JP2007211753A - Submersible pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a submersible pump excellent in durability maintaining constant operation accuracy for a long period of time by preventing damage to a rolling bearing and a mechanical seal. <P>SOLUTION: This submersible pump has a motor part M, a pump part P and a mechanical seal chamber S provided between the motor part and the pump part erectly provided in a vertical direction. The rolling bearing provided in a side near to the mechanical seal chamber is provided with an annular slinger 20 preventing intrusion of foreign matter into the bearing and the mechanical seal chamber. The slinger includes a base end part 20a for fixing the slinger on a rotation wheel 6a, a surface part 20b continuing to the base end part and extending in a direction crossing between the bearing and the mechanical seal 18, and a wall part 20c continuing to the surface part and extending at predetermined bend angle α of not less than 90 degrees and not more than 180 degrees in an external direction of the bearing with keeping a predetermined interval between opposing bearing stationary rings 6b. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to, for example, extending the life of a submersible pump used for raw water transfer in a septic tank, miscellaneous drainage, wastewater drainage, and the like.

Conventionally, as an example of the submersible pump used for such various purposes, for example, a submersible pump configured as shown in FIG. 10 is known.
The submersible pump has a vertical shaft structure in which the main shaft 2 extends in the vertical direction. The main shaft 2 is the same as the two rolling bearings 6 and 8 (the lower bearing (lower bearing 6) in FIG. 10). The upper bearing (upper bearing 8) in the figure is rotatably supported. An impeller 10 having a plurality of blades 12 is attached to one end side (lower side in FIG. 10) of the main shaft 2 and an electric motor (motor) 4 is provided between the two rolling bearings 6 and 8. It is arranged. The motor 4 is provided with a rotor 4a fixed to the main shaft 2 and a stator 4b fixed to the frame 14, for example, between the stator 4b and the rotor 4a when current is supplied to the stator 4b. The motor 4 can rotate the main shaft 2 by magnetic interaction. Thereby, the submersible pump can circulate while circulating the liquid (for example, various waste water etc.) in the pump part P, when the several blade | wing 12 of the impeller 10 attached to the main shaft 2 rotates. . In this case, the two rolling bearings 6 and 8 and the motor 4 (the rotor 4a and the stator 4b) are accommodated in the motor part M, and the impeller 10 is accommodated in the pump part P.

  In addition, the submersible pump is provided with a mechanical seal chamber S between the motor part M and the pump part P. Inside the mechanical seal chamber S, a mechanical seal 18 for keeping the motor part M airtight is disposed. Thereby, for example, the liquid (for example, various drainage etc.) pumped from the pump part P is prevented from entering the motor part M, so that the motor part M can be kept airtight. In this case, the mechanical seal 18 has sliding portions (sliding surfaces) (two in total) at both ends (upper and lower ends in FIG. 10), and each sliding surface is formed by one coil spring (not shown). A so-called monocoil double seal type seal that applies surface pressure is applied, and the mechanical seal (monocoil double seal) 18 is externally fitted to the main shaft 2. Further, inside the mechanical seal chamber S, a lubricating liquid for lubricating and cooling the sliding surface of the mechanical seal 18 is enclosed.

  Since such a submersible pump is used in water, there is a possibility that liquid (for example, various kinds of drainage) may enter the pump from the outside. For example, when foreign matters contained in various types of drainage enter the sliding portion of the mechanical seal 18, a slight gap is generated in the sliding portion, and the lubricating liquid enclosed in the mechanical seal chamber S leaks and the motor is leaked. There is a case of entering the part M. In addition, for example, a slight gap may be generated in the sliding portion of the mechanical seal 18 depending on how the mechanical seal 18 is fitted (assembled) to the main shaft 2, and the lubricating liquid may enter the motor portion M in the same manner. . In this case, for example, when the leaked lubricating liquid enters the inside of the lower bearing 6, the lubricant (for example, grease) sealed in the lower bearing 6 is softened, and the grease is removed from the bearing to the outside of the bearing. There is a risk of leakage (outflow).

When grease leaks (outflows) from the inside of the lower bearing 6 in this way, the amount of grease in the bearing decreases, and the lower bearing 6 becomes insufficiently lubricated. For example, the raceway surface of the bearing ring and the rolling element The rolling contact surface may be damaged (weared) by friction. Further, when the above-described foreign matter enters the inside of the lower bearing 6 together with the lubricating liquid leaked from the mechanical seal chamber S, for example, the foreign matter is caught between the raceway surface of the bearing ring and the rolling surface of the rolling element. In rare cases, abnormal noise may be generated from the lower bearing 6. As a result, in any case, the lower bearing 6 cannot be used with a constant rotational accuracy over a long period of time.
Further, when grease that leaks (outflows) from the inside of the lower bearing 6 enters the sliding portion of the mechanical seal 18, for example, the sliding portion is rubbed due to poor lubrication, and the mechanical seal 18 generates heat. An abnormality may occur.

  As a measure for solving such a problem, for example, Patent Document 1 discloses that the lubricating liquid leaked from the upper sliding portion (sliding surface) of the mechanical seal to the lower bearing side enters the bearing. An example of such a configuration is a submersible pump that discharges without leakage, and a storage section that stores the leaked (discharged) lubricating liquid below the lower bearing (in the mechanical seal direction). It is disclosed as. Further, for example, in Patent Document 2, a reservoir portion of grease that has flowed out from the lower bearing is formed between the lower bearing and the mechanical seal, and the grease directly contacts the sliding portion (sliding surface) of the mechanical seal. A configuration of a submersible pump that is prevented from flowing out is disclosed as an example.

Such a reservoir or reservoir, for example, the lubricating liquid leaked from the mechanical seal chamber and the grease flowing out from the lower bearing are transmitted to the frame side of the submersible pump (for example, the lower bearing outer ring side or the housing side). When flowing, there is an effect of preventing the lubricant from entering the bearing and preventing the grease from entering the sliding portion (sliding surface) of the mechanical seal. However, the lubricating fluid leaking from the mechanical seal chamber and the grease flowing out of the bearing may flow along the main shaft of the submersible pump. In such a case, simply forming the above-described reservoir or reservoir. Therefore, the effect of preventing the lubricating liquid from entering the lower bearing and the grease from entering the sliding portion (sliding surface) of the mechanical seal is diminished.
JP 2003-227490 A Japanese Patent No. 3578585

  The present invention has been made in order to solve such a problem, and its purpose is to prevent damage to the rolling bearing and the mechanical seal, and thus has excellent durability for maintaining a constant operation accuracy over a long period of time. It is to provide a submersible pump.

  In order to achieve such an object, a submersible pump according to the present invention includes an electric motor that rotates a main shaft extending in a vertical direction, and a motor unit that houses a plurality of rolling bearings that rotatably support the main shaft. A mechanical seal chamber provided between a pump unit containing an impeller attached to the lower end side of the main shaft and a motor unit and the pump unit, and provided with a mechanical seal for keeping the motor unit airtight Are erected vertically. In such a submersible pump, the rolling bearing disposed near the mechanical seal chamber is provided with an annular slinger for preventing foreign matter from entering the interior of the bearing and the mechanical seal chamber. . In this case, the slinger includes a base end portion for fixing the slinger to the rotating wheel, a surface portion continuously extending from the base end portion and extending in a direction crossing between the rolling bearing and the mechanical seal, and the surface portion. And a wall portion extending at a predetermined bending angle of 90 degrees or more and 180 degrees or less in the external direction of the bearing with a predetermined interval between the stationary ring of the opposing rolling bearing. Yes.

  In addition, an annular sealing plate for sealing the inside of the bearing is interposed between the stationary ring and the rotating ring of the rolling bearing so as to face the slinger. The inner diameter portion is fixed to the stationary wheel, and the inner diameter portion thereof is in contact with at least one of the inner circumferential surface and the outer circumferential surface of the seal groove formed continuously along the circumferential direction on the surface of the rotating wheel facing the stationary wheel. Further, the sealing plate is provided with a convex portion that protrudes toward the slinger and comes into contact with the slinger on the surface facing the slinger.

  ADVANTAGE OF THE INVENTION According to this invention, the submersible pump excellent in durability which maintains a fixed driving | operation precision over a long period can be provided by preventing damage to a rolling bearing and a mechanical seal.

