WO2018159680A1

WO2018159680A1 - Pump device and maintenance method for pump device

Info

Publication number: WO2018159680A1
Application number: PCT/JP2018/007510
Authority: WO
Inventors: 誠安田; 学沼田; 岡本　茂
Original assignee: 株式会社荏原製作所
Priority date: 2017-02-28
Filing date: 2018-02-28
Publication date: 2018-09-07
Also published as: CN110325744B; CN110325744A

Abstract

This pump device has: a main shaft for rotating an impeller that pressurizes a conveyed liquid through driving of a drive machine in a predetermined direction; a bearing that rotatably supports the main shaft; a bearing cover that is penetrated by the main shaft; and a seal member that prevents a lubricant of the bearing from leaking from a sealed fluid side through the outer peripheral surface of the main shaft to the atmosphere side, wherein the bearing cover is configured such that the lubricant spattered from the bearing flows through the bearing cover to the seal member, and the main shaft is provided with, on the outer peripheral surface, a groove that is inclined so as to force back the lubricant on the outer peripheral surface of the main shaft from the atmosphere side to the sealed fluid side when the main shaft rotates.

Description

Pump device and maintenance method of pump device

The present invention relates to a pump device and a maintenance method for the pump device.

The pump device supports a rotating main shaft with a bearing, and a lubricant is used for the bearing. If the pump device continues to be used, the bearing lubricant may leak out of the pump device due to deterioration over time, which may contaminate the surroundings and increase the number of maintenance such as replenishment or replacement of the lubricant.

Japanese Patent Publication No. 61-46679 Japanese Utility Model Publication No. 1-115069 JP-A-8-254213 Japanese Patent No. 5980217 Japanese Patent No. 5950997 Japanese Utility Model Publication No.59-116631 Japanese Patent No. 6073746

The present invention has been made in view of such problems, and an object of the present invention is to provide a pump maintenance method for suppressing the leakage of the lubricant to the outside of the pump device, and to reduce the leakage of the lubricant to the outside of the pump device. It is an object to provide a manufacturing method of a lubricant leakage suppressing pump and a pump device capable of suppressing the leakage of the lubricant to the outside of the pump device.

According to one aspect of the present invention, an oil seal that is disposed at a position where a lubricant from a bearing that rotatably supports a main shaft that rotates in a predetermined direction can be scattered and slides on an outer peripheral surface of the main shaft is disposed on the main shaft. When the main shaft rotates in the predetermined direction on at least a part of the outer surface of the main shaft opposite to the bearing from the sliding surface with the oil seal. Further, there is provided a maintenance method for a pump device comprising: a step of forming a groove inclined in a direction in which the lubricant on the sliding surface is pushed back to the bearing side; and a step of attaching an oil seal to the main shaft.
By forming such a groove, the lubricant is pushed back to the bearing side by the pumping action, so that leakage of the lubricant can be suppressed. Further, since the lubricant from the bearing is scattered on the oil seal, the sliding between the oil seal and the main shaft can be kept good.

In the step of forming the groove, the groove may be formed in at least a part of the sliding surface.
As a result, the effect of pushing back the lubricant is increased, and the pressure of the groove on the sliding surface between the oil seal and the main shaft is reduced, and bubbles are generated in the lubricant, thereby reducing the sliding surface between the oil seal and the main shaft. Low friction can be achieved.

In the step of forming the groove, the groove may be formed in at least a part of the bearing side from the sliding surface.
This increases the effect of pushing back the lubricant.

The step of separating, the step of forming the groove, and the step of attaching the oil seal may be performed on the pump device in which a predetermined amount or more of the lubricant leaks from the sliding surface to the opposite side of the bearing.
Such maintenance prevents the lubricant from leaking to the opposite side of the bearing.

Removing the lubricant from the bearing body covering the main shaft; removing the body cover disposed inside the bearing body and the pump body from the pump body housing the impeller attached to the main shaft; The method may include a step of removing the impeller from the main shaft, a step of removing the body cover from the bearing body, and a step of removing a shaft seal device provided on the main shaft, followed by the step of separating. .
In this way, maintenance of the main shaft in the pump including the impeller, the pump body, and the body cover can be performed.

According to another aspect of the present invention, when the main shaft rotates in a predetermined direction on at least a part of the outer peripheral surface of the main shaft opposite to the bearing with the oil seal, the sliding surface There is provided a method of manufacturing a lubricant leakage suppression pump comprising: a step of forming a groove inclined in a direction in which the lubricant is pushed back to the bearing side; and a step of attaching an oil seal to the main shaft.
By forming such a groove on the main shaft, the lubricating oil is pushed back to the bearing side by the pumping action, so that leakage of the lubricating oil can be suppressed.

According to another aspect of the present invention, a pump, a main shaft for rotating the impeller of the pump in a predetermined direction to send a carrier liquid by the operation of the pump, and the main shaft are rotatably supported. In the pump apparatus comprising: a bearing; and an oil seal that slides on the outer peripheral surface of the main shaft and prevents the lubricant from leaking from the sealed fluid side to the atmosphere side along the outer peripheral surface of the main shaft. An oil seal is disposed at a position where the lubricant from the bearing scatters, and an outer peripheral surface of the main shaft on the outer side of the main shaft from the oil seal when the pump is operated. A pump device is provided, characterized in that a groove inclined in a direction in which the lubricant exposed to the surface is pushed back to the sealed fluid side is provided.
Since such a groove is provided in the main shaft, the lubricant is pushed back to the bearing side by the pumping action, so that leakage of the lubricant can be suppressed. Further, since the lubricant from the bearing is scattered on the oil seal, the sliding between the oil seal and the main shaft can be kept good.

When the pump is operated, the inclined groove forms a first flow in which the lubricant is pushed back to the bearing side, and a second flow in which the lubricant from the bearing reaches the sliding surface. It is desirable that a predetermined amount of the lubricant be interposed on the sliding surface between the oil seal and the outer peripheral surface of the main shaft.
The leakage of the lubricant is suppressed by the first flow, and the sliding between the oil seal and the main shaft can be favorably maintained by the second flow.

The inclined groove is preferably provided in at least a part of the outer peripheral surface of the main shaft on the atmosphere side.
With such a groove, the lubricant can be pushed back to the bearing side by a pumping action.

It is preferable that the inclined groove is provided on a sliding surface with the oil seal on the outer peripheral surface of the main shaft.
As a result, the effect of pushing back the lubricant is increased, and the pressure of the groove on the sliding surface between the oil seal and the main shaft is reduced, and bubbles are generated in the lubricant, thereby reducing the sliding surface between the oil seal and the main shaft. Low friction can be achieved.

The inclined groove is preferably provided in at least a part of the outer peripheral surface of the main shaft on the sealed fluid side.
This increases the effect of pushing back the lubricant.

According to another aspect of the present invention, a main shaft for rotating an impeller that pressurizes the carrier liquid by driving a driving device in a predetermined direction, a bearing that rotatably supports the main shaft, and the main shaft include: And a seal member that prevents the lubricant of the bearing from passing through the outer peripheral surface of the main shaft and leaking from the sealed fluid side to the atmosphere side, and the bearing cover is scattered from the bearing. The lubricant is configured to flow through the bearing cover and to the seal member, and the lubricant on the outer peripheral surface of the main shaft rotates from the atmosphere side when the main shaft rotates on the outer peripheral surface of the main shaft. A pump device is provided in which an inclined groove is provided so as to be returned to the sealed fluid side.
As a result, the lubricant supplied from the bearing through the bearing cover to the seal member via the bearing cover is formed with fine grooves on the spindle, which increases the contact area between the spindle and the lubricant. Since the lubricant exposed to the outer peripheral surface of the main shaft on the atmosphere side is returned from the seal member to the bearing side by the pumping action, the lubricant can be prevented from leaking from the seal member to the atmosphere side.

The pump device is preferably a horizontal shaft type pump device.
Thereby, while the main shaft is stationary, the pump device can seal the sealed fluid by the action of the seal member. Thus, the groove on the outer peripheral surface of the main shaft in the horizontal shaft type pump device has an increased tolerance for surface roughness and machining accuracy.

It is desirable that the inclined groove is provided in at least a part of a region adjacent to the atmosphere side with respect to a region facing the seal member on the outer peripheral surface of the main shaft.
As a result, as the main shaft rotates, on the air side of the outer peripheral surface of the main shaft on which the inclined groove is formed, air is generated from the air side of the outer peripheral surface of the main shaft toward the bearing, and lubrication is performed by this wind. The agent is pushed back in the direction of the bearing.

The inclined groove preferably extends from the atmosphere side to the sealed fluid side in the outer peripheral surface of the main shaft.
As a result, the lubricant is returned to the bearing side as the main shaft rotates.

When the main shaft is stationary, the oil level of the lubricant is preferably at a liquid level below the main shaft.
Thereby, when the main shaft is stationary, the lubricant does not leak to the atmosphere side along the inclined groove of the main shaft.

The seal member is an oil seal incorporated into the bearing cover, and the bearing cover has a sliding portion between the oil seal and the outer peripheral surface of the main shaft by the lubricant scattered from the bearing passing through the bearing cover. It is desirable to be configured to be supplied between.
As a result, the lubricant splashed from the bearing passes through the bearing cover, and the lubricant is supplied between the sliding portion between the oil seal and the outer peripheral surface of the main shaft, so that the sliding between the oil seal and the main shaft can be kept good. it can. Further, since the inclined groove is formed, the lubricant exposed from the seal member to the outer peripheral surface of the main spindle on the atmosphere side is pushed back to the bearing side by the pumping action, so that the lubricant leaks from the seal member to the atmosphere side. Can be suppressed.

It is desirable that the inclined groove is provided in at least a part of the atmosphere side contacting between the oil seal and the sliding portion of the outer peripheral surface of the main shaft.
As a result, wind is generated from the atmosphere side of the outer peripheral surface of the main shaft toward the bearing, and the lubricant is pushed back toward the bearing by the wind.

It is desirable that the inclined groove is provided in a sliding portion between the oil seal and the outer peripheral surface of the main shaft.
As a result, the effect of pushing back the lubricant is increased, and the pressure of the groove on the sliding surface between the oil seal and the main shaft is reduced, and bubbles are generated in the lubricant, thereby reducing the sliding surface between the oil seal and the main shaft. Low friction can be achieved.

The inclined groove is preferably provided in at least a part of the outer peripheral surface of the main shaft on the sealed fluid side.
This increases the effect of returning the lubricant on the outer peripheral surface of the main shaft to the bearing side.

The bearing cover preferably has a structure for guiding the lubricant scattered on the bearing cover to the seal member on a surface on the bearing side.
Thereby, the lubricant scattered from the bearing can be guided to the seal member.

As a structure for guiding the lubricant to the seal member, the surface including at least the ceiling surface portion of the inner peripheral surface of the bearing cover is moved toward the main shaft as it approaches the seal member along the major axis direction of the main shaft. It is desirable to be inclined so as to approach.
Thereby, the lubricant scattered from the bearing can be guided to the seal member.

The bearing cover preferably includes a bearing cover main body and a guide member for guiding the lubricant scattered from the bearing to the seal member as a structure for guiding the lubricant to the seal member.
Thereby, the lubricant scattered from the bearing can be guided to the seal member.

The guide member is provided on the inner peripheral surface including the uppermost part of the inner peripheral surface of the bearing cover body, and has a protrusion shape extending to the seal member along the major axis direction of the main shaft,
It is desirable that the surface of the guide member that faces the main shaft be inclined so as to approach the main shaft as it approaches the seal member along the major axis direction of the main shaft.
Thereby, the lubricant flows along the inclination of the surface facing the main shaft of the guide member, so that the lubricant can be supplied to the seal member.

The guide member is provided on an inner peripheral surface of the bearing cover main body, has a protrusion shape extending to the seal member along the major axis direction of the main shaft, and is parallel to the major axis direction of the main shaft and In the vertical cross section including the guide member, it is desirable that they are arranged substantially horizontally.
As a result, the lubricant scattered from the bearing adheres to the upper surface of the inner peripheral surface of the bearing cover body, and then falls on the guide member along the circumferential direction of the inner surface of the bearing cover body. The lubricant that has fallen on the guide member moves along the guide member to the seal member due to inertia. In this way, the lubricant can be supplied to the seal member.

The guide member is provided on an inner peripheral surface of the bearing cover main body, has a protrusion shape extending to the seal member along the major axis direction of the main shaft, and is parallel to the major axis direction of the main shaft and In a vertical cross section including the guide member, it is desirable that it is inclined downward as it approaches the seal member along the major axis direction of the main shaft.
Thereby, the lubricant scattered from the bearing adheres to the upper surface of the inner peripheral surface of the bearing cover main body, and then falls on the guide member along the inner peripheral surface of the bearing cover main body in the circumferential direction. The lubricant that has fallen on the guide member moves along the guide member to the seal member according to the inclination provided on the guide member. In this way, the lubricant can be supplied to the seal member.

As a structure for guiding the lubricant to the seal member, it is preferable to further include a deflector member attached to the main shaft at a position between the bearing and the seal member.
As a result, the lubricant scattered from the bearing hits the bearing cover, falls on the main shaft, and the lubricating oil that has fallen on the main shaft by the deflector member is again blown to the bearing cover by centrifugal force. The skipped lubricant is supplied to the seal member through the bearing cover. Thereby, the lubricant is supplied to the sliding surfaces of the seal member and the main shaft. This lubricant is returned to the bearing side by the pumping action of the groove formed on the surface of the main shaft.

Preferably, the pump device has variable speed means, and the drive unit is driven by the variable speed means.

According to another aspect of the present invention, a main shaft for rotating an impeller that pressurizes the carrier liquid by driving a driving device in a predetermined direction, a bearing that rotatably supports the main shaft, and the main shaft include: And a seal member that prevents the lubricant of the bearing from passing through the outer peripheral surface of the main shaft and leaking from the sealed fluid side to the atmosphere side, and the bearing cover is scattered from the bearing. A maintenance method for a pump device configured to allow the lubricant to flow through the bearing cover to the seal member, wherein a seal member that slides with an outer peripheral surface of the main shaft is connected to the seal member on the main shaft. A groove inclined so that the lubricant exposed to the outer peripheral surface of the main shaft on the atmosphere side is pushed back to the sealed fluid side when the main shaft rotates. Forming on a peripheral surface, a maintenance method of pumping devices and a step of attaching the sealing member to the main shaft is provided.
Such maintenance suppresses the lubricant from leaking to the atmosphere side of the seal member.

Lubricant leakage in the seal member that prevents the lubricant from leaking from the sealed fluid side to the atmosphere side is suppressed.

