricating oil supplied to the thrust bearing unit 9A is appropriately maintained. Furthermore, since the splashing range of the lubricating oil scooped up from the oil disk 11 by the guide casing 15 is limited, leakage of the lubricating oil from the shaft seal device 8 can be prevented.

Also, by appropriately setting the axial gap W1 and the radial gap W2, it is possible to suppress heat generation due to friction and stirring of the lubricating oil. For example, under the operating conditions of the multistage pump shown in FIG. 2, the axial gap W1 is 4 mm, and the radial gap W2 is 5 mm. Thus, the axial gap W1 and the radial gap W2 are appropriately set according to the pump type and / or pump operating conditions (for example, the viscosity of the lubricating oil and the rotational speed of the rotary shaft 1).

A plurality of lubricating oil introduction grooves 16 are provided on the inner surface (inner side surface) of the guide casing 15 that faces the side surface of the oil disk 11. More specifically, as shown in FIG. 7, a plurality of lubricating oil introduction grooves 16 are provided on the inner surface of the guide disk 15A disposed closer to the thrust bearing unit 9A than the guide disk 15B. These lubricating oil introduction grooves 16 are disposed close to the side surface of the oil disk 11 and extend from the vicinity of the rotating shaft 1 in the radially outward direction of the oil disk 11. The outer end of the lubricating oil introduction groove 16 is connected to an inlet 17a of a lubricating oil passage 17 that sends the lubricating oil to the thrust bearing unit 9A.

FIG. 8 is a view showing an inner side surface of the guide casing 15 provided with a plurality of lubricating oil introduction grooves 16. In the illustrated example, three lubricating oil introduction grooves 16 are provided, and these lubricating oil introduction grooves 16 are located in the upper half of the guide casing 15. The lubricating oil introduction groove 16 is connected to a lubricating oil passage 17 for supplying the lubricating oil pumped up by the oil disk 11 to the thrust bearing unit 9A. The guide casing 15 surrounds the oil disk 11 with the limited gaps W1 and W2 so that the lubricating oil pumped up by the oil disk 11 is not scattered unnecessarily. The lubricating oil accompanying the rotation direction in the gaps W1 and W2 between the oil disks 11 flows along the lubricating oil introduction groove 16, and is guided to the inlet 17a of the lubricating oil passage 17. The lubricant introduction groove 16 is provided to guide the lubricant from the gaps W1 and W2 between the guide casing 15 and the oil disk 11 to the lubricant passage 17. Therefore, the lubricating oil passage 17 is formed in the bearing casing 35 that accommodates the thrust bearing unit 9A and the radial bearing unit 9B. The cooling jacket 27 described above is also formed in the bearing casing 35.

The direction in which the lubricating oil introduction groove 16 extends from the inlet 17 a of the lubricating oil passage 17 is inclined toward the upstream side in the rotational direction of the oil disk 11 with respect to the radial direction of the oil disk 11. As described above, the lubricating oil introduction groove 16 is inclined toward the upstream side in the rotation direction of the oil disk 11, so that the lubricating oil scooped up by the rotating oil disk 11 easily enters the lubricating oil introduction groove 16. The angle of the lubricating oil introduction groove 16 with respect to the radial direction of the oil disk 11 is, for example, in the range of 30 degrees to 60 degrees. The inclination angle of the lubricating oil introduction groove 16 is appropriately set in consideration of operating conditions such as the rotational speed of the rotating shaft 1, physical properties such as the viscosity of the lubricating oil, and the amount of lubricating oil supplied to the thrust bearing unit 9A. The The lubricating oil introduction groove 16 may be an arcuate groove having an appropriate curvature radius according to specifications such as operating conditions and physical properties of the lubricating oil. For example, the lubricant introduction groove 16 may be a spiral groove.

FIG. 9 is a view showing the inner surface of the guide disk 15B facing the oil disk 11. As shown in FIG. As shown in FIG. 9, the lubricating oil introduction groove 16 is not provided on the inner surface of the guide disk 15B.