Hereinafter, submersible pumps according to embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 (a) shows a submersible pump according to a first embodiment of the present invention. The submersible pump has a vertical shaft structure in which a main shaft 2 extends in the vertical direction. 2 includes a motor part M, a pump part P, and a mechanical seal chamber S inserted therein. The motor unit M, the pump unit P, and the mechanical seal chamber S are erected in the order of the pump unit P, the mechanical seal chamber S, and the motor unit M from the lower side of the submersible pump.
In the configuration shown in FIG. 1A, the motor M accommodates an electric motor (motor) 4 that rotates the main shaft 2 and a plurality (two) of rolling bearings 6 and 8 that rotatably support the main shaft 2. Has been. In this case, the two rolling bearings 6 and 8 are arranged so as to sandwich the motor 4 from both sides in the extending direction of the main shaft 2 (vertical direction in FIG. 1A), and the rolling bearing (lower bearing). 6 is positioned on the lower side of FIG. 1 (a), and the rolling bearing (upper bearing) 8 is positioned on the upper side of FIG. 1 (a). Further, the pump portion P accommodates an impeller 10 which is attached to one end side (the lower side of FIG. 1A) of the main shaft 2 and has a plurality of blades 12.

  The motor 4 is provided with a rotor 4a fixed to the main shaft 2 and a stator 4b fixed to the frame 14. For example, when the current is supplied to the stator 4b, the stator 4b and the rotor 4a Due to the magnetic interaction between them, the motor 4 can rotate the main shaft 2. Thereby, the submersible pump can circulate while circulating the liquid (for example, various waste water etc.) in the pump part P, when the several blade | wing 12 of the impeller 10 attached to the main shaft 2 rotates. .

  The mechanical seal chamber S is provided between the motor unit M and the pump unit P, and a mechanical seal 18 for keeping the motor unit M airtight is disposed therein. Thereby, for example, it is possible to prevent liquid (for example, various kinds of drainage) pumped from the pump unit P from entering the motor unit M, and as a result, the motor unit M can be kept airtight. In this case, the mechanical seal 18 has sliding portions (sliding surfaces) (two in total) at both ends thereof (upper and lower ends in FIG. 1A), and each coil spring (not shown) has each of them. A so-called monocoil double seal type seal that applies surface pressure to the sliding surface is applied as an example, and the mechanical seal (monocoil double seal) 18 is externally fitted to the main shaft 2. Further, inside the mechanical seal chamber S, a lubricating liquid for lubricating and cooling the sliding surface of the mechanical seal 18 is enclosed.

  The two rolling bearings 6 and 8 that rotatably support the main shaft 2 include a pair of bearing rings (inner rings 6a and 8a and outer rings 6b and 8b) that are opposed to each other so as to be relatively rotatable, and inner rings 6a and 6a. A plurality of rolling elements 6c and 8c are provided so as to be freely rollable between raceway surfaces respectively formed on opposing surfaces of 8a and outer rings 6b and 8b. In this case, the inner rings 6a and 8a are rotating wheels that rotate together with the main shaft 2, and the outer rings 6b and 8b are stationary wheels that are always maintained in a non-rotating state. In addition, a lubricant (for example, grease) for lubricating the raceway surface of the raceway and the rolling surface of the rolling element is sealed in the two rolling bearings 6 and 8, respectively.

  In the present embodiment, of the two rolling bearings 6 and 8, the bearing (lower bearing 6) disposed at least near the mechanical seal chamber S includes the inside of the lower bearing 6 and the mechanical seal chamber S. An annular slinger is provided to prevent foreign matter from entering the inside (specifically, the upper sliding portion of the mechanical seal 18). In this case, the slinger is provided in a portion of the lower bearing 6 on the mechanical seal 18 side (lower portion in FIG. 1A). In addition, the slinger can be formed in an arbitrary shape, for example, can be formed so as to have various shapes shown in FIGS. The foreign matter includes, for example, dust, dust, various metal powders, etc., but in the following description, the lubricant leaked from the mechanical seal chamber S and the grease leaked (flowed out) from the lower bearing 6 are used. Assume a certain case.

  In the configuration shown in FIGS. 1B to 1D, the slinger 20 is formed in an annular plate shape, and the slinger 20 is fixed to a predetermined portion of the rotating wheel (inner ring 6a) of the lower bearing 6. Base end portion 20a and a surface portion extending in a direction (continuous to FIGS. 1B to 1D) across the base end portion 20a and crossing between the lower bearing 6 and the mechanical seal 18. 20b and a stationary ring (outer ring 6b) of the lower bearing 6 that is continuous with the surface portion 20b and faces the outer surface of the lower bearing 6 with a predetermined space therebetween (see FIGS. 1B to 1D). And a wall portion 20c extending at a predetermined bending angle α of 90 degrees or more and 180 degrees or less.

  In this case, the base end portion 20 a of the slinger 20 is formed in a cylindrical shape whose inner diameter is slightly larger than the outer diameter of the inner ring 6 a of the lower bearing 6. The surface portion 20b of the slinger 20 has an outer diameter slightly smaller than the inner diameter of the outer ring 6b of the lower bearing 6, and its inner diameter is slightly larger than the outer diameter of the inner ring 6a. It is formed in a shape. The slinger 20 has a surface portion 20b that is substantially perpendicular to the base end portion 20a and extends in the direction of the outer ring 6b of the lower bearing 6 (upward direction in FIGS. 1B to 1D). Further, the surface portion 20b is formed continuously to one end of the base end portion 20a (the left end in FIGS. 1B to 1D). The slinger 20 has a surface portion 20b inclined at a predetermined angle with respect to the base end portion 20a in the direction of the outer ring 6b of the lower bearing 6 (upward direction in FIGS. 1B to 1D). The surface 20b may be formed continuously with one end of the base end 20a (the left end in FIGS. 1B to 1D) so as to extend.

  The wall portion 20c of the slinger 20 is formed in an annular shape whose outer diameter is slightly smaller than the inner diameter of the outer ring 6b. In this case, the wall portion 20c of the slinger 20 forms a predetermined bending angle α of 90 degrees or more and 180 degrees or less with respect to the surface portion 20b, and the external direction of the lower bearing 6 (FIGS. 1 (b) to (b)). What is necessary is just to form the wall part 20c continuously at the end (upper end of FIG.1 (b)-(d)) of the surface part 20b so that it may extend in the d direction of d).

  For example, in the configuration shown in FIG. 1B, the slinger 20 has a wall portion 20c that is substantially perpendicular (90 degrees) with respect to the surface portion 20b at a bending angle α (direction of the mechanical seal 18 (direction of the mechanical seal 18)). The wall portion 20c is formed continuously with one end of the surface portion 20b (the upper end of FIG. 1B) so as to extend in the right direction in FIG. In the configuration shown in FIG. 1 (c), the slinger 20 has a wall portion 20c with respect to the surface portion 20b at a predetermined bending angle α (for example, 135 degrees) greater than 90 degrees and smaller than 180 degrees. The wall portion 20c is formed continuously with one end of the surface portion 20b (the upper end in FIG. 1C) so as to extend in the external direction (upper right direction in FIG. 1C). Further, in the configuration shown in FIG. 1 (d), the slinger 20 has a wall portion 20c with a bending angle α of 180 degrees with respect to the surface portion 20b, toward the outside of the lower bearing 6 (upward direction in FIG. 1 (d)). The wall portion 20c is formed continuously with one end of the surface portion 20b (the upper end in FIG. 1 (d)) so as to extend to the front. That is, in this case, the slinger 20 is formed such that the wall 20c is continuous with one end of the surface 20b in parallel with the surface 20b, and the surface 20b and the wall 20c form a series of flat surfaces.

  The base end 20a of the slinger 20 is fixed to a portion of the inner ring 6a of the lower bearing 6 on the side of the mechanical seal 18 (the portion on the right side in FIGS. 1B to 1D). In the present embodiment, the slinger 20 is externally fitted to the inner ring 6a so that the inner peripheral surface 22a of the base end portion 20a abuts on the outer peripheral surface of the inner ring 6a (the surface facing the outer ring 6b) 6d. In this case, as an example, the inner ring 6a has a protrusion that protrudes by a predetermined length from the end of the outer ring 6b to the outer side of the lower bearing 6 (the right side in FIGS. 1B to 1D). The part t is formed continuously along the circumferential direction, and the slinger 20 is externally fitted to the outer peripheral surface t1 of the protruding part t. And the slinger 20 can leave a predetermined space (gap) between the wall 20c and the inner peripheral surface (opposite surface to the inner ring 6a) 6e of the outer ring 6b in a state of being fitted on the inner ring 6a. It is configured to be able to. Thereby, the slinger 20 rotates with the inner ring | wheel 6a, without contacting the outer ring | wheel 6b.