The schematic sectional drawing of the pump used as the maintenance object in this embodiment. The schematic exploded perspective view of the pump used as the maintenance object in this embodiment. FIG. 3 is an enlarged cross-sectional view of the vicinity of a main shaft 1, an oil seal 11, and a bearing 2 that are maintenance targets according to the present embodiment. 2B is an enlarged view of the vicinity of the oil seal 11 in FIG. 2A (the broken line portion in FIG. 2A). The expanded sectional view of the main shaft 1, the oil seal 11, and the bearing 2 vicinity after a maintenance. The figure which expanded further the oil seal 11 vicinity of FIG. 3A (dashed line part of FIG. 3A) further. The enlarged view at the time of using the oil seal 11 'different from FIG. 3B. The enlarged view at the time of using the oil seal 11 '' different from FIG. 3B. Process drawing which shows the maintenance procedure of a pump. The schematic sectional drawing of the pump which shows a maintenance process. The schematic sectional drawing of the pump which shows a maintenance process following FIG. The schematic sectional drawing of the pump which shows a maintenance process following FIG. The schematic sectional drawing of the pump which shows a maintenance process following FIG. The schematic sectional drawing of the pump which shows a maintenance process following FIG. The schematic sectional drawing of a pump apparatus with few lubricating oil leaks. The schematic sectional drawing of the pump used as the maintenance object in 2nd Embodiment. The schematic exploded perspective view of the pump used as the maintenance object in 2nd Embodiment. The expanded sectional view of the main axis | shaft 201 used as the maintenance object which concerns on 2nd Embodiment, the oil seal 211, and the bearing 202 vicinity. The figure which further expanded the oil seal 211 vicinity (dashed line part of FIG. 2A) of FIG. 12A. The expanded sectional view of the main shaft 201 after maintenance, the oil seal 211, and the bearing 202 vicinity. The figure which further expanded the oil seal 211 vicinity (dashed line part of FIG. 3A) of FIG. 13A. The enlarged view at the time of using the oil seal 211 'different from FIG. 13B. The enlarged view at the time of using the oil seal 211 '' different from FIG. 13B. Process drawing which shows the maintenance procedure of a pump. The schematic sectional drawing of the pump which shows a maintenance process. The schematic sectional drawing of the pump which shows a maintenance process following FIG. The schematic sectional drawing of the pump which shows a maintenance process following FIG. The schematic sectional drawing of the pump which shows a maintenance process following FIG. The schematic sectional drawing of the pump which shows a maintenance process following FIG. The schematic sectional drawing of a pump apparatus with few lubricating oil leaks. It is a table | surface which shows an example which compared the leakage of the lubricant with the pump apparatus of a prior art, and the pump apparatus which concerns on 2nd Embodiment. It is the graph which showed the result shown in the table | surface of FIG. 21 as a change in elapsed time. It is a longitudinal cross-sectional view which shows a part of structure of the pump apparatus which concerns on a comparative example. It is sectional drawing in X of the pump apparatus of FIG. It is a longitudinal cross-sectional view which shows the structure of a part of pump apparatus which concerns on the modification of 3rd Embodiment. It is a longitudinal cross-sectional view which shows the structure of a part of pump apparatus which concerns on 4th Embodiment. It is a longitudinal cross-sectional view which shows the structure of a part of pump apparatus which concerns on 5th Embodiment. It is a cross-sectional arrow view of the arrow A in the pump apparatus of FIG. In the pump apparatus which concerns on the modification 1 of 5th Embodiment, it is a cross-sectional arrow view of the arrow A of the pump apparatus of FIG. FIG. 30 is a cross-sectional view taken along the line B-B ′ of FIG. 29. FIG. 31 is a cross-sectional view taken along arrow A of the pump device of FIG. 27 in the pump device according to Modification 2 of the fifth embodiment. FIG. 32 is a cross-sectional view taken along the line C-C ′ of FIG. 31. It is a schematic diagram which shows schematic structure of the pump apparatus which concerns on 6th Embodiment. It is DD sectional drawing of FIG. It is sectional drawing which shows the structure of a part of pump apparatus which concerns on 7th Embodiment.

First, the pump device that is the subject of the present invention and the cause of the occurrence of lubricant leakage in such a pump device will be described.

1A and 1B are a schematic cross-sectional view and an exploded perspective view of a target pump device 101, respectively. The pump device 101 includes a pump 100 including an impeller 30, a pump body 32, and a body cover 21, a main shaft 1,

bearings

2 and 3, a bearing body 4, bearing covers 5 and 6, and an

oil seal

11, 12, etc. Further, the pump body 32 includes a suction port 32-2 and a discharge port 32-1 for the transport liquid. The pump device 101 is often installed in a machine room, a pump room, a factory facility, or the like that is distinguished from a residence or a commercial space.

The main shaft 1 is attached to one end side (the right side in FIG. 1A and FIG. 1B) with an impeller 30 and is connected to the main shaft end 20 (the left side) on the other end side via a coupling. It is comprised so that the rotating shaft of an electric motor (not shown) may be connected. When the pump 100 is operated, the pump 100 is driven by the electric motor to rotate in a predetermined direction, so that the pump 100 converts the carrier liquid flowing in from the suction port 32-2 into a centrifugal force due to the rotation of the impeller 30. And pressurize to flow out to the discharge port 32-1. The pump device 101 is a horizontal shaft type pump device in which a main shaft 1 is covered with a bearing body 4 and extends in a substantially horizontal direction, and is rotatably supported by two

bearings

2 and 3 arranged at intervals. is there. A bearing cover 5 through which the main shaft 1 passes is attached to the bearing body 4 by bolts 10 a on the main shaft end 20 side of the bearing 2. On the impeller 30 side of the bearing 3, a bearing cover 6 through which the main shaft 1 passes is attached to the bearing body 4 by bolts 10b.

The main shaft 1 is a large-diameter shaft 1a between the bearing 2 on the main shaft end 20 side and the bearing 3 on the impeller 30 side. The vertical surface of the bearing 2 on the impeller 30 side is in contact with one end of the large-diameter shaft 1a. The motor-side vertical surface of the bearing 3 is in contact with the other end of the large-diameter shaft 1a. The outer surfaces of the

bearings

2 and 3 are sandwiched from both sides by the protruding portions 7 of the bearing covers 5 and 6 attached to the bearing body 4.

The lubricant is stored between the

bearings

2 and 3 in the bearing body 4, and at the time of operation of the pump 100, at least a part of the

bearings

2 and 3 must be immersed in the lubricant. During the operation of the pump 100, the lubricant in the bearing body 4 evaporates due to the temperature rise. Therefore, the bearing body 4 has a cap 14 for removing air and an oil gauge 15 for checking the reduction of the lubricant. Is provided. Further, the lubricant can be discharged out of the bearing body 4 by removing the plug 16. As the lubricant in the present embodiment, liquid lubricant is used, but semi-solid grease may be used. As the pump 100 is operated, the

bearings

2 and 3 become hot and the grease is liquefied.

Oil seals 11 and 12 are respectively incorporated in the bearing covers 5 and 6 in order to prevent the lubricant from leaking outside along the outer peripheral surface of the main shaft 1. Further, a draining ring 13 may be fitted to the main shaft 1 outside the bearing cover 6. Further, a wave washer 9, which is a kind of elastic washer, is preferably interposed between the vertical surface outside the bearing 3 and the bearing cover 6. A compressive stress is applied to the wave washer 9 by the tightening force of the bolt 10 b, and a reaction force to the motor side acts on the main shaft 1 via the bearing 3.

A fishing gear 17 is attached to the upper part of the bearing body 4. The bearing body 4 is supported by a support base 18. Although the bearing body 4 covers the

bearings

2 and 3, an opening 4a is provided in part (see FIG. 1B). The impeller 30 side of the bearing body 4 is fixed to the intermediate plate 37 by bolts 36. The intermediate plate 37 is fixed to the pump body 32 that houses the impeller 30 by bolts 38. Thereby, the bearing body 4 and the pump body 32 are integrated. Gaskets are interposed between the bearing body 4 and the intermediate plate 37 and between the intermediate plate 37 and the pump body 32 for sealing.

A body cover 21 through which the main shaft 1 passes is provided on the main shaft 1 side of the pump body 32. A shaft seal device is applied to the through portion of the body cover 21. Although FIG. 1 shows an example in which the gland packing 23 is used as the shaft seal device, a mechanical seal may be used. Since the shaft seal portion generates rotational friction, a shaft sleeve 25 for the gland packing 23 is fitted to the main shaft 1, and the gland packing is interposed between the shaft sleeve 25 and the tubular portion 21 a of the body cover 21. The gland packing 23 is fastened by bolts 29 through the presser 28.

An impeller 30 is fitted into a key 19 provided at the tip of the main shaft 1 and is fixed by a nut 31. A liner ring 33 is provided between the shroud side I of the impeller 30 and the pump body 32, and a liner ring 34 is provided between the back shroud side B and the body cover 21. A plurality of balance holes 35 are formed near the boss portion of the impeller 30.

FIG. 2A is an enlarged cross-sectional view of the vicinity of the main shaft 1, the oil seal 11 and the bearing 2 of the pump device 101 according to the present embodiment. Moreover, FIG. 2B is the figure which expanded further the oil seal 11 vicinity (FIG. 2A broken line part) of FIG. 2A. As shown in the figure, the main shaft 1 rotates the impeller 30 in a predetermined direction (clockwise as viewed from the electric motor side (left side in FIG. 2A) in this example), so that the pump 100 can function as a liquid transport machine. I can do it. Hereinafter, as shown in FIG. 2B, the space S is surrounded by a horizontal plane including the radial center of the main shaft 1, the oil seal 11, the bearing cover 5, and the bearing 2. The space surrounded by the outer peripheral surface of the main shaft 1, the oil seal 11, the bearing cover 5, the bearing 2, and the oil surface OL of the lubricant is filled with lubricant as mist.

Since the pump device 101 is a horizontal shaft type pump device, the axis of the main shaft 1 is substantially horizontal and substantially parallel to the oil surface OL of the lubricant. The lubricant is periodically replaced or replenished during maintenance, and the oil level OL of the lubricating oil is near the center of the oil gauge 15, specifically, below the lower end of the main shaft 1 and the

bearings

2, 3. Used at the liquid level above the lower end of That is, in a normal state, the pump 100 is operated in a state where a part of the

bearings

2 and 3 located at a position lower than the main shaft 1 is immersed in the lubricating oil.

2B illustrates the oil seal 11 as a lip seal including a reinforcing ring 11a, a seal lip member 11b, a garter spring 11c, and the like. The reinforcing ring 11a has a substantially L-shaped radial cross section, and a seal lip member 11b is attached to the reinforcing ring 11a in an annular shape. The main shaft 1 side of the seal lip member 11b has an approximately inverted cross-sectional shape, and an edge-shaped portion corresponding to the apex of the triangle forms a lip 11d. The lip 11d is deformed when pressed on the outer peripheral surface of the main shaft 1, and slides on the outer peripheral surface of the main shaft 1 with a predetermined axial contact width. A garter spring 11c that presses the lip 11d against the outer peripheral surface of the main shaft 1 is mounted on the outer periphery of the lip 11d.

Here, since the lip 11d slides on the outer peripheral surface of the main shaft 1, a lubricant is required between the sliding portions of the lip 11d and the main shaft 1. With the lubricant, heat generation due to friction of the sliding surface can be suppressed, and the life of the oil seal 11 and the main shaft 1 can be extended. As the lubricant between the sliding portions of the lip 11d and the main shaft 1, the lubricant in the bearing body 4 is used. Further, if the heat generated in the

bearings

2 and 3 in the continuous operation of the pump 1 is transmitted to the lip 11d through the main shaft 1, the lip 11d may be cured and the life may be shortened. A predetermined distance is required between 11.

Thereafter, the sliding portion between the outer peripheral surface of the main shaft 1 and the oil seal 11 (pressure contact surface between the lip 11d and the outer peripheral surface of the main shaft 1) is divided into two spaces on the main shaft end 20 side and the bearing 2 side. The space on the bearing 2 side of the oil seal 11 including the space S as the first space is referred to as the sealed fluid side, and the space outside the pump device 101 and on the spindle end 20 side from the oil seal 11 as the second space is the atmosphere. Called the side.

Here, as described above, the pump device 101 may be used in a high temperature installation environment such as a pump room, or may be used in a factory facility that operates for 24 hours. Under such an environment, when the pump 100 is continuously operated, the lubricant at the sliding portion between the rotating member and the fixed member of the bearing 2 becomes high temperature, and the viscosity of the lubricant is lowered. There is a risk that the amount of lubricant leakage increases from the fluid side to the atmosphere side. Further, the lip groove 1b is formed on the sliding surface on the outer peripheral surface of the main shaft 1 due to deterioration over time, or the pressure of the garter spring 11c is weakened, so that the pressure of the lip 11d on the main shaft 1 is weakened, and the lubricant is removed. The amount of leakage increases from the sealed fluid side to the atmosphere side.

As described above, since a lubricant is necessary for the sliding surface between the oil seal 11 and the outer peripheral surface of the main shaft 1 and the pump device 101 is often installed in a pump chamber or the like, the lubricant is used as the main shaft. 1 is acceptable as long as the main shaft 1 is moistened along the surface of 1. However, when the amount of the lubricant that leaks from the sealed fluid side to the atmosphere side increases, the lubricant may hang down from the main shaft 1 or may be splashed by the centrifugal force caused by the rotation of the main shaft 1 to contaminate the surroundings. . Furthermore, the lubricant stored in the bearing body 4 is reduced, and the frequency of maintenance such as replenishment and replacement of the lubricant is increased. Therefore, in this embodiment shown in FIG. 10, in order to return the lubricant leaked from the oil seal 11 to the atmosphere side to the sealed fluid side, the outer peripheral surface of the main shaft 1 shown in FIGS. A groove 1c as shown in FIG. In addition, hereinafter, in FIG. 1 described above and FIG. 10 of the present embodiment, the same reference numerals are given to the same configurations, and description thereof is omitted.

FIG. 3A is an enlarged cross-sectional view of the vicinity of the main shaft 1, the oil seal 11, and the bearing 2 in the present embodiment shown in FIG. 3B is an enlarged view of the vicinity of the oil seal 11 in FIG. 3A (the broken line portion in FIG. 3A). As illustrated, an inclined groove 1 c (unevenness) is formed on the outer peripheral surface of the main shaft 1. When the main shaft 1 rotates in a clockwise direction when viewed from the electric motor side (main shaft end 20 side), the inclination direction of the groove 1c is inclined in a direction increasing from the main shaft end 20 side toward the bearing 2 side. The groove 1c is preferably formed over the entire circumference, but there may be a part where the groove 1c is not provided. In addition, the recesses and projections of the groove 1c are desirably formed at regular intervals, but the recesses and projections may be formed at irregular intervals.

When the main shaft 1 rotates, an air flow is generated by the groove 1c on the atmosphere side and is pushed back from the atmosphere side to the sealed fluid side. That is, the direction of the inclination of the groove 1c can be said to be the direction in which the first flow FL1 is formed which is a lubricant flow that returns the lubricant on the sliding surface to the bearing 2 side when the main shaft 1 rotates. .

Furthermore, since the pump 100 is operated in a state where the oil level OL of the lubricant is lower than the lower end of the main shaft 1 as described above, the pump device 101 is separated from the bearing 2 in the space S during the operation of the pump 100. The oil seal 11 may be disposed at a position where the lubricant is scattered on the bearing cover 5 and the lubricant on the sliding surface between the lip 11d and the outer peripheral surface of the main shaft 1 exists. As an example of the arrangement position adjustment of the oil seal 11 in the present embodiment, the main shaft 1 of the oil seal 11 is adjusted by adjusting the position of the bearing cover 5 by adjusting the tightening force of the bolt 10 a and the thickness of the protruding portion 7. It is good to adjust the upper arrangement position. Further, not only the position of the oil seal 11 in the main shaft 1 direction but also the position of the bearing 2 in the axial direction may be adjusted. At the time of adjustment, the distance between the bearing 2 and the oil seal 11 is not less than the predetermined distance described above. As an example, the distance between the bearing 2 and the oil seal 11 is about 5 to 50 mm. One or a plurality of bolts 10a and protruding portions 7 may be used.