As shown in FIG. 3, the lubricating oil that has entered the lubricating oil introduction groove 16 is guided to the lubricating oil passage 17 that communicates with the lubricating oil introduction groove 16. The lubricating oil passage 17 extends to the thrust bearing unit 9A. More specifically, the lubricating oil passage 17 extends from the inner surface of the guide casing 15 in the axial direction of the rotary shaft 1 and further extends in a direction perpendicular to the axial direction of the rotary shaft 1 to reach the thrust bearing unit 9A. Yes. The lubricating oil is supplied to the thrust bearing unit 9A through the lubricating oil passage 17. Circumferential position of the lubricating oil passage 17 and the form of the lubricating oil passage 17 (for example, cross-sectional area, length, passage direction relative to the oil disk rotation direction, flow resistance factors such as surface roughness, or excess provided in the passage By appropriately designing the lubricating oil discharge hole and the like, the amount of lubricating oil supplied to the thrust bearing unit 9A can be limited to a suitable amount. The lubricating oil passage 17 may be disposed at a position near the rotating shaft 1 that is equal to or smaller than the outer diameter of the oil disk 11.

As shown in FIG. 3, the thrust bearing unit 9 A according to this embodiment includes two

bearings

31 and 32 arranged in series on the rotary shaft 1, and an annular shape arranged between the

bearings

31 and 32. And a spacer (spacer) 19. As the

bearings

31 and 32, angular ball bearings that can receive both the axial load and the radial load of the rotary shaft 1 are used. This angular ball bearing functions as a radial bearing and a thrust bearing. The spacer 19 also functions as a lubricant guide for supplying lubricant to the

bearings

31 and 32 evenly. Three or more bearings may be provided. Also in this case, the spacer 19 is disposed between two adjacent bearings.

FIG. 10A is a sectional view showing a part of the bearing device along the longitudinal direction of the rotating shaft 1, and FIG. 10B is a diagram showing a section of the bearing device seen from the longitudinal direction of the rotating shaft 1. A plurality of oil supply holes 18 for efficiently distributing the lubricant supplied from the lubricant passage 17 to the

bearings

31 and 32 are provided on the outer periphery of the spacer 19. Each oil supply hole 18 extends from the outer peripheral surface of the spacer 19 to the inner peripheral surface. The diameter and number of the oil supply holes 18 are appropriately set in consideration of operating conditions such as the rotational speed of the rotating shaft 1, physical properties such as the viscosity of the lubricating oil, and the amount of lubricating oil supplied to the thrust bearing unit 9A. The

According to the configuration described above, since the lubricating oil pumped up by the rotation of the oil disk 11 is properly supplied to the thrust bearing unit 9A, a highly reliable self-lubricating bearing device can be configured even at a high peripheral speed. It becomes possible. Specifically, in the past, a peripheral speed of about 14 m / s was the limit of a self-lubricating bearing device. However, according to the present invention, the peripheral speed limit applicable to self-lubrication is 16 to 18 m / s, or It becomes possible to increase to the above peripheral speed.

According to the present invention, it is possible to stably supply the lubricating oil to the thrust bearing unit 9A even under high peripheral speed conditions of the rotary shaft 1, which has been difficult to supply by conventional techniques such as an oil ring. As a result, the forced oiling device is not required, the installation area of the pump is reduced, and the cost is reduced, so that the product competitiveness in the market can be increased. Further, since the oil disk 11 is surrounded by the guide casing 15 disposed opposite to and close to the oil disk 11, it is possible to prevent useless scattering of the lubricating oil pumped up by the oil disk 11. . As a result, an amount of lubricating oil more than necessary and sufficient can be guided to the lubricating oil passage 17 that leads to the

bearings

31 and 32. Since the lubricating oil passage 17 extends in the axial direction from the inner surface of the oil disk 15, it is possible to provide a bearing device that is more compact than the conventional one without requiring complicated processing.

Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Is possible. For example, by extending the lubricating oil introduction groove 16 from the lubricating oil passage 17 toward the downstream side in the rotation direction of the oil disk 11, it becomes possible to easily suppress the lubricating oil supply amount, and unnecessary heat generation due to excessive lubricating oil supply. Can be prevented. In the above-described embodiment, the oil disk 11 and the guide casing 15 are provided for supplying the lubricating oil to the thrust bearing unit 9A. However, the oil disk and the guide for supplying the lubricating oil to the radial bearing unit 9B are provided. A casing may be provided.