  The method of fixing the slinger 20 is not particularly limited as long as the slinger 20 can be rotated together with the inner ring 6a without contacting the outer ring 6b. Good. The slinger 20 is preferably provided on the rotating wheel (in this embodiment, the inner ring 6a) in order to maximize the effects described later, but can also be provided on the outer ring 6b. In this case, for example, a projecting portion that protrudes by a predetermined length on the outer side of the lower bearing 6 (on the right side in FIGS. 1B to 1D) from the end portion of the inner ring 6a at the end portion of the outer ring 6b in the circumferential direction. And the slinger 20 may be fixed (for example, external fitting, adhesion, welding, etc.) to the inner peripheral surface of the projecting portion.

  As described above, by providing the slinger 20 on the lower bearing 6, even if the lubricating liquid leaked from the mechanical seal chamber S enters the motor portion M along the outer peripheral surface of the main shaft 2, the leakage lubrication is performed. The liquid can be dammed with the slinger 20. As described above, since the slinger 20 rotates together with the inner ring 6a of the lower bearing 6, the lubricating liquid blocked by the slinger 20 receives a centrifugal force generated by the rotation of the slinger 20, and is directed toward the outside of the submersible pump ( It is scattered toward the outside of the lower bearing 6 (the right direction or the upward direction in FIGS. 1B to 1D). As a result, the lubricating liquid leaked from the mechanical seal chamber S can be prevented from entering the inside of the lower bearing 6. Thereby, for example, it is possible to effectively prevent the lubricant (for example, grease) enclosed in the lower bearing 6 from being softened and leaking (outflowing) from the inside of the bearing to the outside of the bearing.

Further, even when the grease leaks (outflows) from the inside of the bearing to the outside of the bearing, the grease is dammed by the slinger 20, and the external direction of the submersible pump (the external direction of the lower bearing 6 (FIG. 1B to FIG. 1)). (d) rightward or upward)). As a result, it is possible to prevent the grease leaked (outflowed) from the inside of the lower bearing 6 from entering the sliding portion of the mechanical seal 18. Thereby, for example, heat generation of the mechanical seal 18 due to poor lubrication of the sliding portion can be effectively prevented.
As described above, by providing the slinger 20 on the lower bearing 6, the lower bearing 6 and the mechanical seal 18 are prevented from being damaged, so that the submersible pump can be operated with a certain accuracy over a long period of time (long life). ). As a result, the durability of the submersible pump can be improved.

  In addition to providing the slinger 20 on the lower bearing 6, the above-described leakage flow path for discharging the lubricating liquid, the storage section for storing the discharged lubricating liquid, and the reservoir section for the grease that has flowed out are combined with the submersible pump. By being formed, the slinger 20 is dammed up and scattered toward the outside of the submersible pump (the outside of the lower bearing 6 (the right direction or the upward direction in FIGS. 1B to 1D)). Lubricants and grease can be stored. Thereby, the lubricating liquid leaked from the mechanical seal chamber S enters the inside of the lower bearing 6, and the grease leaked (outflowed) from the inside of the lower bearing 6 enters the sliding portion of the mechanical seal 18. Can be more effectively prevented.

  Further, the slinger 20 extends, for example, in a direction crossing between the lower bearing 6 and the mechanical seal 18 (downward direction in FIGS. 1B to 1D) continuously from the wall portion 20c. A return portion (not shown) may be provided. In this case, the slinger 20 has its return portion 20d extending toward the inner ring 6a of the lower bearing 6 (downward direction in FIGS. 1B to 1D) with a predetermined bending angle with respect to the wall portion 20c. In addition, the return portion may be formed continuously at one end of the wall portion 20c (the right end in FIGS. 1B and 1C and the upper end in FIG. 1D). For example, in the configuration shown in FIG. 1B, as an example, the return portion of the slinger 20 has an outer diameter slightly smaller than the inner diameter of the outer ring 6b of the lower bearing 6, and the inner diameter is smaller than the outer diameter of the inner ring 6a. What is necessary is just to make it large and the inside forms a hollow disk shape, and to make it continue to the end (right end of FIG.1 (b)) of the wall part 20c.

Further, the present invention is not limited to the configuration according to the above-described embodiment. For example, the same effect can be obtained even with the bearing configuration according to each modification shown in FIGS.
2 to 9, an annular seal for sealing the inside of the bearing 6 is provided between the stationary ring (outer ring 6 b) and the rotating ring (inner ring 6 a) of the lower bearing 6. A plate (sealing plate) 30 is interposed to face the slinger 20. In this case, the seal plate (sealing plate) 30 has an outer diameter portion fixed to the outer ring 6b, and an inner diameter portion formed continuously on the facing surface (outer peripheral surface 6d) of the inner ring 6a with respect to the outer ring 6b along the circumferential direction. The seal groove 50 is in contact with at least one of the inner peripheral surface and the outer peripheral surface.

FIG. 2 shows a lower bearing 6 of the submersible pump according to the first modified example. In the configuration shown in FIG. 2, the inner ring 6a of the lower bearing 6 has an axial direction ( A mounting groove 6f is formed continuously along the circumferential direction at the end of the mounting groove 6f, and a slinger 20 is mounted in the mounting groove 6f (for example, fixed by internal fitting, adhesion, welding, or the like). Have been). In this case, the slinger 20 has a wall portion 20c continuous with one end of the surface portion 20b in parallel with the surface portion 20b (at a bending angle of 180 degrees), and the surface portion 20b and the wall portion 20c form a series of flat surfaces. Is formed.
Further, on the outer ring 6 b of the lower bearing 6, a contact-type seal plate (sealing plate) 30 as a seal member is opposed to the slinger 20 at the end of the inner peripheral surface 6 e in the axial direction (left-right direction in FIG. 2). It is attached. In this case, the seal plate (sealing plate) 30 has, for example, an inner diameter portion (lip 30 b) that is in contact with the inner peripheral surface 50 a of the seal groove 50.

In the configuration shown in FIG. 2, the mounting groove 6f formed in the inner ring 6a has an annular inner peripheral surface 41 that is eccentric by a predetermined amount with respect to the axis of the inner ring 6a.
The slinger 20 includes an annular portion (surface portion 20b) that covers the opening of the end portion of the lower bearing 6 (right end portion in FIG. 2), and a cylindrical portion (base end portion) that is continuously formed on the inner periphery of the surface portion 20b. 20a), and the outer peripheral surface of the base end portion 20a fitted and fixed concentrically with the inner ring 6a with respect to the annular inner peripheral surface 41 of the mounting groove 6f is provided on the annular inner peripheral surface 41. Engagement protrusions (not shown) are formed to protrude radially outward (upward and downward in FIG. 2) according to the amount of eccentricity.

The slinger 20 presses the engaging protrusion into a position where the radial depth of the annular inner peripheral surface 41 is the deepest (a position where the eccentricity is maximum), so that the base end 20a is a circle of the mounting groove 6f. It is fitted and fixed to the annular inner peripheral surface 41 concentrically with the inner ring 6a. Further, in the inner ring 6a, an escape portion 34 corresponding to the thickness of the surface portion 20b (the distance in the left-right direction in FIG. 2) is formed at an end portion (right end portion in FIG. 2) adjacent to the mounting groove 6f. By complementarily attaching the surface portion 20b of the slinger 20 to the relief portion 34, the outer surface (right surface in FIG. 2) 26b of the surface portion 20b is substantially flush with the end surface (right end surface in FIG. 2) of the outer ring 6b. The axial width (bearing width) of the lower bearing 6 including the slinger 20 can be reduced. In addition, since the gap (labyrinth) between the seal plate (sealing plate) 30 and the surface portion 20b and the wall portion 20c of the slinger 20 can be reduced, the mechanical seal chamber S (FIG. It is possible to effectively prevent the lubricating fluid leaked from (see)) from entering and the grease from leaking out (flowing out) from the lower bearing 6.
Further, in the configuration shown in FIG. 2, the outer peripheral portion 51 of the surface portion 20b of the slinger 20 is bent inward in the axial direction (left side in FIG. 2) and is disposed close to the seal plate (sealing plate) 30, and the wall portion 20c. The front end 22c is disposed close to the inner peripheral surface of an annular protrusion 37 provided on the seal plate (sealing plate) 30 so as to protrude outward in the axial direction (rightward in FIG. 2).