In the space S, when the oil seal 11 is disposed at a position where the lubricant from the bearing 2 scatters on the oil seal 11, the outer periphery of the lip 11 d and the main shaft 1 is transmitted along the side surface of the bearing cover 5 on the space S side and the oil seal 11. A second flow FL2, which is a flow of lubricant flowing on the sliding surface with the surface, is formed. In the present embodiment, the lubricant is supplied to the oil seal 11 by the second flow FL2, and the lubricant is returned to the bearing body 4 by the first flow FL1, which is the flow of the lubricant by the groove 1c. By repeating the lubricant flows FL1 and FL2, it is possible to prevent the lubricant from leaking to the atmosphere side while maintaining good sliding between the oil seal 11 and the outer peripheral surface of the main shaft 1.

The oil seal 11 is disposed at a position where the lubricant from the bearing 2 scatters, and the outer peripheral surface of the main shaft 1 is disposed on the outer peripheral surface of the main shaft 1 from the oil seal 11 when the pump 100 is operated. A groove 1c inclined in a direction in which the exposed lubricant is pushed back to the sealed fluid side is provided. Therefore, it is possible to prevent the lubricant from leaking to the atmosphere side while maintaining good sliding between the oil seal 11 and the outer peripheral surface of the main shaft 1.

Here, the inclined groove 1c is provided in at least a part of a region adjacent to the atmosphere side with respect to the region facing the oil seal 11 on the outer peripheral surface of the main shaft 1. That is, the groove 1c may be formed on the atmosphere side at least adjacent to the sliding surface with the oil seal 11 on the outer peripheral surface of the main shaft 1 (reference A in FIG. 3B). Thereby, when the main shaft 1 rotates, an air flow is generated by the groove 1c, and an effect of pushing back the lubricant leaked to the atmosphere side by the lubricant flow FL1 is obtained.

Further, the inclined groove 1 c is provided on the sliding surface with the oil seal 11 on the outer peripheral surface of the main shaft 1. That is, the groove 1c may be formed or extended on at least a part of a sliding surface (or lip groove 1b) with the lip 11d on the outer peripheral surface of the main shaft 1 (reference numeral B in FIG. 3B). The pressure of the seal portion on the sliding surface that slides relatively decreases, and bubbles are generated in the oil film of the lubricant in the groove 1c on the sliding surface of the lip 11d and the main shaft 1. By this bubble, the lip 11d, the main shaft 1 and the sliding surface can be reduced in friction (also referred to as “low friction”). Thereby, friction and wear between the lip 11d and the outer peripheral surface of the main shaft 1 can be reduced.

Furthermore, the inclined groove 1c is provided in at least a part of the outer peripheral surface of the main shaft 1 on the sealed fluid side. That is, the groove 1c is adjacent to the sliding surface with the oil seal 11 on the outer peripheral surface of the main shaft 1, and may be formed or further extended in at least a part on the sealed fluid side (reference numeral in FIG. 3B). C). By doing so, the lubricant can be returned to the bearing 2 more. In particular, when the groove 1c is extended until it abuts against the bearing 2 and the lubricant pushed back from the atmosphere side reaches the side surface 2-1 of the bearing 2, the oil surface OL of the lubricant is lower than that of the main shaft 1. The lubricant pushed back from the side can be quickly returned into the bearing 2 along the side surface 2-1 of the bearing 2 positioned below the main shaft 1 through the groove 1c.

Therefore, the oil seal 11 is disposed at the position where the groove 1c is formed and the lubricant from the bearing 2 is scattered on the oil seal 11, thereby preventing the lubricant from being scattered outside and contaminating the surroundings, or the pump device. Maintenance work for replenishing or replacing the lubricant to the bearing body 4 due to the leakage of the lubricant in 101 can be reduced. In addition, even when the pressure of the lip 11d becomes weak due to aging deterioration, the sealing performance can be ensured by returning the lubricant to the sealed fluid side by the first flow FL1, and as a result, the replacement life of the oil seal 11 is increased. Can be long. Furthermore, during the operation of the pump 100, since the lubricant is supplied to the sliding portion of the lip 11d and the main shaft 1 by the second flow FL2 of the lubricant, heat generation and wear due to friction of the sliding surface are generated. The life of the oil seal 11 and the main shaft 1 can be extended.

Further, as shown in FIG. 10, the bearing 3 and the oil seal 12 arranged on the impeller 30 side, the groove 1 c formed on the outer peripheral surface of the main shaft 1 facing the bearing 3 and the oil seal 12, and the lubricant from the bearing 3. By disposing the oil seal 12 at a position where the oil seal 12 scatters, it is possible to suppress the leakage of the lubricant from the oil seal 12 while maintaining good sliding between the oil seal 12 and the main shaft 1.

A shaft sleeve (not shown) may be used at a position including at least the sliding surfaces of the oil seals 11 and 12 in the main shaft 1 for protecting the sliding surface of the main shaft 1. In that case, the main shaft 1 is fitted in the shaft sleeve, and the main shaft 1 and the shaft sleeve rotate concentrically in the radial direction. Therefore, the shaft sleeve is a part of the main shaft. Furthermore, also in the pump device 101 using the oil seal 11 ′ or 11 ″ shown in FIG. 3C or 3D described later, the formation of the groove 1c and the lubricant from the

bearing

2 or 3 are applied to the oil seal 11 ′ or 11 ″. By disposing the oil seal 11 ′ or 11 ″ at a position where it can be scattered, the sliding of the oil seal 11 ′ or 11 ″ and the main shaft 1 is kept good, and leakage of the lubricant to the atmosphere side is suppressed. be able to.

In FIG. 1A, the pump device 101 using a single-stage single-suction centrifugal pump has been described as an example. However, any pump device, particularly an oil bath type bearing using a lubricant, and a bearing lubricant are sealed. The groove 1c and the arrangement of the bearing and the oil seal on the outer peripheral surface of the main shaft 1 according to the present embodiment can be applied to a horizontal shaft type pump device provided with an oil seal and a horizontal shaft pump.

In the pump apparatus 101 which is an example of the embodiment, the following maintenance can be performed on the pump apparatus 101 in FIG. 1 in which a predetermined amount or more of the lubricant leaks to the atmosphere side due to deterioration over time. That is, the oil seal 11 and the main shaft 1 in FIG. 2A and FIG. 2B are separated, and a groove 1c as shown in FIG. 3A and FIG. By attaching the oil seal 11 and the main shaft 1, the pump device 101 shown in FIG. 10 is obtained.

At this time, the oil seal 11 does not have to be completely separated from the main shaft 1. It is good also as a process separated from the sliding surface with the oil seal in the outer peripheral surface of the main shaft 1 by sliding the oil seal 11 on the main shaft 1.

FIG. 3A is an enlarged sectional view of the vicinity of the main shaft 1, the oil seal 11 and the bearing 2 after maintenance. 3B is an enlarged view of the vicinity of the oil seal 11 in FIG. 3A (the broken line portion in FIG. 3A). As illustrated, an inclined groove 1 c (unevenness) is formed on the outer peripheral surface of the main shaft 1. When the main shaft 1 rotates in the clockwise direction when viewed from the motor side, the inclination direction of the groove 1c is inclined in a direction that increases from the motor side toward the bearing 2 side.

By forming such a groove 1c, when the main shaft 1 rotates, an air flow is generated by the groove 1c in the atmosphere, whereby the lubricant is pushed back from the atmosphere side to the sealed fluid side. That is, it can be said that the inclination direction of the groove 1c is a direction in which the air-side lubricant is returned to the bearing 2 side when the main shaft 1 rotates. Thereby, it can suppress that a lubricant leaks.

If the groove 1c is formed at least on the atmosphere side of the main shaft 1, an effect of pushing back the lubricant can be obtained by generating an air flow by the groove 1c when the main shaft 1 rotates. The groove 1c may be formed or extended on at least a part of the sliding surface (or lip groove 1b) of the main shaft 1 (reference numeral B in FIG. 3B). Thereby, the friction between the oil seal 11 and the main shaft 1 can be reduced. Further, the groove 1c may be formed or extended from the sliding surface (or lip groove 1b) of the main shaft 1 to at least a part on the bearing 2 side (reference numeral C in FIG. 3B). This further increases the effect of pushing back the lubricant.

Thus, in the present embodiment, the oil seal 11 and the bearing 2 are arranged at a position where the lubricant scattered from the bearing 2 reaches the sliding surface between the oil seal 11 and the outer peripheral surface of the main shaft 1. Then, when the main shaft 1 rotates, a part of such a lubricant is pushed back to the bearing 2 side. As a result, leakage of the lubricant is suppressed, and an appropriate amount of lubricant is interposed on the sliding surface between the oil seal 11 and the main shaft 1.

Note that such maintenance can also be applied to the outer peripheral surface of the main shaft 1 facing the bearing 3 and the oil seal 12 and the bearing 3 and the oil seal 12 arranged on the impeller 30 side in FIG. 1. That is, the sliding surface between the oil seal 12 and the outer peripheral surface of the main shaft 1 is separated, and the groove 1c inclined from the sliding surface between the oil seal 12 and the main shaft 1 to the impeller 30 side (opposite side of the bearing 3) is formed. May be. The inclination direction of the groove 1c is a direction in which the lubricant on the sliding surface is returned to the bearing 3 side when the main shaft 1 rotates, and is opposite to the groove 1c formed on the bearing 2 side.

Further, various oil seals can be applied.
FIG. 3C is an enlarged view when an oil seal 11 ′ different from FIG. 3B is applied. As a part of the main shaft 1, a sealing sleeve 80 is provided. The oil seal 11 'includes a resin-made seal lip member 81 having an L-shaped cross section. The seal lip member 81 includes an outer joint metal ring 82 having a substantially L-shaped cross section and an inner side having a substantially L-shaped cross section. Is held between the presser metal ring 83. A cylindrical lip 84 is formed on the inner peripheral side of the seal lip member 81, and this cylindrical lip 84 corresponds to the lip 11 d of FIG. 3B and seals the fluid to be sealed in close contact with the outer peripheral surface of the sealing sleeve 80. . When the oil seal 11 ′ shown in FIG. 3C is used, the groove 1 c may be formed in the sealing sleeve 80 that is a part of the main shaft 1.

FIG. 3D is an enlarged view when an oil seal 11 ″ different from that in FIG. 3B is applied. The oil seal 11 ″ has a cylindrical portion 92. Depending on the installation environment, foreign substances such as dust may enter from the atmosphere side. Therefore, the cylindrical portion 92 prevents foreign matter from entering the oil seal 11 ″. Therefore, it is possible to reduce wear of the sliding surfaces on the lip portion of the oil seal 11 ″ and the outer peripheral surface of the main shaft 1 due to the mixing of foreign matter from the atmosphere side.

Hereinafter, the maintenance procedure will be described in detail.
FIG. 4 is a process diagram illustrating a maintenance procedure of the pump device 101. Note that FIG. 4 is merely an example of a procedure, and each step may be appropriately replaced or omitted.

First, disconnect from the motor (not shown). (Step S1). Further, the plug 16 is removed and the lubricant is removed from the bearing body 4 (step S2). Subsequently, the bolt 38 for the pump body 32 is removed, and the intermediate plate 37, the body cover 21 and the bearing body 4 are removed from the pump body 32 (step S3). As a result, the state shown in FIG. 5 is obtained.

Thereafter, the nut 31 for the impeller 30 is removed, and the impeller 30 is removed from the main shaft 1 (step S4). Then, the key 19 on the impeller 30 side is removed from the main shaft 1. As a result, the state shown in FIG. 6 is obtained. Further, the bolt 36 is removed, and the intermediate plate 37 and the body cover 21 are removed from the bearing body 4 (step S5). Next, the bolts 29 for the gland packing 23 are removed, and the gland packing 23 is removed (step S6). As a result, the state shown in FIG. 7 is obtained.

And when the draining ring 13 exists, the draining ring 13 is extracted from the main shaft 1 (step S7). Next, the

bolts

10a and 10b for the bearing covers 5 and 6 are removed, the bearing covers 5 and 6 and the oil seals 11 and 12 are removed from the bearing body 4, and the main shaft 1 is pulled out (step S8). As a result, the state shown in FIG. 8 is obtained. In this way, the main shaft 1 and the oil seals 11 and 12 are separated. When the main shaft 1 is pulled out, the rotation state of the

bearings

2 and 3 is inspected, and if the rotation is not smooth, the

bearings

2 and 3 are replaced.

Then, the groove 1c described with reference to FIGS. 3A and 3B is formed in the vicinity of the

bearings

2 and 3 in the main shaft 1 (step S9). As a result, the state shown in FIG. 9 is obtained. Specifically, the groove 1 c is formed by scratching the outer peripheral surface of the main shaft 1. The groove 1c is preferably formed over the entire circumference, but there may be a part where the groove 1c is not provided.

Then, if necessary, the oil seals 11 and 12 are made new and the pump is assembled in the reverse procedure. Accordingly, it can be said that a new pump device (lubricant leakage suppressing pump device) with less lubricant leakage shown in FIG. 10 is manufactured.

Thus, in this embodiment, it is possible to prevent the lubricant from leaking along the main shaft 1 by a simple method of forming a groove 1c by scratching the outer peripheral surface of the main shaft 1 in a predetermined direction.

As a maintenance, the groove 1c may not be formed in the main shaft 1, but the groove 1c may be provided in advance on the outer peripheral surface of the main shaft 1 of a new pump. In FIG. 1A, the pump device 101 using the single-stage single-suction centrifugal pump has been described as an example. However, any pump device, in particular, an oil bath type bearing using a lubricant, an oil seal, and a horizontal shaft pump are used. This embodiment can be applied to a horizontal shaft type pump device provided with

The pump device 101 that has been maintained according to the above-described procedure can reduce maintenance work for replenishment or replacement of lubricant due to lubricant leakage. Further, even when the pressure of the lip 11d becomes weak due to deterioration over time, the sealing performance can be secured by returning the lubricant to the bearing body 4 by the first flow FL1, and as a result, the replacement life of the oil seal 11 is extended. can do. Further, during the operation of the pump, the lubricant is supplied between the lip 11d and the sliding portion of the outer peripheral surface of the main shaft 1 by the second flow FL2 of the lubricant. Wear can be suppressed and the life of the oil seal 11 and the main shaft 1 can be extended. 1, the bearing 3 and the oil seal 12 disposed on the impeller 30 side, and the outer peripheral surface of the main shaft 1 facing the bearing 3 and the oil seal 12 are also applicable.

The above-described embodiments are described for the purpose of enabling the person having ordinary knowledge in the technical field to which the present invention belongs to implement the present invention. Various modifications of the above embodiment can be naturally made by those skilled in the art, and the technical idea of the present invention can be applied to other embodiments. Therefore, the present invention should not be limited to the described embodiments, but should be the widest scope according to the technical idea defined by the claims.