Furthermore, the diameter and surface shape of the oil disk 11, the oil surface height of the lubricating oil storage tank 10, the guide casing 15 and the oil disk 11, depending on various conditions such as pump operating conditions and physical properties such as the viscosity of the lubricating oil. The axial gap W1 and radial gap W2 between them, the circumferential position and inclination of the lubricant introduction groove 16, the cross-sectional area of the lubricant passage 17, the shape of the spacer 19 disposed between the bearings, and the like are appropriately designed and By selecting, the present invention can be applied to various types of pumps.

The present invention relates to a bearing device used for a horizontal shaft pump or the like, and more particularly, to a bearing device capable of appropriately supplying lubricating oil to a bearing even when the diameter of a rotating shaft is increased or the rotational speed is increased. Is available. Further, the present invention can be used for a pump provided with such a bearing device.

DESCRIPTION OF SYMBOLS 1 Rotating shaft 1a Key 2 Impeller 3 Suction port 4 Discharge port 5 Pump casing 6 Guide vane 7 Balance device 8 Shaft seal device (mechanical seal)
DESCRIPTION OF SYMBOLS 9 Bearing apparatus 9A Thrust bearing unit 9B Radial bearing unit 10 Lubricating oil storage tank 10A Lubricating oil surface 11 Oil disk 11a Key groove 12 Annular groove 13 Indentation 14 Radial groove 15 Guide casing 16 Lubricating oil introduction groove 17 Lubricating oil passage 17a Inlet 18 Oil supply hole 19 spacer 20 oil ring 21 oil pump 22 oil tank 23 oil cooler 24 filter 25 monitoring instrument 26 forced oil supply device 27 cooling jacket 28

communication passage

31, 32 bearing 35 bearing casing 100 horizontal shaft pump (rotary machine)
200 electric motor

Claims

A bearing that receives the load of the rotating shaft;
A lubricating oil reservoir disposed below the bearing;
An oil disk that is fixed to the rotating shaft and rotates integrally with the rotating shaft, thereby scooping up the lubricating oil stored in the lubricating oil storage tank;
A lubricating oil passage extending to the bearing;
A guide casing that guides the lubricating oil pumped up by the oil disk to the lubricating oil passage,
The guide casing has an inner surface facing a side surface and an outer peripheral surface of the oil disk.
The lubricating oil introduction groove connected to the lubricating oil passage is formed on the inner surface of the guide casing, and the lubricating oil introduction groove is adjacent to a side surface of the oil disk. The bearing device according to 1.
2. The bearing according to claim 1, wherein the lubricating oil passage extends in an axial direction of the rotating shaft from an inner surface of the guide casing and further extends in a direction perpendicular to the axial direction to reach the bearing. apparatus.
The bearing device according to claim 1, wherein an annular groove is provided on an outer peripheral surface of the oil disk.
The bearing device according to claim 1, wherein a plurality of depressions are provided on an outer peripheral surface of the oil disk.
The bearing device according to claim 1, wherein a plurality of radial grooves are provided on a side surface of the oil disk.
A key is provided on the outer peripheral surface of the rotating shaft, and a key groove is formed on an inner peripheral surface of a through hole formed in the center of the oil disk, and the key and the key groove are engaged with each other. The bearing device according to claim 1, wherein the oil disk is fixed to the rotating shaft.
The bearing is one of at least two bearings arranged in series on the rotating shaft, and an annular spacer is arranged between the at least two bearings. Item 8. The bearing device according to any one of Items 1 to 7.
The bearing device according to claim 8, wherein the spacer has an oil supply hole extending from an outer peripheral surface to an inner peripheral surface, and the oil supply hole is connected to the lubricating oil passage.
The bearing device according to any one of claims 1 to 9, wherein the bearing is a thrust bearing that receives an axial load of the rotating shaft.
The bearing device according to claim 10, wherein the thrust bearing is configured to receive both an axial load and a radial load of the rotary shaft.
A rotation axis;
An impeller fixed to the rotating shaft;
A pump comprising: the bearing device according to claim 1, which rotatably supports the rotating shaft.