According to the above configuration, the slinger 20 has a base end portion 20a that is fitted and fixed concentrically with the inner ring 6a to the annular inner peripheral surface 41 of the mounting groove 6f formed in the inner ring 6a. In accordance with the amount of eccentricity of the annular inner peripheral surface 41 that is eccentric with respect to the axis 6a, the engaging protrusion formed on the outer peripheral surface of the base end portion 20a is press-fitted into the annular inner peripheral surface 41. It can be firmly and stably fixed to the inner ring 6a.
For this reason, even if the main shaft 2 of the submersible pump (see FIG. 1A) rotates at a high speed, the base end portion 20a of the slinger 20 expands in the radial direction (vertical direction in FIG. 2) due to centrifugal force. The engaging projection of the base end portion 20a is locked to the eccentric annular inner peripheral surface 41 of the mounting groove 6f, so that the slinger 20 can be prevented from being rotated. Can be securely fixed to the inner ring 6a.
Thereby, even if it is a case where the main axis | shaft 2 (refer Fig.1 (a)) of a submersible pump rotates at high speed, the effect similar to the submersible pump which concerns on 1st Embodiment mentioned above can be acquired.

FIG. 3 shows a lower bearing 6 of the submersible pump according to the second modified example. In the configuration shown in FIG. 3, the inner ring 6a of the lower bearing 6 has an axial direction ( A step (mounting groove) 6f is recessed in the end of the left and right direction in FIG. 3, and a cover (slinger 20) is mounted in the mounting groove 6f (for example, fixed by internal fitting, adhesion, welding, or the like). Have been). In this case, the slinger 20 has a wall portion 20c continuous with one end of the surface portion 20b in parallel with the surface portion 20b (at a bending angle of 180 degrees), and the surface portion 20b and the wall portion 20c form a series of flat surfaces. Is formed.
Further, on the outer ring 6 b of the lower bearing 6, a contact-type seal plate (sealing plate) 30 as a seal member is opposed to the slinger 20 at the end portion in the axial direction (left-right direction in FIG. 3) of the inner peripheral surface 6 e. Attached. In this case, the seal plate (sealing plate) 30 has, for example, an inner diameter portion (lip 30 b) that is in contact with the inner peripheral surface 50 a of the seal groove 50.

  The slinger 20 and the seal plate 30 are positioned so that the slinger 20 is located on the outer side of the bearing (the left side in FIG. 3), and the surface portion 20b and the wall portion 20c of the slinger 20 are the outer surfaces (the left side surface in FIG. 3). A predetermined gap (labyrinth) is provided between the outer surface 30a and the outer surface 30a so as to cover substantially the entire surface. The width of the inner ring 6a in the axial direction (left-right direction in FIG. 3) is such that the surface portion 20b and the wall portion 20c of the slinger 20 are not protruded to the outside of the lower bearing 6 (left side in FIG. 3). In consideration of the thickness of the wall portion 20c (the distance in the left-right direction in FIG. 3), it is configured to be smaller than the width of the outer ring 6b in the axial direction (left-right direction in FIG. 3) by a predetermined length (the end of the inner ring 6a). (A relief portion 34 is formed at the left end portion in FIG. 3).

In the configuration shown in FIG. 3, the mounting groove 6f includes, as an example, an axial surface 6h continuous along the circumferential direction with a predetermined width in the axial direction (left-right direction in FIG. 3), and a predetermined depth in the radial direction. Now, it is formed by forming a substantially L-shaped groove in a sectional view composed of a radial surface 6 i continuous along the circumferential direction. The base end portion 20a of the slinger 20 is fixed to the inner ring 6a within the range of the width and depth of the mounting groove 6f.
In this case, the base end portion 20a is attached with the thickness (distance in the vertical direction in FIG. 3) attached to the axial surface 6h of the mounting groove 6f of the inner ring 6a with the outer peripheral surface 24a in contact with the outer end surface 24a. It is configured to be within the depth range of the groove 6f so that the inner peripheral surface 22a does not protrude from the inner peripheral surface 6j of the inner ring 6a (so that a predetermined step d is formed). According to such a configuration, since the slinger 20 is accommodated in the mounting groove 6f and a recessed step d is formed, it is possible to secure a tolerance of the inner diameter of the lower bearing 6 by the step d. Further, the base end portion 20a is long in a state where the inner surface (the right side surface in FIG. 3) 24b of the surface portion 20b is in contact with the escape portion 34 formed at the end portion (left end portion in FIG. 3) of the inner ring 6a. (The distance in the left-right direction in FIG. 3) falls within the range of the width of the mounting groove 6f, and the outer surface (the left surface in FIG. 3) 26b of the surface portion 20b and the end surface of the outer ring 6b (the left end surface in FIG. 3) are approximately. It is comprised so that it may become flush.

  Further, the wall portion 20c has a tip 22c extending in the outer direction of the submersible pump (upward in FIG. 3) positioned in a non-contact state with the inner peripheral surface 6e of the outer ring 6b, and the inner peripheral surface 6e. A predetermined labyrinth is formed in the axial direction (left-right direction in FIG. 3) between the two and the seal plate 30 located on the inner side (right side in FIG. 3) with respect to the wall portion 20c, and the radial direction together with the surface portion 20b. A predetermined long labyrinth is formed (in the vertical direction in FIG. 3). Further, the surface portion 20b has a thickness (FIG. 3) in which the outer surface (left surface in FIG. 3) 26b does not protrude outward (leftward in FIG. 3) than the width in the axial direction (left-right direction in FIG. 3) of the outer ring 6b. 3 in the left-right direction). Note that the thickness of the wall portion 20c (the distance in the left-right direction in FIG. 3) is configured similarly to the thickness of the surface portion 20b.

  According to the above configuration, the lower bearing 6 is sealed by both the slinger 20 and the seal plate 30 without increasing the bearing width, and the submersible pump mechanical seal chamber S (see FIG. 1A). It is possible to reliably prevent the lubricating liquid leaking from the inside from entering the inside of the lower bearing 6. Further, it is possible to reliably prevent the lubricant (for example, grease) sealed in the lower bearing 6 from leaking (outflowing) outside the bearing. For this reason, the effect similar to the submersible pump which concerns on 1st Embodiment mentioned above can be acquired, aiming at size reduction of a submersible pump.

  FIG. 4 shows a lower bearing 6 of the submersible pump according to the third modified example. In the configuration shown in FIG. 4, the lower bearing 6 includes a slinger type flat plate shield plate on the inner ring 6a. A slinger 20) is provided. In this case, the base end portion 20a of the slinger 20 is mounted between the end portion of the inner ring 6a of the lower bearing 6 (the left end portion in FIG. 4) and the retaining ring 60 so as to be attached to the inner ring 6a. In addition, the slinger 20 is formed so that the surface portion 20b is continuous with one end of the base end portion 20a in parallel with the base end portion 20a, and the base end portion 20a and the surface portion 20b form a series of flat surfaces. . Further, the slinger 20 has a wall portion 20c continuous with one end of the surface portion 20b in parallel with the surface portion 20b (at a bending angle of 180 degrees), and the surface portion 20b and the wall portion 20c form a series of flat surfaces. Is formed. That is, the slinger 20 is configured such that the base end portion 20a and the wall portion 20c are parallel to the surface portion 20b (at a bending angle of 180 degrees) and are continuous with the surface portion 20b to form a series of flat surfaces. ing.