<Second Embodiment>
Next, a second embodiment will be described. First, problems of the prior art will be described.

In Patent Document 6, at least the upper half of the inner surface of the end wall of the outer box (bearing cover) is provided with an oil flow lower portion surrounding the rotating shaft. Oil drops that flow along the inner wall of the outer wall of the outer box from the upper part of the rotating shaft flow down to the lower part of the outer box so as to avoid the rotating shaft by the lower part of the oil flow, and oil leaks from between the penetrating part and the rotating shaft. To prevent it. Specifically, since the groove surrounding the rotation shaft is formed on the inner surface of the end wall, the oil droplet flows into the groove and is guided and flows down so as to avoid the rotation shaft. And it flows out from the groove | channel lowest part and is stored by the lower part of an outer box. The oil droplets are guided by the groove and flow down so as to avoid the rotating shaft, so that the oil is prevented from leaking between the rotating shaft and the seal member.

However, the scattering of oil droplets from the bearing varies depending on the rotational speed of the rotating shaft. Due to the recent demand for energy saving, there are cases where the rotational speed of the pump is controlled (for example, the known constant pressure control or estimated terminal pressure control) using variable speed means such as an inverter. When the rotation speed of the rotating shaft is low, the scattering distance of the oil droplets scattered from the bearing is shortened, and the oil droplets do not reach the outer casing (bearing cover) and travel along the rotating shaft in the circumferential direction. There is a problem that oil may leak from between the rotating shafts. Further, as a lubricant for a bearing of a rotary machine, not only a liquid lubricant but also a semi-solid grease or the like may be used. However, in Patent Document 6, a semi-solid lubricant or a deteriorated and high viscosity is used. If lubricating oil is used, it will harden in the groove surrounding the rotating shaft and will not act to flow down the oil droplets.

In Patent Document 7, an oil cover and an oil drain ring are arranged between the bearing and the bearing cover, and an oil relief groove is formed in a portion of the inner surface of the bearing cover facing the bearing. In Patent Document 7, the bearing cover, the oil cover, and the oil drain ring prevent the lubricating oil scattered from the bearing when the main shaft rotates from flowing out of the oil escape groove to the outside (motor side). It is disclosed that it functions as a lubricating oil outflow suppression device.

However, this lubricating oil spill suppression device has a problem that the number of parts increases because the oil cover is attached to the bearing cover. Moreover, it is used for the mechanism which seals lubricating oil with an oil relief groove. As a lubricant for a bearing of a rotating machine, not only a liquid lubricant but also a semi-solid grease or the like may be used. However, the lubricant outflow suppression device of Patent Document 7 is a semi-solid lubricant and a lubricant. An oil seal is not considered as a mechanism for sealing the oil.

In Patent Document 4, the pumping portion machined on the rotating shaft has three actions: leakage prevention at rest, action of sucking the sealed fluid, and action of discharging the sealed fluid. Moreover, since it corresponds also to the case where a sliding surface rotates to both directions, the shape of a pumping part is complicated and processing precision is requested | required. For this reason, when taking measures against lubricant leakage during maintenance, it is difficult to perform such processing where a pump where the lubricant has leaked is installed, such as factories with dedicated processing machines. There is a problem that it takes time and labor.

Furthermore, the leakage of the bearing lubricant in the pump device that pressurizes and feeds the carrier liquid varies depending on the installation location, the environment in which it is used, and the usage situation. Further, the range in which the leakage of the lubricant is allowed varies depending on the operator of the pump. Therefore, it is desired that the countermeasure against the leakage of the lubricant is a means that can be easily processed at the time of shipment or maintenance. In particular, when taking measures against lubricant leakage during maintenance, it is desirable that the measures can be performed regardless of the environmental temperature, the rotational speed of the pump, the type of lubricant in the bearing, the lubricant sealing device, and the like.

FIG. 11A and FIG. 11B are a schematic sectional view and an exploded perspective view of a target pump device 301, respectively. The pump device 301 includes a pump 300 including an impeller 230, a pump body (pump casing) 232, and a body cover 221, a main shaft (shaft) 201,

bearings

202 and 203, a bearing body 204, and bearing covers 205 and 206. And oil seals 211, 212, and the like. The pump body 232 includes a suction port 232-2 and a discharge port 232-1 for the transport liquid. Here, the oil seals 211 and 212 are an example of a seal member that seals between the main shaft 201 and the bearing cover 205 that are concentrically arranged inside and outside in the radial direction. As an example, the pump device 301 is often installed in a machine room, a pump room, a factory facility, or the like that is distinguished from a residence or a commercial space.

The main shaft 201 has an impeller 230 attached to one end side (the right side in FIG. 11A and FIG. 11B), and a main shaft end 220 (the left side) on the other end side via a coupling. A rotating shaft (not shown) is connected. When the pump 300 is operated, the main shaft 201 driven by the electric motor rotates in a predetermined direction. The pump 300 pressurizes the carrier liquid flowing in from the suction port 232-2 by the centrifugal force generated by the rotation of the impeller 230, and flows out to the discharge port 232-1. The pump device 301 is a horizontal axis type pump device. Specifically, the main shaft 201 is covered with a bearing body 204 and extends in a substantially horizontal direction, and is rotatably supported by two

bearings

202 and 203 arranged with a space therebetween. A bearing cover 205 through which the main shaft 201 passes is attached to the bearing body (bearing housing) 204 by a bolt 210a on the main shaft end 220 side of the bearing 202. On the impeller 230 side of the bearing 203, a bearing cover 206 through which the main shaft 201 passes is attached to the bearing body 204 with bolts 210b. Thereby, the bearing cover 205 covers at least a part of the outer ring of the bearing 203. Further, the bearing cover 205 and the bearing body 204 through which the main shaft 201 passes may be integrally formed.

The main shaft 201 is a large-diameter shaft 201a between the bearing 202 on the main shaft end 220 side and the bearing 203 on the impeller 230 side. The vertical surface of the bearing 202 on the impeller 230 side is in contact with one end of the large-diameter shaft 201a. The motor-side vertical surface of the bearing 203 is in contact with the other end of the large-diameter shaft 201a. The outer surfaces of the outer rings of the

bearings

202 and 203 are sandwiched from both sides by protruding portions 207 of bearing covers 205 and 206 attached to the bearing body 204. Thereby, the bearing cover 205 supports the bearing 202 as an example, and the bearing cover 206 supports the bearing 203.

The lubricant is stored between the

bearings

202 and 203 in the bearing body 204, and at least a part of the

bearings

202 and 203 is immersed in the lubricant when the pump 300 is operated. During the operation of the pump 300, the lubricant in the bearing body 204 evaporates due to a rise in temperature. Therefore, the bearing body 204 has a cap 214 for removing air and an oil gauge 215 for checking the reduction of the lubricant. Is provided. Further, when the plug 216 is removed, the lubricant can be discharged out of the bearing body 204. In addition, although the liquid lubricant is used for the lubricant in the present embodiment, semi-solid grease may be used. As the pump 300 is operated, the

bearings

202 and 203 become hot and the grease is liquefied.

Oil seals 211 and 212 are incorporated in the bearing covers 205 and 206 to prevent the lubricant from leaking outside along the outer peripheral surface of the main shaft 201. Further, a draining ring 213 may be fitted to the main shaft 201 outside the bearing cover 206. Further, a wave washer 209, which is a kind of elastic washer, is preferably interposed between the vertical surface outside the bearing 203 and the bearing cover 206. The wave washer 209 is given a compressive stress by the tightening force of the bolt 210 b, and the reaction force to the motor side acts on the main shaft 201 via the bearing 203.

The fishing tackle 217 is attached to the upper part of the bearing body 204. The bearing body 204 is supported by a support base 218. The opening 204a is provided in the bearing body 204 (see FIG. 11B). The impeller 230 side of the bearing body 204 is fixed to the intermediate plate 237 by bolts 236, and the intermediate plate 237 is fixed to the pump body 232 in which the impeller 230 is housed by bolts 238. Thereby, the bearing body 204 and the pump body 232 are integrated. Gaskets are interposed between the bearing body 24 and the intermediate plate 237 and between the intermediate plate 237 and the pump body 232 for sealing.

The body cover 221 through which the main shaft 201 passes is provided on the main shaft 201 side of the pump body 232. A through portion of the main shaft 201 of the body cover 221 includes a shaft seal device. Although FIG. 11 shows an example in which the gland packing 223 is used as the shaft seal device, the shaft seal device may be a mechanical seal. Since the shaft seal portion generates rotational friction, a shaft sleeve 225 for the gland packing 223 is fitted to the main shaft 201, and the gland packing is interposed between the shaft sleeve 225 and the cylindrical portion 221 a of the body cover 221. The gland packing 223 is tightened by the bolt 229 through the presser 228.

The impeller 230 is fitted into a key 219 provided at the tip of the main shaft 201 and is fixed to the main shaft 201 by a nut 231. The liner ring 233 is provided between the shroud side I of the impeller 230 and the pump body 232. The liner ring 234 is provided between the back shroud side B and the body cover 221. The plurality of balance holes 235 are formed in the vicinity of the boss portion of the impeller 230.

FIG. 12A is an enlarged cross-sectional view of the vicinity of the main shaft 201, the oil seal 211, and the bearing 202 of the pump device 301 according to the second embodiment. 12B is an enlarged view of the vicinity of the oil seal 211 in FIG. 12A (the broken line portion in FIG. 12A). As illustrated, when the impeller 230 is rotated in a predetermined direction (clockwise as viewed from the electric motor side (left side in FIG. 12A) in this example), the pump 300 functions as a liquid transport machine. Hereinafter, as shown in FIG. 12B, a space S surrounded by a horizontal plane including the radial center of the main shaft 201, the oil seal 211, the bearing cover 205, and the bearing 202 is assumed. The space surrounded by the outer peripheral surface of the main shaft 201, the oil seal 211, the bearing cover 205, the bearing 202, and the oil surface OL of the lubricant is filled with lubricant as oil smoke (mist).

Since the pump device 301 is a horizontal axis type pump device, the main shaft 201 is substantially horizontal and substantially parallel to the oil surface OL of the lubricant. Further, the lubricant is periodically replaced or replenished during maintenance, and the oil level OL of the lubricating oil is near the center of the oil gauge 215, specifically, below the lower end of the main shaft 201 and the

bearings

202 and 203. Used at the liquid level above the lower end of That is, the pump 300 is operated in a state where a part of the

bearings

202 and 203 located at a position lower than the main shaft 201 is immersed in the lubricating oil.

The oil seal 211 uses a deformable material such as felt, synthetic rubber, or synthetic resin, and performs a sealing action by bringing the tip into frictional contact with the main shaft 201. As an example, the oil seal 211 in FIG. 12B illustrates a lip seal including a reinforcing ring 211a, a seal lip member 211b, a garter spring 211c, and the like. The reinforcing ring 211a has a substantially L-shaped radial cross section, and a seal lip member 211b is attached to the reinforcing ring 211a in an annular shape. The main shaft 201 side of the seal lip member 211b has a substantially inverted cross-sectional shape, and an edge-shaped portion corresponding to the apex of the triangle forms a lip 211d. The lip 211d is deformed when pressed onto the outer peripheral surface of the main shaft 201 and slides on the outer peripheral surface of the main shaft 201 with a predetermined axial contact width. A garter spring 211c that presses the lip 211d against the outer peripheral surface of the main shaft 201 is attached to the outer periphery of the lip 211d.

Here, since the lip 211d slides on the outer peripheral surface of the main shaft 201, a lubricant is required between the sliding portions of the lip 211d and the main shaft 201. The life of the oil seal 211 and the main shaft 201 can be extended by suppressing heat generation due to friction of the sliding surface with the lubricant. As the lubricant between the sliding portions of the lip 211d and the main shaft 201, the lubricant in the bearing body 204 is used. In addition, when the heat of the

bearings

202 and 203 is transmitted to the lip 211d through the main shaft 201, the lip 211d is cured to reduce the life, so that a predetermined distance is required between the

bearings

202 and 203 and the oil seal 211. .

Thereafter, the first space on the main shaft end 220 side and the second space on the bearing 202 side at the sliding portion between the outer peripheral surface of the main shaft 201 and the oil seal 211 (pressure contact surface between the lip 211d and the outer peripheral surface of the main shaft 201). It is divided into two spaces. The first space is a space on the bearing 202 side of the oil seal 211 including the space S, and is referred to as a sealed fluid side. The second space is a space on the outside of the pump device 301 and on the main shaft end 220 side from the oil seal 211, and is referred to as the atmosphere side.

Here, as described above, the pump device 301 is used in an installation environment where the temperature is high, such as a pump chamber, as an example. In another example, the pump device 301 is used in factory equipment that operates for 24 hours. In this way, when the pump 300 is continuously operated in an environment where the outside air temperature is high, the lubricant in the sliding portion between the rotating member and the fixed member of the bearing 202 becomes high temperature and the viscosity becomes low. Then, the oil seal 211 increases the amount of lubricant leaking from the sealed fluid side to the atmosphere side. In addition, when the lip groove 201b is formed due to aging on the sliding surface of the main shaft 201, the amount of the lubricant leaking from the sealed fluid side to the atmosphere side due to insufficient pressing of the lip 211d to the main shaft 201. Will increase. Further, when the pressure of the garter spring 211c is weakened due to aging, the pressure of the lip 211d on the main shaft 201 is insufficient, and the amount of lubricant leaking from the sealed fluid side to the atmosphere side increases.

As described above, the sliding surface between the oil seal 211 and the outer peripheral surface of the main shaft 201 requires a lubricant. The pump device 301 is often installed in a pump chamber or the like. Therefore, the operator of the pump device 301 allows the lubricant that leaks from the sealed fluid side to the atmosphere side along the surface of the main shaft 201 to be wet. However, when the amount of lubricant that leaks from the sealed fluid side to the atmosphere side increases, the lubricant hangs down from the main shaft 201 or splashes due to the centrifugal force generated by the rotation of the main shaft 201, thereby contaminating the surroundings. Furthermore, the lubricant stored in the bearing body 204 decreases, and the pump device 301 increases the frequency of maintenance such as replenishment and replacement of the lubricant. Therefore, in the present embodiment shown in FIG. 20, in order to return the lubricant leaking from the oil seal 211 to the atmosphere side to the sealed fluid side, the outer surface of the main shaft 201 shown in FIGS. 12A and 12B is shown in FIGS. 13A and 13B. A groove 201c as shown is formed. In addition, hereinafter, in FIG. 11 described above and FIG. 20 of the present embodiment, the same reference numerals are given to the same configurations, and the description thereof is omitted.

FIG. 13A is an enlarged cross-sectional view of the vicinity of the main shaft 201, the oil seal 211, and the bearing 202 in the present embodiment shown in FIG. 13B is an enlarged view of the vicinity of the oil seal 211 in FIG. 13A (the broken line portion in FIG. 13A). As shown in the figure, the main shaft 201 forms a groove 201c (unevenness) inclined on the outer peripheral surface. When the main shaft 201 rotates in the clockwise direction when viewed from the electric motor side (main shaft end 220 side), the inclination direction of the groove 201c is on the main shaft end 220 side on the right side surface viewed from the electric motor side (main shaft end 220 side). To the bearing 202 side. The groove 201c is preferably formed over the entire circumference of the main shaft 201, but a portion of the main shaft 201 that does not have the groove 201c may be provided. In addition, the recesses and projections of the groove 201c are desirably formed at regular intervals, but the recesses and projections may be formed at irregular intervals.