Further, on the outer ring 6 b of the lower bearing 6, a contact-type seal plate (sealing plate) 30 as a seal member is opposed to the slinger 20 at the end portion in the axial direction (left-right direction in FIG. 4) of the inner peripheral surface 6 e. Attached. In this case, the seal plate (sealing plate) 30 has, for example, an inner diameter portion (lip 30 b) that is in contact with the inner peripheral surface 50 a of the seal groove 50.
The slinger 20 and the seal plate (sealing plate) 30 are positioned on the outer side of the bearing (left side of FIG. 4), and the surface portion 20b of the slinger 20 is the outer surface of the seal plate (sealing plate) 30 (FIG. 4). A predetermined gap (labyrinth) is provided between the left side surface 30a and the wall portion 20c so as to cover the entire outer surface 30a.

  According to the above configuration, since the slinger 20 is provided on the lower bearing 6 so as to cover the entire seal plate (sealing plate) 30, the seal plate (sealing plate) 30 is, for example, a submersible pump. Direct contact with the lubricant leaked from the mechanical seal chamber S (see FIG. 1A) can be avoided. Further, since the slinger 20 is opposed to the seal plate (sealing plate) 30 with a predetermined gap (labyrinth), the sealing performance of the lower bearing 6 can be improved, and the mechanical seal chamber S of the submersible pump. (See FIG. 1 (a).) The lubricating fluid leaked from the inside of the lower bearing 6 and the lubricant (for example, grease) sealed in the lower bearing 6 leaked out (outflow). ) Can be reliably prevented. Further, since the slinger 20 can be provided without any special change in the lower bearing 6 itself and its peripheral structure, the cost is low and there is no significant increase in space. For this reason, the effect similar to the submersible pump which concerns on 1st Embodiment mentioned above can be acquired, aiming at size reduction of a submersible pump.

  FIG. 5 shows a lower bearing 6 of a submersible pump according to a fourth modification. In the configuration shown in FIG. 5, the lower bearing 6 is provided with a slinger 20 as a bearing peripheral component. . In this case, the base end portion 20a of the slinger 20 is attached to the end portion (left end portion in FIG. 5) of the inner ring 6a of the lower bearing 6 (for example, fixed by external fitting, adhesion, welding, or the like). ). Thereby, the slinger 20 rotates together with the inner ring 6 a of the lower bearing 6. In addition, the slinger 20 is formed so that one end of the base end portion 20a is continuous with the surface portion 20b parallel to the base end portion 20a, and the base end portion 20a and the surface portion 20b form a series of flat surfaces. . Further, the slinger 20 has a wall portion 20c continuous with one end of the surface portion 20b in parallel with the surface portion 20b (at a bending angle of 180 degrees), and the surface portion 20b and the wall portion 20c form a series of flat surfaces. Is formed. That is, the slinger 20 is configured such that the base end portion 20a and the wall portion 20c are parallel to the surface portion 20b (at a bending angle of 180 degrees) and are continuous with the surface portion 20b to form a series of flat surfaces. ing.

In addition to the slinger 20, the bearing peripheral parts include, for example, a shielding plate, a stepped shaft, or a second sealing plate provided to face the sealing plate (first sealing plate (sealing plate 30)). May be. Further, the outer ring 6b of the lower bearing 6 has a contact-type seal plate (sealing plate) 30 as a seal member at the end portion in the axial direction (left-right direction in FIG. 5) of the inner peripheral surface 6e. Are attached oppositely. In this case, the seal plate (sealing plate) 30 has, for example, an inner diameter portion (lip 30 b) that is in contact with the inner peripheral surface 50 a of the seal groove 50.
The seal plate (sealing plate) 30 is provided with an annular protrusion 37 that protrudes outward in the axial direction (leftward in FIG. 5), and the annular protrusion 37 is between the tip 22 c of the wall portion 20 c of the slinger 20. A predetermined gap (labyrinth) is formed.

  In the configuration shown in FIG. 5, the labyrinth between the annular protrusion 37 of the seal plate (sealing plate) 30 and the tip 22c of the wall portion 20c of the slinger 20, for example, the mechanical seal chamber S (FIG. It is possible to prevent the lubricating liquid leaked from the above) from entering the lower bearing 6. Further, the lubricating liquid adhering to the surface 37a of the annular protrusion 37 of the seal plate (sealing plate) 30 is moved outwardly from the bearing along the surface 37a of the annular protrusion 37 by the air flow generated by the rotation of the slinger 20 (upper side in FIG. 5). Therefore, the lubricating liquid can be effectively prevented from entering the lip 30b portion of the seal plate (sealing plate) 30. As described above, the annular bearing 37 is provided on the seal plate (sealing plate) 30 in the direction of the lip 30b only by providing the seal plate (sealing plate) 30 without any special change of the lower bearing 6 itself and its peripheral structure. A sealing performance sufficient to prevent the intrusion of the lubricating liquid can be ensured over a long period of time. For this reason, the effect similar to the submersible pump which concerns on 1st Embodiment mentioned above can be acquired, aiming at the cost reduction of a submersible pump.

  6 shows a lower bearing 6 of a submersible pump according to a fifth modification. In the configuration shown in FIG. 6, the inner ring 6a of the lower bearing 6 has an axial direction of its outer peripheral surface 6d (see FIG. 6 is provided with an attachment groove 6f formed continuously along the circumferential direction at the end, and a cover (slinger 20) is attached to the attachment groove 6f (for example, internal fitting, adhesion, welding, etc.) Fixed by). Further, on the outer ring 6 b of the lower bearing 6, a contact-type seal plate (sealing plate) 30 as a seal member is opposed to the slinger 20 at the end portion in the axial direction (left-right direction in FIG. 6) of the inner peripheral surface 6 e. Attached. In this case, the seal plate (sealing plate) 30 has, for example, an inner diameter portion (lip 30 b) that is in contact with the inner peripheral surface 50 a of the seal groove 50. Further, the seal groove 50 of the seal plate (sealing plate) 30 is formed continuously to the attachment groove 6f of the slinger 20 and positioned on the inner side of the inner ring 6a (right side in FIG. 6) than the attachment groove 6f.

  The slinger 20 and the seal plate (sealing plate) 30 are positioned on the outer side of the bearing (left side in FIG. 6), and the surface portion 20b and the wall portion 20c of the slinger 20 are the outer surfaces of the seal plate (sealing plate) 30. (Left side surface in FIG. 6) A predetermined gap (labyrinth) is provided between the outer surface 30a and the outer surface 30a so as to cover substantially the entire surface. Further, the width of the inner ring 6a in the axial direction (left-right direction in FIG. 6) is such that the surface portion 20b of the slinger 20 and the wall portion 20c do not protrude to the outside of the lower bearing 6 (left side in FIG. 6). In consideration of the thickness of the wall portion 20c (the distance in the left-right direction in FIG. 6), it is configured to be smaller than the width of the outer ring 6b in the axial direction (left-right direction in FIG. 6) by a predetermined length (the end of the inner ring 6a). (A relief portion 34 is formed at the left end of FIG. 6).

  In the configuration shown in FIG. 6, the slinger 20 is formed in an annular plate shape, and has a proximal end portion 20 a on its inner diameter portion. In this case, the base end portion 20a of the slinger 20 is substantially perpendicular to the axial fitting piece 28a fitted to the inner ring 4a (end portion of the outer peripheral surface 6d) and the axial fitting piece 28a. And radial guide pieces 29a that are in contact with the end face of the inner ring 4a (the left end in FIG. 6) are provided alternately along the circumferential direction. The surface portion 20b of the slinger 20 is continuous with one end of the base end portion 20a, that is, one end of the axial fitting piece 28a (left end in FIG. 6) and one end of the radial guide piece 29a (upper end in FIG. 6). Is formed.

In addition, each axial direction fitting piece 28a of the base end part 20a is formed by bending the inner diameter part of the slinger 20 in several axial directions (right direction in FIG. 6) as an example. Further, the axial fitting piece 28a has a plurality of projecting pieces circumferentially formed on the inner diameter portion of the slinger 20 integrally or separately in the axial direction (right direction in FIG. 6). It may be formed by projecting in the axial direction (right direction in FIG. 6) continuously in the direction. In this case, you may comprise so that the internal diameter part of the slinger 20 may become the radial direction guide piece 29a as it is. The slinger 20 externally fits each axial fitting piece 28a to the outer peripheral surface 6d (attachment groove 6f) of the inner ring 6a of the lower bearing 6, and the radial guide piece 29a to the end of the inner ring 6a (FIG. 6). The left end portion of the contact portion 34 is fixed in contact with the escape portion 34 formed at the left end portion.
Further, in this case, the slinger 20 has a wall portion 20c continuous at one end of the surface portion 20b in parallel with the surface portion 20b (at a bending angle of 180 degrees), and the surface portion 20b and the wall portion 20c form a series of flat surfaces. Is formed.

  According to the above configuration, since the slinger 20 is provided on the lower bearing 6 so as to cover substantially the entire seal plate (sealing plate) 30, for example, the mechanical seal chamber S of the submersible pump (FIG. 1). Even when leaking from (a), most of the leakage is blocked by the slinger 20, and the seal plate (sealing plate) 30 can be prevented from coming into direct contact with the lubricating liquid. Further, the sealing performance of the lower bearing 6 is improved by the labyrinth between the surface portion 20b and the wall portion 20c of the slinger 20 and the seal plate 30, and the labyrinth between the tip 22c of the wall portion 20c and the outer ring 6b. The lubricant leaked from the mechanical seal chamber S of the submersible pump (see FIG. 1A) enters the inside of the lower bearing 6 and the lubricant enclosed in the lower bearing 6 (for example, Leakage (outflow) of grease to the outside of the bearing can be reliably prevented. Further, as described above, the slinger 20 can be firmly and stably fixed to the inner ring 6a by using both the outer peripheral surface 6d (attachment groove 6f) of the inner ring 6a and the relief portion 34 of the inner ring 6a.

  For this reason, the lower bearing 6 can be manufactured at a low cost without any special change of itself and its peripheral structure, and the bearing width is not increased. Even if the main shaft 2 (see FIG. 1A) of the submersible pump rotates at high speed, the slinger 20 can be reliably fixed to the inner ring 6a. Thereby, even if the main shaft 2 (see FIG. 1A) of the submersible pump rotates at high speed while reducing the size of the submersible pump, the same effect as the submersible pump according to the first embodiment described above can be obtained. Obtainable.

  FIG. 7 shows a lower bearing 6 of a submersible pump according to a sixth modification. In the configuration shown in FIG. 7, the inner ring 6a of the lower bearing 6 has an axial direction (see FIG. 7 is provided with a mounting groove 6f continuously along the circumferential direction at the end, and a cover (slinger 20) is attached to the mounting groove 6f (for example, internal fitting, adhesion, welding, etc.) Fixed by). Further, on the outer ring 6 b of the lower bearing 6, a contact-type seal plate (sealing plate) 30 as a seal member is opposed to the slinger 20 at the end portion in the axial direction (left-right direction in FIG. 7) of the inner peripheral surface 6 e. Attached. In this case, the seal plate (sealing plate) 30 has, for example, an inner diameter portion (lip 30 b) that is in contact with the inner peripheral surface 50 a of the seal groove 50. Further, the seal groove 50 of the seal plate (sealing plate) 30 is formed so as to be continuous with the attachment groove 6f of the slinger 20 and positioned on the inner side (right side in FIG. 7) of the inner ring 6a than the attachment groove 6f.

  The slinger 20 and the seal plate 30 are positioned so that the slinger 20 is located on the outer side of the bearing (left side in FIG. 7), and the surface portion 20b of the slinger 20 is between the outer surface (left side surface in FIG. 7) 30a. A predetermined gap (labyrinth) is provided at each of the outer surfaces 30a so as to cover substantially the entire outer surface 30a. Further, the width of the inner ring 6a in the axial direction (left-right direction in FIG. 7) is such that the surface portion 20b of the slinger 20 and the wall portion 20c are not protruded to the outside of the lower bearing 6 (left side in FIG. 7). The width of the outer ring 6b in the axial direction (left and right direction in FIG. 7) by a predetermined length in consideration of the thickness (distance in the left and right direction in FIG. 7) and the length of the wall portion 20c (distance in the left and right direction in FIG. 7) (The escape portion 34 is formed at the end of the inner ring 6a (left end in FIG. 7)).

  Further, in the configuration shown in FIG. 7, the outer ring 6b protrudes from the end (left end in FIG. 7) to the outer side of the lower bearing 6 (left side in FIG. 7) by a predetermined length at the end (left end in FIG. 7). The protruding portion u is continuously formed along the circumferential direction. In this case, the protrusion u is configured such that the thickness (the distance in the vertical direction in FIG. 7) gradually decreases toward the outside of the lower bearing 6 (left side in FIG. 7). That is, the protrusion u is formed such that its inner peripheral surface u1 is inclined at a predetermined angle toward the outside of the lower bearing 6 (left side in FIG. 7).

  In the configuration shown in FIG. 7, the slinger 20 is formed in an annular plate shape, and has a proximal end portion 20 a on its inner diameter portion. In this case, the base end portion 20a of the slinger 20 is substantially perpendicular to the axial fitting piece 28a fitted to the inner ring 4a (end portion of the outer peripheral surface 6d) and the axial fitting piece 28a. And radial guide pieces 29a that are in contact with the end face of the inner ring 4a (the left end in FIG. 7) are provided alternately along the circumferential direction. The surface portion 20b of the slinger 20 is continuous with one end of the base end portion 20a, that is, one end of the axial fitting piece 28a (left end in FIG. 7) and one end of the radial guide piece 29a (upper end in FIG. 7). Is formed.

  In addition, each axial direction fitting piece 28a of the base end part 20a is formed by bending the inner diameter part of the slinger 20 in several axial directions (right direction in FIG. 7) as an example. In addition, the axial fitting piece 28a has a plurality of protruding pieces arranged circumferentially or integrally on the inner diameter portion of the slinger 20 in the axial direction (right direction in FIG. 7) or separately. It may be formed by projecting in the axial direction (right direction in FIG. 7) continuously in the direction. In this case, you may comprise so that the internal diameter part of the slinger 20 may become the radial direction guide piece 29a as it is. The slinger 20 externally fits each axial fitting piece 28a to the outer peripheral surface 6d (mounting groove 6f) of the inner ring 6a of the lower bearing 6, and the radial guide piece 29a to the end of the inner ring 6a (FIG. 7). The left end portion of the contact portion 34 is fixed in contact with the escape portion 34 formed at the left end portion.

  In the present modification, the slinger 20 has a wall portion 20c with respect to the surface portion 20b at a predetermined bending angle α (for example, 135 degrees) of 90 degrees or more and 180 degrees or less (for example, 135 degrees). 7, the wall portion 20c is formed continuously with one end of the surface portion 20b. The predetermined bending angle α may be set so as to substantially coincide with the predetermined inclination angle of the protruding portion u (inner peripheral surface u1) of the outer ring 6b. Accordingly, the slinger 20 can be configured such that the outer peripheral surface 24c of the wall portion 20c faces the inner peripheral surface u1 with a predetermined gap along the inner peripheral surface u1 of the protruding portion u. it can. In addition, without providing the protrusion u in the outer ring 6b, the thickness (the distance in the vertical direction in FIG. 7) gradually decreases as the end of the outer ring 6b moves toward the outside of the lower bearing 6 (left side in FIG. 7). (For example, an R-shaped chamfer may be provided). In this case, the slinger 20 faces the outer peripheral surface 24c of the wall portion 20c so as to face the end portion of the outer ring 6b (for example, an R-shaped chamfered portion) with a predetermined gap therebetween. The wall portion 20c may be continuously formed at one end of the surface portion 20b at a predetermined bending angle α.

  According to the above configuration, since the slinger 20 is provided on the lower bearing 6 so as to cover substantially the entire seal plate (sealing plate) 30, for example, the mechanical seal chamber S of the submersible pump (FIG. 1). Even when leaking from (a), most of the leakage is blocked by the slinger 20, and the seal plate (sealing plate) 30 can be prevented from coming into direct contact with the lubricating liquid. The slinger 20 has a wall portion 20c extending at a predetermined bending angle α (for example, 135 degrees) toward the outside of the lower bearing 6 (upper left direction in FIG. 7). The lubricating liquid moving along the wall portion 20c can be effectively scattered toward the outside direction of the submersible pump (the outside direction of the lower bearing 6 (upper left direction in FIG. 7)).