When the main shaft 201 is rotated by the operation of the pump 300, an air flow is generated by the groove 201c on the atmosphere side, and the lubricant is pushed back from the atmosphere side to the sealed fluid side. That is, the direction of the inclination of the groove 201c forms the first flow FL1 in which the lubricant on the outer peripheral surface of the main shaft 201 returns from the main shaft end 220 side to the bearing 202 side when the main shaft 201 rotates by the operation of the pump 300. Direction.

Furthermore, in the pump device 301, when the main shaft is stationary, the oil level OL of the lubricant is at a liquid level below the main shaft 201 as described above. The oil seal 211 is a position where the lubricant from the bearing 202 scatters in the bearing cover 205 in the space S during the operation of the pump 300 and the lubricant on the sliding surface between the lip 211d and the outer peripheral surface of the main shaft 201 exists. It is good to arrange in. As an example of the adjustment method of the arrangement position of the oil seal 211 in this embodiment, the arrangement position of the oil seal 211 adjusts the position of the bearing cover 205 by adjusting the tightening force of the bolt 210a and the thickness of the protruding portion 207. Further, the arrangement position of the oil seal 211 may be adjusted not only by adjusting the position of the oil seal 211 in the direction of the main shaft 201 but also by adjusting the position of the bearing 202 in the axial direction. At the time of adjustment, the distance between the bearing 202 and the oil seal 211 is not less than the predetermined distance described above. As an example, the distance between the bearing 202 and the oil seal 211 is about 5 to 50 mm. One or a plurality of bolts 210a and protruding portions 207 may be used.

In the space S, when the oil seal 211 is disposed at a position where the lubricant from the bearing 202 scatters on the oil seal 211, the outer periphery of the lip 211 d and the main shaft 201 is transmitted along the side surface of the bearing cover 205 on the space S side and the oil seal 211. A second flow FL2, which is a flow of lubricant flowing on the sliding surface with the surface, is formed. In the present embodiment, the lubricant is supplied to the oil seal 211 by the second flow FL2, and the lubricant is returned to the bearing body 204 by the first flow FL1, which is the flow of the lubricant by the groove 201c. By repeating the first flow FL1 and the second flow FL2 of the lubricant, the sliding of the oil seal 211 and the outer peripheral surface of the main shaft 201 is kept good, and the leakage of the lubricant to the atmosphere side is suppressed. it can.

The oil seal 211 in the pump device 301 is disposed at a position where the lubricant from the bearing 202 scatters, and the outer peripheral surface of the main shaft 201 is provided with a groove 201c. Then, when the pump 300 is operated, the groove 201c is inclined in a direction in which the lubricant exposed from the oil seal 211 to the outer peripheral surface of the main shaft 201 on the atmosphere side is pushed back to the sealed fluid side. Thereby, the pump apparatus 301 can suppress the lubricant of the bearing 202 from leaking to the atmosphere side while maintaining good sliding between the oil seal 211 and the outer peripheral surface of the main shaft 201.

Here, the inclined groove 201c is provided in at least a part of the outer peripheral surface of the main shaft 201 on the atmosphere side. That is, this groove 201c may be formed on the atmosphere side adjacent to at least the sliding surface with the oil seal 211 on the outer peripheral surface of the main shaft 201 (reference A in FIG. 13B). Accordingly, when the main shaft 201 rotates, an air flow is generated on the outer peripheral surface of the main shaft 201 by the groove 201c, and an effect of pushing back the lubricant leaked to the atmosphere side by the lubricant flow FL1 is obtained.

Further, the inclined groove 201c is provided on a sliding surface with the oil seal 211 on the outer peripheral surface of the main shaft 201. That is, the groove 201c may be formed or extended in at least a part of a sliding surface (or lip groove 201b) with the lip 211d on the outer peripheral surface of the main shaft 201 (reference numeral B in FIG. 13B). The sliding surface between the lip 211d and the main shaft 201 reduces the pressure of the seal portion on the sliding surface that slides relatively, and the lubricant oil film in the groove 201c on the sliding surface between the lip 211d and the main shaft 201 Bubbles are generated inside. The bubbles can reduce the friction between the lip 211d, the main shaft 201, and the sliding surface (also referred to as “low friction”). As a result, friction and wear between the lip 211d and the outer peripheral surface of the main shaft 201 can be reduced.

Furthermore, the inclined groove 201c is provided in at least a part of the outer peripheral surface of the main shaft 201 on the sealed fluid side. That is, the groove 201c is adjacent to the sliding surface of the outer peripheral surface of the main shaft 201 with the oil seal 211, and may be formed or further extended in at least part of the sealed fluid side (reference numeral in FIG. 13B). C). By doing so, the pump device 301 can return the lubricant toward the bearing 202 more. In particular, when the groove 201c is extended to contact the bearing 202 and the lubricant pushed back from the atmosphere side reaches the side surface 202-1 of the bearing 202, the oil surface OL of the lubricant is lower than that of the main shaft 201. The lubricant pushed back from the side can be quickly returned into the bearing 202 along the side surface 202-1 of the bearing 202 positioned below the main shaft 201 through the groove 201c.

Therefore, the pump device 301 disposes the periphery by forming the groove 201c of the main shaft 201 and disposing the oil seal 211 at a position where the lubricant from the bearing 202 scatters on the oil seal 211, thereby contaminating the surroundings. Thus, the maintenance work for replenishing or replacing the lubricant to the bearing body 204 can be reduced. Even when the pressure on the lip 211d is weakened due to aging, the lubricant leaked to the atmosphere side is returned to the sealed fluid side by the first flow FL1. Thus, since the pump apparatus 301 can ensure the sealing performance of the oil seal 211, the pump apparatus 301 can extend the replacement life of the oil seal 211 as a result. Furthermore, during the operation of the pump 300, the lubricant is supplied to the sliding portion of the lip 211d and the main shaft 201 by the second flow FL2 of the lubricant. Therefore, heat generation and wear due to friction of the sliding surface can be suppressed, and the life of the oil seal 211 and the main shaft 201 can be extended.

Further, as shown in FIG. 20, a groove 201 c is also formed on the outer peripheral surface of the main shaft 201 facing the oil seal 212 arranged on the impeller 230 side, and the lubricant from the bearing 203 is scattered on the oil seal 212. By disposing the oil seal 212 at the position, it is possible to suppress the leakage of the lubricant from the oil seal 212 while maintaining good sliding between the oil seal 212 and the main shaft 201.

When the main shaft 201 rotates in the counterclockwise direction when viewed from the impeller 230 side, the inclination direction of the groove 201c formed on the outer peripheral surface of the main shaft 201 facing the oil seal 212 is viewed from the impeller 230 side. The left side surface is inclined in a direction that increases from the impeller 230 side toward the bearing 203 side.

In addition, the sliding surface of the

oil seal

211 or 212 of the main shaft 201 may use a shaft sleeve (not shown) for protection. Since the main shaft 201 is fitted into the shaft sleeve, the main shaft 201 and the shaft sleeve rotate concentrically in the radial direction. Therefore, the shaft sleeve is a part of the main shaft 201. Further, also in the pump device 301 using the oil seal 211 ′ of FIG. 13C described later, the oil seal 211 ′ is formed at a position where the groove 201c is formed and the lubricant from the bearing 202 or 203 can be scattered on the oil seal 211 ′. By disposing, the pump device 301 can suppress the lubricant from leaking to the atmosphere side while maintaining good sliding between the oil seal 211 ′ and the main shaft 201. Also in the pump device 301 using the oil seal 211 ″ of FIG. 13D, the oil seal 211 ′ ′ is provided at a position where the groove 201c is formed and the lubricant from the bearing 202 or 203 can be scattered on the oil seal 211 ′. By disposing, the pump device 301 can suppress the leakage of the lubricant to the atmosphere side while maintaining good sliding between the oil seal 211 ′ and the main shaft 201.

Moreover, FIG. 11A illustrated and demonstrated the pump apparatus 301 using the single stage piece suction centrifugal pump. However, the groove 201c and the arrangement of the bearing and the oil seal on the outer peripheral surface of the main shaft 201 according to the present embodiment are arranged according to any pump device, particularly an oil bath type bearing using a lubricant, and an oil seal for sealing the lubricant of the bearing. And a horizontal axis type pump device provided with a horizontal axis pump.

In the pump device 301 as an example of the embodiment, an operator who performs maintenance performs the following maintenance on the pump device 301 in FIG. 11 in which a predetermined amount or more of lubricant leaks to the atmosphere due to aging. You can also. That is, the operator separates the oil seal 211 and the main shaft 201 in FIGS. 12A and 12B, forms a groove 201 c as shown in FIGS. 13A and 13B on the outer peripheral surface of the main shaft 201, and then returns to the original oil seal. By attaching 211 or a new oil seal 211 and the main shaft 201, a pump device 301 shown in FIG.

At this time, the oil seal 211 does not have to be completely separated from the main shaft 201. The oil seal 211 may be slid on the main shaft 201 and separated from the sliding surface with the main shaft 201.

FIG. 13A is an enlarged cross-sectional view of the vicinity of the main shaft 201, the oil seal 211, and the bearing 202 after maintenance. 13B is an enlarged view of the vicinity of the oil seal 211 in FIG. 13A (the broken line portion in FIG. 13A). As illustrated, an inclined groove 201 c (unevenness) is formed on the outer peripheral surface of the main shaft 201. When the main shaft 201 rotates in the clockwise direction when viewed from the motor side, the inclination direction of the groove 201c in the vicinity of the oil seal 211 is the bearing 202 from the motor side on the right side surface when viewed from the motor side (main shaft end 220 side). It is inclined in the direction of increasing toward the side.

When such a groove 201c is formed, when the main shaft 201 rotates, an air flow is generated by the groove 201c in the atmosphere. Then, the lubricant is pushed back from the atmosphere side to the sealed fluid side. That is, it can be said that the inclination direction of the groove 201c is a direction in which the air-side lubricant is returned to the bearing 202 side when the main shaft 201 rotates. Thereby, it can suppress that a lubricant leaks.

If the groove 201c is formed at least on the atmosphere side of the main shaft 201, an effect of pushing back the lubricant is obtained by rotating the main shaft 201 to generate an air flow by the groove 201c. Further, the groove 201c may be formed or extended on at least a part of the sliding surface (or lip groove 201b) of the main shaft 201 (reference numeral B in FIG. 13B). Thereby, the friction between the oil seal 211 and the main shaft 201 can be reduced. Further, the groove 201c may be formed or extended from at least a part of the bearing 202 side (symbol C in FIG. 13B) from the sliding surface (or lip groove 201b) of the main shaft 201. This further increases the effect of pushing the lubricant back to the bearing 202 side.

As described above, in this embodiment, the oil seal 211 and the bearing 202 are disposed at a position where the lubricant scattered from the bearing 202 reaches the sliding surface between the oil seal 211 and the outer peripheral surface of the main shaft 201. Then, when the main shaft 201 rotates, a part of such a lubricant is pushed back to the bearing 202 side. As a result, leakage of the lubricant is suppressed, and an appropriate amount of lubricant is interposed on the sliding surface between the oil seal 211 and the main shaft 201.

Note that such maintenance can also be applied to the outer peripheral surface of the main shaft 201 facing the oil seal 212 disposed on the impeller 230 side in FIG. That is, the operator separates the sliding surface between the oil seal 212 and the outer peripheral surface of the main shaft 201, and the groove is inclined to the impeller 230 side (opposite the bearing 203) from the sliding surface between the oil seal 212 and the main shaft 201. 201c may be formed. The inclination direction of the groove 201c formed in the main shaft 201 facing the oil seal 212 is a direction in which the lubricant on the sliding surface is returned to the bearing 203 side when the main shaft 201 rotates, and the oil seal on the bearing 202 side. This is the opposite of the groove 201 c formed in the main shaft 201 facing to 211.

Further, various oil seals can be applied.
FIG. 13C is an enlarged view when an oil seal 211 ′ different from FIG. 13B is applied. The sealing sleeve 280 is provided as a part of the main shaft 201. The oil seal 211 'includes a resin-made seal lip member 281 having an L-shaped cross section, and the seal lip member 281 includes an outer joint metal ring 282 having a substantially L-shaped cross section and an inner side having a substantially L-shaped cross section. The presser metal ring 283 is clamped. A cylindrical lip 284 is formed on the inner peripheral side of the seal lip member 281. This cylindrical lip 284 corresponds to the lip 211d in FIG. 13B, and seals the fluid to be sealed in close contact with the outer peripheral surface of the sealing sleeve 280. . When the oil seal 211 ′ shown in FIG. 13C is used, the groove 201c is formed in the sealing sleeve 280 that is a part of the main shaft 201.

FIG. 13D is an enlarged view when an oil seal 211 ″ different from that in FIG. 13B is applied. The oil seal 211 ″ has a cylindrical portion 292. Depending on the installation environment, foreign matter such as dust may enter the sliding surface between the oil seal and the outer peripheral surface of the main shaft 201 from the atmosphere side. Therefore, the cylindrical portion 292 prevents foreign matter from entering the oil seal 211 ″. Therefore, the oil seal 211 ″ can reduce the wear of the sliding surface on the lip portion of the oil seal 211 ″ and the outer peripheral surface of the main shaft 201 due to the entry of foreign matter from the atmosphere side.

Hereinafter, the maintenance procedure will be described in detail.
FIG. 14 is a process diagram showing a maintenance procedure of the pump device 301. FIG. 14 is merely an example of a procedure, and each step may be appropriately replaced or omitted. In step S21 of FIG. 14, the maintenance of this embodiment for the pump device 301 of FIG. 11A is started.

First, the operator disconnects from the motor (not shown). (Step S21). Further, the operator removes the plug 216 and removes the lubricant from the bearing body 204 (step S22). Subsequently, the operator removes the bolt 238 for the pump body 232, and removes the intermediate plate 237, the body cover 221 and the bearing body 204 from the pump body 232 (step S23). As a result, the state shown in FIG. 15 is obtained.

Thereafter, the operator removes the nut 231 for the impeller 230 and removes the impeller 230 from the main shaft 201 (step S24). Then, the operator removes the key 219 on the impeller 230 side from the main shaft 201. As a result, the state shown in FIG. 16 is obtained. Further, the operator removes the bolt 36 and removes the intermediate plate 237 and the body cover 221 from the bearing body 204 (step S25). Next, the worker removes the bolt 229 for the gland packing 223 and removes the gland packing 223 (step S26). As a result, the state shown in FIG. 17 is obtained.

And when the draining ring 213 exists, the operator pulls out the draining ring 213 from the main shaft 201 (step S27). Next, the operator removes the

bolts

210a and 210b for the bearing covers 205 and 206, removes the bearing covers 205 and 206 and the oil seals 211 and 212 from the bearing body 204, and removes the main shaft 201 (step S28). As a result, the state shown in FIG. 18 is obtained. In this way, the main shaft 201 is separated from the oil seals 211 and 212. When the operator pulls out the main shaft 201, the operator checks the rotation state of the

bearings

202 and 203, and replaces the

bearings

202 and 203 when smooth rotation is not possible.