  Further, the labyrinth between the surface portion 20b of the slinger 20 and the sealing plate (sealing plate) 30 and the labyrinth between the outer peripheral surface 24c of the wall portion 20c and the inner peripheral surface u1 of the protruding portion u of the outer ring 6b The sealability of the bearing 6 can be further improved, and the lubricant leaked from the mechanical seal chamber S (see FIG. 1A) of the submersible pump enters the lower bearing 6 or inside the lower bearing 6. Leakage (outflow) of the lubricant (for example, grease) enclosed in the outside of the bearing can be reliably prevented. Further, as described above, the slinger 20 can be firmly and stably fixed to the inner ring 6a by using both the outer peripheral surface 6d (attachment groove 6f) of the inner ring 6a and the relief portion 34 of the inner ring 6a. For this reason, even if the main shaft 2 of the submersible pump (see FIG. 1A) rotates at a high speed, the slinger 20 can be reliably fixed to the inner ring 6a.

  Thus, the main shaft 2 (see FIG. 1 (a)) of the submersible pump can be obtained simply by continuously forming the wall portion 20c of the slinger 20 at one end of the surface portion 20b at a predetermined bending angle α (for example, 135 degrees). Even in the case of high-speed rotation, it is possible to easily enhance the scattering effect of the lubricating liquid in the external direction of the submersible pump (upper left direction in FIG. 7), which is the same as the submersible pump according to the first embodiment described above. An effect can be obtained.

FIG. 8 shows the lower bearing 6 of the submersible pump according to the seventh modified example. In the configuration shown in FIG. 8, the inner ring 6a, the outer ring 6b, and the slinger 20 of the lower bearing 6 are the same as those described above. It is comprised similarly to the lower bearing 6 of the submersible pump which concerns on a modification.
In this modification, the seal plate (sealing plate) 30 protrudes toward the slinger 20, and a convex portion 30d that comes into contact with the slinger 20 is opposed to the slinger 20 (the outer surface of the seal plate (sealing plate) 30). The left surface of FIG. 8)) is provided on 30a. In this case, the convex portion 30d has an inner peripheral surface 34d and an outer peripheral surface 32d continuously formed in the circumferential direction along the facing surface 30a of the seal plate (sealing plate) 30, and the inner peripheral surface 34d. Is raised in the direction of the slinger 20 (left direction in FIG. 8) at a predetermined inclination angle β of 90 degrees or more and less than 180 degrees with respect to the facing surface 30a, and the outer peripheral surface 32d is surrounded by the inner peripheral surface 34d. It is configured as a three-dimensional solid (projection) formed by rising from the facing surface 30a in the direction of the slinger 20 (left direction in FIG. 8) so as to be connected along the direction. Note that the height of the convex portion 30d (the distance in the left-right direction in FIG. 8) is set to a predetermined height at which the tip portion contacts the inner surface (the right-side surface in FIG. 8) 24b of the surface portion 20b of the slinger 20. Therefore, there is no particular limitation here. Further, the rising angle of the outer peripheral surface 32d of the convex portion 30d (inclination angle with respect to the facing surface 30a) is set to an angle at which the outer peripheral surface 32d can be connected to the inner peripheral surface 34d along the circumferential direction. Then there is no particular limitation.

  As an example, in the configuration shown in FIG. 8, the convex portion 30d has a predetermined inclination angle β (for example, the bending of the slinger 20 described above) whose inner peripheral surface 34d is 90 degrees or more and smaller than 180 degrees with respect to the facing surface 30a. 8 rises in the direction of the slinger 20 (left direction in FIG. 8) and the outer peripheral surface 32d is substantially perpendicular to the facing surface 30a (in the slinger 20 direction (in FIG. 8)). Standing left). And the inner peripheral surface 34d and the outer peripheral surface 32d of the convex part 30d are connected linearly along the circumferential direction. The inner peripheral surface 34d and the outer peripheral surface 32d of the convex portion 30d may be connected in a planar shape via a predetermined plane along the circumferential direction. Further, the inner peripheral surface 34d and the outer peripheral surface 32d of the convex portion 30d may be formed in any shape such as a flat surface, a convex curved surface, and a concave curved surface. Furthermore, the convex portions 30d may be provided in a plurality of rows along the circumferential direction. The convex portion 30d may be intermittently formed in the circumferential direction, but in order to enhance the sealing effect of a seal plate (sealing plate) 30 described later, the convex portion 30d is provided along the circumferential direction. It is preferable to provide them continuously.

  According to the above configuration, since the slinger 20 is provided on the lower bearing 6 so as to cover substantially the entire seal plate 30, for example, the mechanical seal chamber S of the submersible pump (see FIG. 1A). Even if it leaks from (), most of it is blocked by the slinger 20, and the seal plate 30 can be prevented from coming into direct contact with the lubricating liquid. The slinger 20 has a wall portion 20c extending at a predetermined bending angle α (for example, 135 degrees) toward the outside of the lower bearing 6 (upper left direction in FIG. 8). The lubricating liquid moving along the wall portion 20c can be effectively scattered toward the outside direction of the submersible pump (the outside direction of the lower bearing 6 (upper left direction in FIG. 8)).

In addition to the labyrinth between the surface portion 20b of the slinger 20 and the seal plate 30, and the labyrinth between the outer peripheral surface 24c of the wall portion 20c and the inner peripheral surface u1 of the protruding portion u of the outer ring 6b, the surface portion of the slinger 20 By providing the convex portion 30d of the seal plate (sealing plate) 30 that contacts the inner surface (right surface in FIG. 8) 24b of the 20b, the sealing performance of the lower bearing 6 is further improved than the sixth modification described above. Can be improved. As a result, the lubricant leaked from the mechanical seal chamber S of the submersible pump (see FIG. 1A) enters the lower bearing 6 or the lubricant (for example, Leakage (outflow) of grease to the outside of the bearing can be prevented more reliably. The convex portion 30d of the sealing plate (sealing plate) 30 has an inner peripheral surface 34d with a predetermined inclination angle β with respect to the opposing surface 30a (for example, substantially the same angle as the bending angle α of the slinger 20 described above). Is formed in the direction of the slinger 20 (the left direction in FIG. 8), so that the lubricating liquid (oil droplets) adhering to the inner peripheral surface 34d is submerged along the inner peripheral surface 34d by its own weight. Can be moved more effectively in the external direction (the external direction of the lower bearing 6 (upper left direction in FIG. 8)). As a result, the sealing performance of the lower bearing 6 can be further improved.
Further, as described above, the slinger 20 can be firmly and stably fixed to the inner ring 6a by using both the outer peripheral surface 6d (attachment groove 6f) of the inner ring 6a and the relief portion 34 of the inner ring 6a. For this reason, even if the main shaft 2 of the submersible pump (see FIG. 1A) rotates at a high speed, the slinger 20 can be reliably fixed to the inner ring 6a.

  Thus, the wall portion 20c of the slinger 20 is continuously formed at one end of the surface portion 20b at a predetermined bending angle α (for example, 135 degrees), and the convex portion 30d of the seal plate (sealing plate) 30 is formed on the inner periphery. The surface 34d is formed so as to rise in the slinger 20 direction (left direction in FIG. 8) at a predetermined inclination angle β (for example, substantially the same angle as the bending angle α of the slinger 20 described above) with respect to the facing surface 30a. Thus, even when the main shaft 2 of the submersible pump (see FIG. 1 (a)) rotates at a high speed, the above direction of the lubricant submerged pump (the direction of the lower bearing 6) (the upper left direction of FIG. 8) )) And the sealing effect of the lower bearing 6 can be easily enhanced over a long period of time, and the same effect as the submersible pump according to the first embodiment described above can be obtained.

FIG. 9 shows a lower bearing 6 of the submersible pump according to the eighth modification. In the configuration shown in FIG. 9, the inner ring 6a of the lower bearing 6 has an end (right end in FIG. 9). Further, a projecting portion t projecting by a predetermined length is formed continuously along the circumferential direction from the end of the outer ring 6b to the outside of the lower bearing 6 (right side in FIG. 9).
In this modification, the slinger 20 is externally fitted to the inner ring 6a so that the base end portion 20a abuts the inner peripheral surface 22a thereof on the outer peripheral surface t1 of the protruding portion t. In addition, it is good also as a structure which externally fits the slinger 20 to the edge part of the outer peripheral surface 6d, without providing the protrusion part t in the inner ring | wheel 6a. Further, the slinger 20 has the surface portion 20b at the base end so that the surface portion 20b extends substantially perpendicularly to the base end portion 20a and extends toward the outer ring 6b of the lower bearing 6 (upward in FIG. 9). It is formed continuously at one end of the portion 20a. Further, the slinger 20 has a wall portion 20c continuous with one end of the surface portion 20b in parallel with the surface portion 20b (at a bending angle of 180 degrees), and the surface portion 20b and the wall portion 20c form a series of flat surfaces. Is formed.
Further, on the outer ring 6 b of the lower bearing 6, a contact-type seal plate (sealing plate) 30 as a seal member is opposed to the slinger 20 at the end portion in the axial direction (left-right direction in FIG. 9) of the inner peripheral surface 6 e. Attached. In this case, the seal plate (seal plate) 30 has, for example, an inner diameter portion (lip 30 b) that is in contact with the outer peripheral surface 50 b of the seal groove 50.

The slinger 20 and the seal plate 30 are positioned on the outer side of the bearing (right side in FIG. 9), and the surface portion 20b and the wall portion 20c of the slinger 20 are outside the seal plate (sealing plate) 30 (in FIG. 9). A predetermined gap (labyrinth) is provided between the right surface 30a and the outer surface 30a so as to cover the entire outer surface 30a.
Further, the wall portion 20c has a tip 22c extending in the outer direction of the submersible pump (upward in FIG. 9) positioned in a non-contact state with the inner peripheral surface 6e of the outer ring 6b, and the inner peripheral surface 6e. A predetermined labyrinth is formed in the axial direction (left-right direction in FIG. 9) between the two and a surface portion between the sealing plate (sealing plate) 30 located on the inner side (left side in FIG. 9) than the wall portion 20c. A predetermined labyrinth that is relatively long in the radial direction (the vertical direction in FIG. 9) is formed together with 20b.

According to the above configuration, since the slinger 20 is provided on the lower bearing 6 so as to cover the entire seal plate (sealing plate) 30, the seal plate (sealing plate) 30 is, for example, a submersible pump. Direct contact with the lubricant leaked from the mechanical seal chamber S (see FIG. 1A) can be avoided. Further, since the slinger 20 is opposed to the seal plate (sealing plate) 30 with a predetermined gap (labyrinth), the sealing performance of the lower bearing 6 can be improved, and the mechanical seal chamber S of the submersible pump. (See FIG. 1 (a).) The lubricating fluid leaked from the inside of the lower bearing 6 and the lubricant (for example, grease) sealed in the lower bearing 6 leaked out (outflow). ) Can be reliably prevented. Furthermore, since the inner diameter portion (lip 30b) of the seal plate (sealing plate) 30 is in contact with the outer peripheral surface 50b of the seal groove 50, the seal plate (sealing plate) 30 particularly from the mechanical seal chamber S of the submersible pump (see FIG. 1 (a)). The effect of preventing the leaked lubricant from entering the lower bearing 6 is high, and the sealing performance of the lower bearing 6 can be further improved.
Thereby, the effect similar to the submersible pump which concerns on 1st Embodiment mentioned above can be acquired, without accompanying the significant change of lower bearing 6 itself and its periphery structure.

The form of the slinger 20 is not particularly limited to the configurations of the first embodiment and the first to eighth modifications described above. For example, the size and thickness of the slinger 20 are the same as those of the lower bearing 6. Now, it may be arbitrarily set according to the outer diameter of the main shaft 2 or the like. Further, in the first embodiment and the first to eighth modifications described above, the material of the slinger 20 is not particularly mentioned, but as the slinger 20, for example, various kinds of metal (for example, steel) Or stainless steel), or all or part of a metal annular plate coated with various resins (for example, rubber or synthetic resin) or those with corrosion-resistant plating (for example, galvanized) Can be applied.
Moreover, although the slinger 20 was provided only in the lower bearing 6 in the first embodiment and the first to eighth modifications described above, the slinger 20 is formed between the lower bearing 6 and the mechanical seal 18 inside the submersible pump. If it is possible to provide a predetermined space therebetween, the slinger 20 may be provided on the main shaft 2 in addition to the lower bearing 6. In addition, although the slinger 20 was provided only in the site | part of the one end side (mechanical seal 18 side) of the lower side bearing 6 in 1st Embodiment mentioned above and its 1st modification-8th modification, in addition to this, others You may provide in the site | part of the end side (opposite side to the mechanical seal 18). Further, in addition to these, a slinger 20 may be provided on the upper bearing 8.

  Furthermore, in the first to eighth modifications described above, the material of the seal plate (sealing plate) 30 is not particularly mentioned. For example, as the seal plate (sealing plate) 30, a core material (various types) can be used. A material formed by coating a metal core or the like with an elastic material (a sealing material such as rubber or synthetic resin) can be used. The seal plate (sealing plate) 30 can be provided with any number of seal lips. As the seal plate (sealing plate) 30, a non-contact type seal or a non-contact type shield formed by pressing various metal plates, for example, may be applied.

It is a figure which shows the structural example of the submersible pump which concerns on 1st Embodiment of this invention, Comprising: (a) is sectional drawing of a principal part, (b)-(d) is the structure of the slinger provided in the lower side bearing. Sectional drawing which shows an example. Sectional drawing which shows the structural example of the slinger provided in the lower bearing of the submersible pump which concerns on the 1st modification of this invention. Sectional drawing which shows the structural example of the slinger provided in the lower bearing of the submersible pump which concerns on the 2nd modification of this invention. Sectional drawing which shows the structural example of the slinger provided in the lower bearing of the submersible pump which concerns on the 3rd modification of this invention. Sectional drawing which shows the structural example of the slinger provided in the lower bearing of the submersible pump which concerns on the 4th modification of this invention. Sectional drawing which shows the structural example of the slinger provided in the lower bearing of the submersible pump which concerns on the 5th modification of this invention. Sectional drawing which shows the structural example of the slinger provided in the lower bearing of the submersible pump which concerns on the 6th modification of this invention. Sectional drawing which shows the structural example of the slinger provided in the lower bearing of the submersible pump which concerns on the 7th modification of this invention. Sectional drawing which shows the structural example of the slinger provided in the lower bearing of the submersible pump which concerns on the 8th modification of this invention. Sectional drawing which shows the structural example of the principal part of the conventional submersible pump.

Explanation of symbols

2 Spindle 4 Electric motors 6 and 8 Rolling bearings 6a and 6b Housing 10 Impeller 18 Mechanical seal 20 Slinger 20a Base end portion 20b Surface portion 20c Wall portion 30 Seal plate (sealing plate)
30b Lip 30d Convex part M Motor part P Pump part S Mechanical seal chamber α Bending angle β Inclining angle

Claims (3)

An electric motor that rotates a main shaft that extends in the vertical direction, a motor unit that houses a plurality of rolling bearings that rotatably support the main shaft, and a pump unit that contains an impeller attached to the lower end side of the main shaft A submersible pump provided between a motor unit and a pump unit, and a mechanical seal chamber in which a mechanical seal for keeping the motor unit airtight is arranged vertically.
The rolling bearing disposed near the mechanical seal chamber is provided with an annular slinger for preventing foreign matter from entering the inside of the bearing and the mechanical seal chamber. A base end portion for fixing to the rotating wheel, a surface portion extending in a direction crossing between the rolling bearing and the mechanical seal continuously to the base end portion, and a rolling bearing continuous to the surface portion and opposed to the surface end portion. A submersible pump characterized by having a wall portion extending at a predetermined bending angle of 90 degrees or more and 180 degrees or less in the external direction of the bearing with a predetermined interval between the stationary ring.   An annular sealing plate for sealing the inside of the bearing is interposed between the stationary ring and the rotating ring of the rolling bearing so as to face the slinger, and the outer diameter portion of the sealing plate is a stationary ring. The inner diameter portion of the seal groove is in contact with at least one of an inner peripheral surface and an outer peripheral surface of a seal groove formed continuously in a circumferential direction on a surface facing the rotating wheel with respect to the stationary wheel. The submersible pump according to claim 1. 3. The submersible pump according to claim 1, wherein the sealing plate is provided with a convex portion that protrudes toward the slinger and comes into contact with the slinger on a surface facing the slinger.

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