Then, the worker forms the groove 201c described with reference to FIGS. 13A and 13B in the vicinity of the

bearings

202 and 203 on the main shaft 201 (step S29). As a result, the state shown in FIG. 19 is obtained. Specifically, the operator forms the groove 201 c by scratching the outer peripheral surface of the main shaft 201. The groove 201c is desirably formed over the entire circumference, but there may be a portion where the groove 201c is not provided in part.

After that, the operator may replace the oil seals 211 and 212 with new ones as necessary, and assemble the pump by the reverse procedure. Accordingly, it can be said that a new pump device (lubricant leakage suppressing pump device) with less lubricant leakage shown in FIG. 20 is manufactured.

As described above, in this embodiment, the maintenance worker leaks the lubricant along the main shaft 201 by a simple method in which the outer peripheral surface of the main shaft 201 is scratched in a predetermined direction to form the groove 201c. Can be suppressed.

It should be noted that, as a maintenance, the operator may provide the groove 201c in advance on the outer peripheral surface of the main shaft 201 of a new pump instead of forming the groove 201c in the main shaft 201. In FIG. 11A, the pump device 301 using a single-stage single-suction centrifugal pump has been described as an example. However, any pump device, in particular, an oil bath type bearing using a lubricant, an oil seal, and a horizontal shaft pump are used. This embodiment can be applied to a horizontal shaft type pump device provided with

The pump device 301 that has been maintained according to the above-described procedure can reduce maintenance work for replenishment or replacement of lubricant due to lubricant leakage. Even when the pressure on the lip 211d is weakened due to aging, the pump device 301 that has been maintained in the above-described procedure ensures the sealing performance by returning the lubricant to the bearing body 204 by the first flow FL1. As a result, the replacement life of the oil seal 211 can be extended. Further, during the pump operation, the lubricant is supplied between the sliding portion of the outer peripheral surface of the lip 211d and the main shaft 201 by the second flow FL2 of the lubricant. Therefore, the sliding surfaces of the oil seal 211 and the main shaft 201 can suppress heat generation and wear due to friction, so that the life of the oil seal 211 and the main shaft 201 can be extended. In FIG. 11, the groove 201 c can also be applied to the outer peripheral surface of the main shaft 201 facing the bearing 203 and the oil seal 212 and the bearing 203 and the oil seal 212 arranged on the impeller 230 side.

21 and 22 are tables showing an example of comparison of lubricant leakage between the pump device of FIG. 11A and the pump device of FIG. The table of FIG. 21 shows the result of the maintenance worker periodically checking for leakage of the lubricant at the time interval TMx at the site where the pump 300 is continuously operated. Therefore, TM0 to TM9 in FIGS. 21 and 22 indicate a period after the operation of the pump devices 310 and 311 is started, and specifically, n times (n) the time interval TMx after the operation of the pump devices 310 and 311 is started. : 0 to 9). In general, the pump apparatus is regularly maintained every year from about 3 months. Hereinafter, for the sake of simplicity, only the oil seal 211 will be described, but the same effect is recognized for the oil seal 212.

Here, the pump device showing the result of lubricant leakage in FIGS. 21 and 22 will be described. The pump device 310 is a pump device in which the groove 201c is not provided on the outer surface of the main shaft 201, and is the pump device 301 shown in FIG. 11A. A pump device 311 in FIG. 21 is the pump device 301 shown in FIG. That is, the pump device 310 is different from the pump device 311 only in that the groove 201 c is not formed on the outer surface of the main shaft 201. Specifically, the pump device 311 is formed by forming an inclined groove 201c on the outer surface of the main shaft 201 of the pump device 310 in accordance with the maintenance procedure of FIG. It was.

Also, the oil seal 211 that is a sealing member of the pump devices 310 and 311 is deteriorated with age, and the lip 11d is hardened due to deterioration over time. Therefore, the oil seal 211 is a consumable part. Even at this site, when a useful life elapses from a new article, it is replaced by a maintenance worker. The lubricant leakage indicates a state where the lubricant leaking from the oil seal 211 to the atmosphere is scattered from the outer surface of the main shaft 201. That is, a state where the lubricant on the atmosphere side is scattered from the main shaft 201 and contaminates the periphery is referred to as “lubricant leakage”.

When the service life of the oil seal 211 is reached, the sealing action is significantly reduced due to the lip 211d of the oil seal 211 being hardened. The service life of the oil seal 211 varies depending on the use environment of the pump device, the lubricant, and the like, but is generally about 2 to 5 years. In the maintenance whose results are shown in FIGS. 21 and 22, the operator determines that the useful life of the oil seal 211 has been reached when the lubricant leaking to the atmosphere side exceeds the allowable leakage amount Mx. The allowable leakage amount Mx varies depending on the installation environment and the operator of the pump device 300, but in general, the maintenance worker attaches the lubricant leaked from the oil seal 211 to the atmosphere side through the support 218 and adheres to the ground. If it is in a state where the scattering of the lubricant from the main shaft 201 is constantly confirmed, it is determined that the allowable leakage amount Mx has been exceeded.

FIG. 21 shows the amount of lubricant leakage for each maintenance cycle.
During the first maintenance, that is, when the oil seal 211 and the main shaft 201 are used during the period TM1, the maintenance worker confirmed a small amount of lubricant leakage (a few drops of traces) with the pump device 310. The lubricant leakage could not be confirmed by the pump device 311.

During the second maintenance, that is, when the oil seal 211 and the main shaft 201 are used for the period TM2, the maintenance operator confirmed a small amount of lubricant leakage (several tens of drops of traces) with the pump device 310. On the other hand, the lubricant leakage could not be confirmed by the pump device 311.

During the fourth maintenance, that is, when the oil seal 211 and the main shaft 201 were used during the period TM4, the maintenance worker confirmed the leakage of the lubricant in both the pump devices 310 and 311. It is considered that this is because the lip 211d is hardened due to aging and the sealing action is lowered. However, the lubricant leakage of the pump device 310 has reached the leakage allowable amount Mx or more, whereas the pump device 311 is smaller than the leakage allowable amount Mx. Accordingly, the maintenance worker determined that the oil seal 211 of the pump device 310 has reached the useful life and replaced it. In addition, as a preventive maintenance, the oil seal 211 was also replaced in the pump device 311 that did not reach the service life.

During the fifth maintenance, that is, when the oil seal 211 after replacement is used for the period TM1 and the main shaft 201 for the period TM5, the maintenance worker leaks a small amount of lubricant with the pump device 310 (a trace of several tens of drops). ) Was confirmed, but the pump device 311 could not confirm lubricant leakage. Here, the pump device 310 confirms a small amount of lubricant leakage in the period TM1 even after the oil seal 211 is replaced in the fourth maintenance. This is considered to be due to the effect of the lip groove 201b formed on the main shaft 201 of the pump device 310.

During the sixth maintenance, that is, when the oil seal 211 after replacement is used for the period TM2 and the main shaft 201 is used for the period TM6, the maintenance worker leaks a small amount of lubricant (several tens of drops of traces) with the pump device 310. ) Was confirmed, but the pump device 311 could not confirm lubricant leakage.

During the seventh maintenance, that is, when the replaced oil seal 211 is used for the period TM3 and the main shaft 201 is used for the period TM7, the maintenance worker confirmed the oil leak with the pump device 310 (a small amount of oil leak). On the other hand, no leakage of lubricant could be confirmed by the pump device 311.

Thus, according to the pump device 311, it is possible to suppress the leakage of the lubricant as compared with the pump device 310.

FIG. 22 is a graph showing the results shown in the table of FIG. 21 as changes in elapsed time. 22A shows a change in the elapsed time of the amount of lubricant leakage of the pump device 310, and FIG. 22B shows a change in the elapsed time of the amount of lubricant leak of the pump device 311. In both FIGS. 22A and 22B, the horizontal axis represents elapsed time, and the vertical axis represents the amount of lubricant leakage. Also, the dotted lines in FIGS. 22A and 22B indicate the leakage allowable amount Mx.

In the period TM3, the pump device 310 has a small amount of lubricant leakage as shown in the region R1 of the graph, whereas the pump device 311 lubricates more than the pump device 310 as shown in the region R2 of the graph. Agent leakage can be suppressed.

In the period T1 after the period TM3 elapses until the period TM4 elapses, the leakage amount of the lubricant in the pump device 310 increases and further exceeds the allowable leakage amount Mx when the period TM4 elapses. The service life of the oil seal 211 at 310 was determined. For this reason, both the pump devices 310 and 311 replace the oil seal 211 after the period TM4 has elapsed from the start of operation. Here, as shown in FIG. 22, in the period T1, the pump device 311 is different from the pump device 310 in that the leakage of lubricant below the allowable leakage amount Mx is confirmed, and the oil seal 211 has not reached its useful life. It can be used continuously after the period TM4. However, the operator replaced the oil seal 211 of the pump device 311 for preventive maintenance. Similarly, in the period T <b> 2 after the period TM <b> 7 elapses until the period TM <b> 8 elapses, both the pump devices 310 and 311 leak lubricant due to the aging deterioration of the oil seal 211, but the pump device 311 has a higher capacity than the pump device 310. Leakage is small.

In the period T3 after the period TM4, it was confirmed that the lip groove 201b was formed in the main shaft 201 by sliding the oil seal 211 with respect to the main shaft 201 in both pump devices 310 and 311.

In the period after the oil seal 211 has been replaced and the period TM4 has elapsed and until the period TM7 has elapsed, the pump device 310 has a small amount of lubricant leakage as shown in a region R3 in the graph of FIG. 311 can suppress the lubricant leakage more than the pump device 310 as indicated by a region R4 in the graph of FIG. Thus, even if the lip groove 201b is formed in the main shaft 201, the pump device 311 can suppress the lubricant leakage more than the pump device 310.

As shown in FIGS. 21 and 22, in periods T1 and T2 in which the oil seal 211 does not normally operate due to aging of the oil seal 211, the mass of the lubricant leaked to the atmosphere in both the pump devices 310 and 311. Therefore, the lubricant is scattered by the centrifugal force generated by the rotation of the main shaft 201. However, when the oil seal 211 operates normally and the amount of leakage is small, the lubricant leaked to the atmosphere side of the pump device 311 increases the contact area with the main shaft 201 by the groove 201c as compared with the pump device 310. It becomes difficult to scatter from the main shaft 201. In addition, the lubricant exposed on the outer peripheral surface of the main shaft 201 on the atmosphere side of the pump device 311 is immediately returned to the sealed fluid side by the first flow FL1 due to the inclined groove 201c. Therefore, as compared with the pump device 310, the pump device 311 can suppress the leakage of the lubricant from the oil seal 211.

Furthermore, as described above, since the pump device 301 is often installed in a pump chamber or the like, the oil pressure is set to about 20% to 80% compared to the pressure of the lip 211d in a general oil seal. In some cases, the lifetime of the

seals

211 and 212 may be increased. Thus, even in the pump device in which the lip 211d is weakly pressed, if the inclined groove 201c is formed in the main shaft 201, the lubricant leaked to the atmosphere side is returned to the sealed fluid side by the first flow FL1, Lubricant leakage can be suppressed. Further, since a small amount of lubricant leakage of about the above-described pump device 310 is often tolerated, a groove 201c inclined to the main shaft 201 by the maintenance method described above with reference to FIG. 14 according to the request from the operator of the pump. May be formed.

As described above, the pump device 301 according to the second embodiment is capable of rotating the main shaft 201 and the main shaft 201 that rotates the impeller 230 that pressurizes the carrier liquid in a predetermined direction by driving the electric motor that is an example of the driving device. And a bearing cover 205 through which the main shaft 201 passes, and a seal member that prevents the lubricant in the bearing 202 from leaking from the sealed fluid side to the atmosphere side through the outer peripheral surface of the main shaft 201. An oil seal 211 is provided. The bearing cover 205 is configured such that the lubricant scattered from the bearing 202 flows through the bearing cover 205 to the oil seal 211. Further, in this pump device 301, an inclined groove 201 c is formed on the outer peripheral surface of the main shaft 201 so that when the main shaft 201 rotates, the lubricant exposed on the outer peripheral surface of the main shaft 201 on the atmosphere side is pushed back to the sealed fluid side. Is provided.

With this configuration, the lubricant scattered from the bearing 202 and flowing through the bearing cover 205 to the oil seal 211 is returned from the atmosphere side to the sealed fluid side by the pumping action by the groove 201c on the outer peripheral surface of the main shaft 201, and the lubricant leakage is prevented. Can be suppressed.

The pump device 301 is a horizontal axis type pump device including a horizontal axis pump 300. With this configuration, the sealed fluid can be sealed by the action of the oil seal 211 while the main shaft 201 is stationary.

In addition, the inclined groove 201c is provided in at least a part of the outer peripheral surface of the main shaft 201 on the atmosphere side. With this configuration, as the main shaft 201 rotates, at least a part of the outer peripheral surface of the main shaft 201 on the atmosphere side generates air in the direction of the bearing 202, and the lubricating oil is pushed in the direction of the bearing 202 by this air. It is. Further, the lubricating oil is returned toward the bearing 202 by the pumping action.

Further, if the seal member is the oil seal 211 incorporated in the bearing cover 205, the lubricant scattered from the bearing 202 is supplied to the oil seal 211 through the bearing cover 205, so that the oil seal 211 and the main shaft 201 are supplied. Since the lubricant is supplied between the oil seal 211 and the main shaft 201, the sliding between the oil seal 211 and the main shaft 201 can be kept good. Further, since the inclined groove 201c is formed, the lubricant exposed on the outer peripheral surface of the main shaft 201 on the atmosphere side is pushed back from the oil seal 211 to the bearing 202 side by the pumping action, so that the lubricant is brought to the atmosphere side. Leakage can be suppressed.

<Third Embodiment>
Next, a third embodiment will be described. FIG. 23 is a longitudinal sectional view showing a partial configuration of a pump device according to a comparative example. FIG. 23 is a longitudinal sectional view showing a configuration of a part of a pump device according to a comparative example, and FIG. 24 is a sectional view at X of the pump device of FIG. A pump device 401 shown in FIG. 23 is different from the pump device 301 shown in FIG. 20 in the shape of a bearing cover 405. Therefore, the same reference numerals are used for components having the same functions as those of the pump device 301 in FIG. As shown in FIG. 24, on the surface of the bearing cover 405 on the main shaft 201 side, the surface below the oil surface of the lubricating oil OL is the bottom surface portion 405b, and the surface facing the bottom surface portion 405b across the axis is the ceiling surface portion 405u, A surface other than the bottom surface portion 405b, the bottom surface portion 405b, and the ceiling surface portion 405u is referred to as a side surface portion 405a. Further, the bearing-side end portion of the ceiling surface portion 405u of the bearing cover 405 is referred to as a bearing-side end portion 405u1, and the end portion on the sealing member side is referred to as a sealing member-side end portion 405u2. In addition, although the cross section of the bearing cover 405 shown in FIG. 24 is substantially circular, it may be polygonal regardless of this.

The bearing cover 405 in the pump device 401 according to this comparative example will be described. The distance Ln1 between the bearing 202 of the bearing cover 405 through which the main shaft 201 passes and the surface of the bearing cover 405 facing the bearing 202 exceeds the distance Ln0 where the lubricant scatters from the bearing 202 during operation of the pump 300. That is, the distance Ln1 is longer than the distance Ln0. And / or, as indicated by a broken line L1 in FIG. 23, if the line connecting the apex from the bearing side end 405u1 to the seal member side end 405u2 of the ceiling surface portion 405u of the bearing cover 405 is substantially horizontal, As indicated by an arrow FLn1 in FIG. 24, the oil droplets Od of the lubricant (here, lubricant oil as an example) splashed from the bearing 402 to the ceiling surface portion 405u is on a plane substantially perpendicular to the inner peripheral axis of the bearing cover 405. Then, it falls to the bottom surface portion 405b or the main shaft 201 of the inner surface of the bearing cover 405. For this reason, the lubricating oil supplied to the oil seal 211 through the bearing cover 405 is remarkably reduced, and furthermore, the lubricating oil is returned to the bearing 402 side by the pumping action of the groove 201c formed on the surface of the main shaft 201. Further, there is a problem that the lubricant on the sliding surface of the main shaft 201 is insufficient, a sound is generated due to friction between the main shaft 201 and the oil seal 211, and the life of the oil seal 211 is shortened due to wear of the lip 211d.

As described above, when heat generated in the bearing 202 in the continuous operation of the pump 300 is transmitted to the lip 211d of the oil seal 211 via the main shaft 201, the lip 211d may be cured and the life of the oil seal 211 may be reduced. Therefore, a predetermined distance (Ln1) is required between the bearing 202 and the oil seal 211. Therefore, the bearing cover according to the third embodiment has a structure on the inner peripheral surface for guiding the lubricant scattered on the bearing cover to the oil seal 211. With this configuration, the lubricant can be supplied to the oil seal 211 even if the distance Ln1 is longer than the distance Ln0 at which the lubricant scatters from the bearing 202. Hereinafter, the bearing cover 505 according to the third embodiment will be specifically described.

FIG. 25 is a longitudinal sectional view showing a configuration of a part of the pump device according to the third embodiment. The pump device 501 shown in FIG. 25 is different from the pump device 401 according to the comparative example of FIG. 23 only in the shape of the bearing cover 505. Therefore, hereinafter, the same functional configuration as that of the pump device 301 in FIG. As shown in FIG. 24, on the surface of the bearing cover 505 on the main shaft 201 side, a portion below the oil surface of the lubricating oil OL is a bottom surface portion 505b, and a surface facing the bottom surface portion 505b across the axis is a ceiling surface portion 505u, A surface other than the bottom surface portion 505b, the bottom surface portion 505b, and the ceiling surface portion 505u is referred to as a side surface portion 505a. Further, the bearing-side end portion of the ceiling surface portion 505u of the bearing cover 505 is referred to as a bearing-side end portion 505u1, and the end portion on the seal member side is referred to as a seal member-side end portion 505u2.

In the pump device 501 according to the third embodiment, the length Lm1 between the bearing 202 and the surface of the bearing cover 505 facing the bearing 202 through which the main shaft 201 passes exceeds the distance Lm0 that the lubricant fly from the bearing 202. ing. As shown by a broken line L2 in FIG. 24A, in the pump device 501, as a structure for guiding the lubricant to the oil seal 211, a surface including at least a part of the ceiling surface portion 505u of the inner peripheral surface of the bearing cover 505. Is inclined so as to approach the main shaft 201 as the oil seal 211 is approached. Specifically, the inner peripheral surface of the bearing cover 505 is inclined at an angle θm from the broken line L1 that is a horizontal plane from the bearing-side end portion 505u1 to the seal member-side end portion 505u2, and the bearing cover 505 is The inner diameter on the oil seal 211 side is smaller than the inner diameter on the bearing 202 side. That is, with this configuration, the bearing cover 505 forms a flow indicated by an arrow FLm1 in FIG. 25 (second flow FL2), and the groove 201c seals the lubricant leaked to the atmosphere side of the outer peripheral surface of the main shaft 201. A first flow FL1 returning to the fluid side is formed. As a result, the lubricant is supplied to the oil seal 211 along the inclination of the inner peripheral surface of the oil seal 211, so that the lubricant is supplied to the sliding surfaces of the oil seal 211 and the main shaft 201, and the pumping of the groove 201c is performed. By the action, the lubricant is returned to the sealed fluid side.

Note that the angle θm described above depends on the amount and viscosity of the lubricant to be scattered, and further on the distance Lm1. Further, if the distance Lm1 is long, the lubricant is likely to fall before reaching the seal member side end 505u2, and therefore the distance Lm1 and the angle θm are preferably proportional.

<Fourth Embodiment>
Next, a fourth embodiment will be described. FIG. 26 is a longitudinal sectional view showing a partial configuration of the pump device according to the fourth embodiment. As shown in FIG. 26, the pump device 601 according to the fourth embodiment further includes a deflector member 640 as compared with the pump device 401 according to the comparative example of FIG. Accordingly, the same components as those of the pump device 401 are denoted by the same reference numerals, and description thereof is omitted. The deflector member 640 is disposed between the bearing 202 and the oil seal 211 and is attached to the main shaft 201. The deflector member 640 is a draining collar and shakes off the liquid flowing along the rotating main shaft 201.

According to this configuration, as shown by the arrow in FIG. 26, when the lubricant scattered from the bearing 202 does not reach the oil seal 211 through the bearing cover 405 and falls on the main shaft 201, the deflector member 640 falls. The lubricant is again blown to the bearing cover 405 by centrifugal force. The skipped lubricant is supplied to the oil seal 211 via the bearing cover 405. Thereby, the lubricant is supplied to the sliding surfaces of the oil seal 211 and the main shaft 201. This lubricant is returned to the bearing 202 side by the pumping action of the groove 201 c formed on the surface of the main shaft 201. Part of the lubricant returned to the bearing 202 side by the pumping action of the groove 201c is blown to the bearing cover 405 by the deflector member 640, whereby the lubricant is supplied to the sliding surfaces of the oil seal 211 and the main shaft 201. .

In the fourth embodiment, a bearing cover 205, a bearing cover 505, or a bearing cover 705 described later may be used instead of the bearing cover 405.

<Fifth Embodiment>
Next, a fifth embodiment will be described. FIG. 27 is a cross-sectional view showing a partial configuration of the pump device according to the fifth embodiment. 28 is a cross-sectional view of arrow A in the pump device of FIG. As shown in FIGS. 27 and 28, the pump device 701 according to the fifth embodiment further includes a guide member 750 constituting a part of the bearing cover 705, as compared with the pump device 401 according to the comparative example of FIG. Prepare. Therefore, the same components as those of the pump device 401 are denoted by the same reference numerals, and a part of the description is omitted.

The bearing cover 705 includes a bearing cover main body 710 and a guide member 750 that guides the lubricant scattered from the bearing 202 to the oil seal 211. The bearing cover body 710 has the same shape as the bearing cover 405. The guide member 750 has a structure for guiding the lubricant to the oil seal 211, and the configuration of the bearing cover 705 forms a second flow FL 2 for guiding the lubricant scattered from the bearing 202 to the oil seal 211. Can do.

As shown in FIG. 28, the bearing cover 705 is a protruding guide member having a width W extending along the major axis direction of the main shaft 201 on the inner peripheral surface including the uppermost portion of the inner peripheral surface of the bearing cover main body 710. 27, and a surface 750u of the guide member 750 facing the main shaft 201 as shown in FIG. 27 approaches the main shaft 210 as it approaches the oil seal 211 along the major axis direction of the main shaft 210 from the bearing 202 side. It is inclined to.
With this configuration, the lubricant flows along the slope of the surface 750 u facing the main shaft 201 of the guide member 750, so that the lubricant can be supplied to the oil seal 211. Further, since the space S can be made wider than that of the pump device 501, an increase in temperature in the space S can be suppressed, leading to a longer life of the oil seal 211.

<Modification 1>
Subsequently, Modification 1 of the fifth embodiment will be described. FIG. 29 is a cross-sectional view of arrow A in the pump device of FIG. 27 in the pump device according to Modification 1 of the fifth embodiment. 30 is a cross-sectional view taken along the line BB ′ of FIG.

As shown in FIG. 29, the bearing cover 705 is provided with a protrusion-shaped guide member 750 a having a thickness H extending in the major axis direction of the main shaft 201 from the bearing 202 side to the oil seal 211 on the inner peripheral surface of the bearing cover main body 710. ing. As shown in FIG. 30, the pair of guide members 750a are arranged so as to extend substantially horizontally in a vertical cross section (for example, a BB ′ cross section shown in FIG. 30) parallel to the long axis direction and including the guide member 750a. Yes.

With this configuration, the lubricant scattered from the bearing 202 adheres to the upper surface of the inner peripheral surface of the bearing cover main body 710, and then falls on the guide member 750a along the inner peripheral surface of the bearing cover main body 710 in the circumferential direction ( (Second flow FL2 in FIG. 29). The lubricant that has fallen on the guide member 750a moves along the guide member 750a to the oil seal 211 due to inertia (second flow FL2 in FIG. 30). In such a second flow FL2, the lubricant can be supplied to the oil seal 211. In the present embodiment, the guide member 750a is provided at a position including a horizontal plane passing through the axis on the inner peripheral surface of the bearing cover main body 710, but the upper surface of the guide member 750a is on the inner peripheral surface of the bearing cover main body 710. You may be provided in the position above the horizontal surface which passes along an axis. Thereby, the guide member 750 a can supply more lubricant to the oil seal 211 than the guide member 750. In addition, the upper surface of the guide member 750a should just be provided in the position above the position where the height is the lowest among the sliding surfaces of the oil seal 211 and the main shaft 201. Thus, the lubricant can be supplied to the sliding surfaces of the oil seal 211 and the main shaft 201 after the lubricant has flowed on the upper surface of the guide member 750a.

<Modification 2>
Subsequently, Modification 2 of the fifth embodiment will be described. FIG. 31 is a cross-sectional view taken along arrow A in the pump device of FIG. 27 in the pump device according to Modification 2 of the fifth embodiment. 32 is a cross-sectional view taken along the line CC ′ of FIG.

31, a protrusion-shaped guide member 750c having a thickness H extending from the bearing 202 side to the oil seal 211 in the major axis direction of the main shaft 201 is provided on the inner peripheral surface of the bearing cover main body 710. Further, as shown in FIG. 32, the pair of guide members 750c is parallel to the major axis direction of the main shaft 201 and includes a vertical cross section including the guide member 750c (for example, the CC ′ cross section shown in FIG. 32). As it approaches the oil seal 211 along the major axis direction of the main shaft 201, it is inclined downward.

With this configuration, the lubricant scattered from the bearing 202 adheres to the upper surface of the inner peripheral surface of the bearing cover main body 710, and then falls on the guide member 750c along the inner peripheral surface of the bearing cover main body 710 in the circumferential direction. The lubricant that has fallen on the guide member 750c moves along the guide member 750c to the oil seal 211 in accordance with the inclination provided on the guide member 750c. In this way, the lubricant can be supplied to the oil seal 211.
In this embodiment, as shown in FIG. 32, the guide member 750c is provided below the horizontal plane passing through the axis on the inner peripheral surface of the bearing cover main body 710, but the lower end of the guide member 750c (on the oil seal 211 side). The upper surface of the end portion may be provided above the oil seal 211. Thus, the guide member 750c can supply the lubricant to the oil seal 211 more quickly than the guide member 750a. The upper surface of the lower end (the end portion on the oil seal 211 side) of the guide member 750c only needs to be provided at a position above the lowest position among the sliding surfaces of the oil seal 211 and the main shaft 201. Thus, the lubricant can be supplied to the sliding surfaces of the oil seal 211 and the main shaft 201 after the lubricant has flowed on the upper surface of the guide member 750c.

Further, although the

guide members

750a and 750c form a pair, only one of them may be provided, or three or more guide members may be provided in the bearing cover main body 710. When there are a plurality of

guide members

750a or 750c, they may have different shapes. Further, the guide member 750, the guide member 750a, and the guide member 750c may be combined.

Further, according to the third to fifth embodiments described above, the maintenance procedure shown in FIG. 14 can be used to suppress lubricant leakage in the pump device of the prior art without any difference from the conventional procedure. . Specifically, as an example, after removing the bearing cover 205 in step 28 of FIG. 14, a groove 201c is formed in the main shaft 201 in step S29. Thereafter, the bearing cover 405 is attached, and thereafter, the pump device may be assembled by a normal procedure. Thus, by forming the groove 201c in the main shaft 201 and attaching the bearing cover 405 instead of the bearing cover 205, it is possible to suppress the leakage of lubricating oil at the installation site of the pump device. A deflector member 640 may be further provided between the bearing 202 and the seal member of the pump device according to the third and fifth embodiments.

<Sixth Embodiment>
Next, a sixth embodiment will be described. The pump device according to the sixth embodiment is provided with an enclosure member for detecting leakage of the lubricant from the oil seal. FIG. 33 is a schematic diagram illustrating a schematic configuration of a pump device according to a sixth embodiment. As shown in FIG. 33, the pump device 801 according to the sixth embodiment includes a pump 800 and an electric motor 860 having a rotary shaft 861 coupled to the main shaft 820 of the pump 800 via a coupling. Here, the configuration of the pump 800 is the same as that of the pump 300 according to the second embodiment, and thus detailed description thereof is omitted. Furthermore, the pump device 801 communicates with the pump 800 and passes a suction pipe 830 through which water sucked from the water tank passes, and a discharge pipe 840 communicates with the pump 830 and passes water discharged from the pump 800. With. The pump device 801 further includes an enclosure member 870 and a base 880 that supports the pump 800, the enclosure member 870, and the electric motor 860.

34 is a cross-sectional view taken along the line DD of FIG. As shown in FIG. 34, the main shaft 820 is covered with an oil seal 811 in a cross section substantially perpendicular to the major axis of the main shaft 820, and the oil seal 811 is covered with a bearing cover 805. Further, the bearing cover 805 is covered with an enclosing member 870 with a space therebetween. As a result, when the lubricant leaked from the oil seal 811 to the atmosphere is scattered by the rotation of the main shaft 820, the scattered lubricant adheres to the inner surface of the enclosure member. Thereby, by observing the inner surface of the enclosure member, an inspector who checks the leakage of the lubricant in the oil seal 811 can check the amount of lubricant scattered from the oil seal 811. For example, the lubricant leakage shown in FIGS. 21 and 22 is equal to the lubricant adhered to the inner surface of the enclosure member.

The above-described embodiments and modifications can be applied to the oil seal 211 ′ or the oil seal 211 ″ instead of the oil seals 211 and 212 as a seal member. Further, in the above-described embodiments and modifications, as an example of a seal member that seals between the main shaft 201 and the bearing cover 205 that are concentrically arranged inside and outside in the radial direction, the oil seals 211 and 212 are replaced by non-contact. Seal can be applied.

<Seventh Embodiment>
FIG. 35 is a cross-sectional view showing a partial configuration of the pump device according to the seventh embodiment. The same components as those in FIG. 20 are denoted by the same reference numerals and description thereof is omitted. A seal member 511b shown in FIG. 35 is a labyrinth seal which is a kind of non-contact seal. Specifically,

labyrinth grooves

541 and 542 called labyrinths are provided in a through portion of the main shaft 201 of the bearing cover 205, that is, a flange surface 540 facing the outer peripheral surface of the main shaft 201 in the bearing cover 205. The seal member 511b includes a flange surface 540 and

labyrinth grooves

541 and 542. According to the labyrinth groove structure, the lubricant that has entered the gap between the flange surface 540 and the main shaft 201 through the side surface of the bearing cover 205 stays in the

labyrinth grooves

541 and 542 due to the surface tension of the lubricant, and the labyrinth groove Guided downward along 541 and 542.

In the present embodiment, the gap between the flange surface 540 and the outer peripheral surface of the main shaft 201 is divided into an atmosphere side on the main shaft end 220 side and a sealed fluid side on the bearing 202 side. Also in the pump device of this embodiment, if the inclined groove 201c is formed in the main shaft 201, the lubricant on the main shaft 201 is returned to the sealed fluid side by the first flow FL1, and the lubricant leakage can be suppressed.

This groove 201c may be formed in a region adjacent to the atmosphere side with respect to a region facing the flange surface 540 of at least the outer peripheral surface of the main shaft 201 (region A1 in FIG. 35). Further, the inclined groove 201c may be provided in a region (region B1 in FIG. 35) facing the flange surface 540 in the outer peripheral surface of the main shaft 201. Furthermore, the inclined groove 201c may be provided in at least a part of a region on the sealed fluid side (region C1 in FIG. 35) of the outer peripheral surface of the main shaft 201. That is, the groove 201c is formed in at least a part on the atmosphere side adjacent to the facing surface of the flange surface 540 on the outer peripheral surface of the main shaft 201, and may further extend to the sealed fluid side. Thereby, like the structure using the oil seal for the seal member, leakage of the lubricant can be suppressed.

Thus, if the inclined groove 201c is formed in the main shaft 201 regardless of the type of the seal member, the lubricant supplied to the seal member by the second flow FL2 leaks to the atmosphere side. By returning to the sealed fluid side by the flow FL1, leakage of the lubricant can be suppressed. Therefore, it can be applied to various pump devices.

Here, the inclined groove formed on the main shaft according to the embodiment and the modification described above will be described. Hereinafter, as an example, the pump device 301 illustrated in FIG. 11A is referred to as a pump device 310, and the pump device 301 illustrated in FIG. 20 is referred to as a pump device 311.

The groove 201c is inclined so that when the pump 300 is operated and the main shaft 201 rotates, the lubricant exposed on the outer peripheral surface of the main shaft 201 on the atmosphere side is returned to the sealed fluid side. That is, the groove 201c is inclined so that the lubricant on the outer peripheral surface of the main shaft 201 is returned from the atmosphere side to the sealed fluid side when the pump 300 is operated and the main shaft 201 rotates. Specifically, when the main shaft 201 rotates in the clockwise direction when viewed from the motor side, the inclined groove 201c is a fluid to be sealed from the atmosphere side on the right side surface viewed from the motor side (main shaft end 220 side). It is a plurality of linear irregularities inclined in the direction of increasing toward the side. Here, in the sliding portion (the pressure contact surface between the lip 212d and the outer peripheral surface of the main shaft 201) between the outer peripheral surface of the main shaft 201 and the oil seal 212, the space on the bearing 203 side is the sealed fluid side and the impeller 30 side. Is the atmosphere side. And it provides in at least one part of the area | region adjacent to the atmosphere side with respect to the area | region which opposes a sealing member among the outer peripheral surfaces of the main axis | shaft 201. FIG. Furthermore, the inclined groove 201c may extend from the atmosphere side to the sealed fluid side of the outer peripheral surface of the main shaft 201.

The linear irregularities of the groove 201c are a plurality of linear irregularities that are substantially parallel to each other, and the linear irregularities include lines that are slightly curved or broken in the process of formation. Further, the plurality of linear irregularities of the groove 201c are formed at a predetermined interval, and the predetermined interval is, for example, about 10 μm to 500 μm, and different intervals may be mixed evenly.

The surface roughness of the main shaft 201 in which the groove 201c of the pump device 311 is formed may be equal to or greater than the surface roughness of the sliding surface with the oil seal 211 of the main shaft 201 of the pump device 310. For example, one of the maximum height roughness Rz and the centerline average roughness Ra in the surface roughness of the main shaft 201 in which the groove 201c of the pump device 311 is formed is equal to the oil seal 211 of the main shaft 201 of the pump device 310. The sliding surface is preferably equal to or greater than the sliding surface. However, when the surface roughness of the main shaft 201 is increased, the wear of the lip 11d is accelerated. Therefore, the maximum height roughness Rz of the main shaft 201 in which the groove 201c of the pump device 311 is formed is preferably 0.8 μmRz to 200 μmRz. The center line average roughness Ra of the main shaft 201 in which the groove 201c of the pump device 310 is formed is preferably 0.1 μmRa to 50 μmRa.

Thus, the groove 201c is fine, and the lubricant that has flowed to the seal member by the second flow FL2 during operation of the pump 300 forms an oil surface that covers the plurality of irregularities of the groove 201c. As a result, the contact area between the main shaft 201 and the lubricant increases, and the lubricant leaking from the seal member to the atmosphere side can be prevented from scattering from the main shaft 201. Further, the lubricant on the main shaft 201 can be prevented from returning to the sealed fluid side and leaking to the atmosphere side by the pumping action of the groove 201c.

Generally, the main shaft 201 on which the oil seal 211 slides is finished by a processing method using a finishing tool such as a grinder and not feeding (that is, not moving the finishing tool in the axial direction). And it is said that it is preferable that the line direction which is the finishing processing flaw is substantially perpendicular to the axis. The operator forms a groove 201c in which the processing flaw is inclined with respect to the axis in the maintenance procedure described above on the main shaft 201 of the pump device 310 finished so that the processing flaw is almost perpendicular to the axis. Also good. At this time, the operator may perform finishing using a finishing tool equivalent to the main shaft 201 of the pump device 310 while feeding (that is, moving the finishing tool in the axial direction).

The above description of surface roughness (maximum height roughness Rz, centerline average roughness Ra) conforms to JISB0601: 2001. The surface roughness of the main shaft 201 in which the groove 201c of the pump device 310 is formed indicates the surface roughness in a cross section perpendicular to the stripe direction of the groove 201c.

Patent Document 5 discloses that when the surface roughness of the shaft 201 is 2.5 μm or more, it causes leakage at rest. On the other hand, in the pump device 311 according to the embodiment of the present invention, the height of the oil surface OL of the lubricant when the pump 300 is stopped is lower than the sliding surface of the oil seal 211 and the main shaft 201. When the lubricant is grease, the grease is cooled and solidified while the rotating shaft 201 is stationary, and the oil surface of the lubricant does not exist. Therefore, the liquefied grease does not act on the sliding surfaces of the oil seal 211 and the main shaft 201. Hereinafter, when the lubricating oil or the liquefied grease is referred to as a sealed fluid, the horizontal axis pump device 311 including the horizontal axis pump 300 is compared with that during the operation of forming the second flow FL2. During the stop, the sealed fluid does not act in the direction of leaking to the atmosphere side. Therefore, while the rotary shaft 201 is stationary, the horizontal shaft-type pump device 311 is operated by the seal member (pressing the lip 211d or flowing down by the labyrinth grooves 541 and 542) regardless of the surface roughness of the main shaft 201. Can be easily sealed. Therefore, compared with the groove of the rotating shaft described in Patent Document 5, the groove 201c of the pump device 310 has a wider range of tolerances for surface roughness and processing accuracy. Furthermore, the processing method for the main shaft 201 for forming the groove 201c and the allowable range of the finishing tool are widened.

Further, in Patent Document 2, if the lead angle θ, which is the angle between the sliding surface and the line direction of the groove 201c, is set in the range of 10 to 30 ° and the lead angle θ is too large, the pump action is too strong and the seal There is a description that the amount of oil that flows out and is retained is insufficient. In the above-described embodiment and modification of the present invention, the lubricant can be supplied to the oil seal 211 along the space S side surface of the bearing cover 205 by the action of the second flow FL2, so that the lead angle θ is By being too large, the lubricant on the sliding surface of the oil seal 211 will not be insufficient. For example, it may be 10 ° to 80 °. Here, if the lead angle θ is about 45 °, the operator who finishes the main shaft 201 can easily recognize the target of inclination, so that workability is improved.

The pump 300 may be operated using variable speed means. In the pump device 311, the amount of lubricant scattered from the bearing 202 and the amount of lubricant returned in the groove 201c are both proportional to the rotational speed. For example, when the rotation speed of the main shaft 201 is reduced to 50% of the normal speed, the amount of lubricant scattered from the bearing 202 decreases and the second flow FL2 for supplying the lubricant to the seal member decreases. Since the pumping action is reduced and the first flow FL1 is also reduced, the shortage of the lubricant and the leakage of the lubricant in the oil seal 211 can be suppressed. Therefore, the pump device 311 can also be used for an automatic water supply pump or the like that performs variable speed operation. In addition, even in the main shaft 201 having worn out such as the lip groove 201b, it is possible to prevent the lubricating oil from leaking from the oil seal 211 to the air side by providing the groove 201c on the air side of the surface of the main shaft 201. Further, the embodiments and modifications described for the bearing cover 205 and the oil seal 211 may be implemented in the bearing cover 206 and the oil seal 212, and the embodiments and modifications described in the pump device 301 are pump devices. 101 is also applicable.

Each embodiment described above is described for the purpose of enabling the person having ordinary knowledge in the technical field to which the present invention belongs to implement the present invention. Various modifications of the above embodiment can be naturally made by those skilled in the art, and the technical idea of the present invention can be applied to other embodiments. Therefore, the present invention should not be limited to the described embodiments, but should be the widest scope according to the technical idea defined by the claims.

The present invention can be used for a pump device and a maintenance method of the pump device.

1 Main shaft 1b Lip groove 1c Groove 2, 3 Bearing 4

Bearing body

5, 6

Bearing cover

11, 12 Oil seal 13 Drain ring 21 Body cover 23 Ground packing 30 Impeller 32 Pump body 201 Main shaft 201b Lip groove 201c Groove 202, 203 Bearing 204

Bearing body

205, 206

Bearing cover

211, 212 Oil seal 213 Draining ring 221 Body cover 223 Gland packing 230 Impeller 232 Pump body 300 Pump

Claims

A main shaft that rotates in a predetermined direction an impeller that pressurizes the carrier liquid by driving a driving machine;
A bearing that rotatably supports the main shaft;
A bearing cover through which the main shaft passes;
A seal member for preventing the lubricant of the bearing from leaking from the sealed fluid side to the atmosphere side along the outer peripheral surface of the main shaft;
With
The bearing cover is configured such that the lubricant scattered from the bearing flows through the bearing cover to the seal member.
The outer peripheral surface of the main shaft is provided with an inclined groove so that when the main shaft rotates, the lubricant on the outer peripheral surface of the main shaft is returned from the atmosphere side to the sealed fluid side.
Pump device.
The pump device is a horizontal shaft type pump device,
The pump device according to claim 1.
3. The pump device according to claim 1, wherein the inclined groove is provided in at least a part of a region adjacent to the atmosphere side with respect to a region facing the seal member on an outer peripheral surface of the main shaft. .
The pump device according to claim 3, wherein the inclined groove extends from the atmosphere side to the sealed fluid side in the outer peripheral surface of the main shaft.
5. The pump device according to claim 1, wherein an oil level of the lubricant is a liquid level below the main shaft when the main shaft is stationary. 6.
The seal member is an oil seal incorporated in the bearing cover,
The said bearing cover is comprised so that the said lubricant scattered from the said bearing may be supplied between the sliding part of the outer peripheral surface of an oil seal and the said main shaft via the said bearing cover. The pump device according to item 1.
The pump device according to claim 6, wherein the inclined groove is provided in at least a part of the atmosphere side contacting between the oil seal and the sliding portion of the outer peripheral surface of the main shaft.
The pump device according to claim 6 or 7, wherein the inclined groove is provided in a sliding portion between an outer peripheral surface of the oil seal and the main shaft.
The pump device according to any one of claims 6 to 8, wherein the inclined groove is provided in at least a part of the outer peripheral surface of the main shaft on the sealed fluid side.
The pump device according to any one of claims 1 to 9, wherein the bearing cover has a structure in which a lubricant scattered on the bearing cover is guided to the seal member on a surface on the bearing side.
As a structure for guiding the lubricant to the seal member, the surface including at least the ceiling surface portion of the inner peripheral surface of the bearing cover is moved toward the main shaft as it approaches the seal member along the major axis direction of the main shaft. The pump device according to claim 10, which is inclined so as to approach.
The pump according to claim 10, wherein the bearing cover includes a bearing cover main body and a guide member that guides the lubricant scattered from the bearing to the seal member as a structure that guides the lubricant to the seal member. apparatus.
The guide member is provided on the inner peripheral surface including the uppermost part of the inner peripheral surface of the bearing cover body, and has a protrusion shape extending to the seal member along the major axis direction of the main shaft,
The pump device according to claim 12, wherein a surface of the guide member facing the main shaft is inclined so as to approach the main shaft as the seal member is approached along a major axis direction of the main shaft.
The guide member is provided on an inner peripheral surface of the bearing cover main body, has a protrusion shape extending to the seal member along the major axis direction of the main shaft, and is parallel to the major axis direction of the main shaft and The pump device according to claim 12, wherein the pump device is arranged substantially horizontally in a vertical section including the guide member.
The guide member is provided on an inner peripheral surface of the bearing cover main body, has a protrusion shape extending to the seal member along the major axis direction of the main shaft, and is parallel to the major axis direction of the main shaft and The pump device according to claim 12, wherein a vertical section including the guide member is inclined downward as approaching the seal member along a major axis direction of the main shaft.
16. The structure according to claim 10, further comprising a deflector member attached to the main shaft at a position between the bearing and the seal member as a structure for guiding the lubricant to the seal member. Pump device.
The pump device according to any one of claims 1 to 16, wherein the pump device includes variable speed means, and the drive unit is driven by the variable speed means.
A main shaft for rotating an impeller that pressurizes the conveying liquid by driving a driving device in a predetermined direction, a bearing that rotatably supports the main shaft, a bearing cover through which the main shaft passes, and lubrication of the bearing And a seal member for preventing the agent from leaking from the sealed fluid side to the atmosphere side along the outer peripheral surface of the main shaft, and the bearing cover has the lubricant scattered from the bearing covered the bearing cover. A maintenance method for a pump device configured to flow through the seal member,
Separating the seal member sliding with the outer peripheral surface of the main shaft from the sliding surface of the main shaft with the seal member;
Forming an inclined groove on the outer peripheral surface of the main shaft so that the lubricant exposed on the outer peripheral surface of the main shaft on the atmosphere side is pushed back to the sealed fluid side when the main shaft rotates;
Attaching a seal member to the main shaft;
The maintenance method of the pump apparatus which has this.